Rotary Valve Assembly
An exemplary rotary valve is disclosed and includes a first valve member having a first aperture and a second valve member having a second aperture, the first and second apertures being at least partially aligned to define an extent of overlap. The rotary valve also includes a first driving mechanism and a third valve member having a third aperture disposed between the other valve members. The first driving mechanism drives the third valve member in movement to move the third aperture along a path across the extent of overlap to cooperate with the other apertures. The third valve member blocks a passage of fluid between the first and second apertures when it is spaced from the extent of overlap. The rotary valve also includes a second driving mechanism engaged with the first or second valve member and operable to drive that valve member in movement to change the overlap.
This application claims is a divisional application of application Ser. No. 11/716,489 for a ROTARY VALVE ASSEMBLY, filed on Mar. 9, 2007, which is hereby incorporated by reference in its entirety and which claimed the benefit of U.S. Provisional Application No. 60/780,694, filed on Mar. 9, 2006.
BACKGROUND OF THE INVENTION1. Field of the Invention
The present invention is directed generally to a valve assembly, and more specifically, to an adjustable rotary valve assembly for selectively controlling the flow of a fluid and a fluid-flow process including said rotary valve assembly.
2. Description of Related Art
Previous valve assemblies are of limited use for fluid flow applications because of their lack of flow-control adaptability, reversal or metering. Generally, prior art processes employ numerous separate valves and sophisticated electronics to control the cooperation of those valves to bring about a desired process fluid flow control. This need for multiple valves and control circuitry to coordinate the operation of the many valves made process fluid control complex and expensive.
For example, storage of cigars at a proper relative humidity is essential for preservation of quality and flavour. Generally, cigar manufacturers recommend storage between 60% and 70% relative humidity, with preferably greater than 63% and less than 68% relative humidity. Cigar storage outside these generally accepted limits may be detrimental to flavour, draw, burn and other favourable characteristics. Cigar storage in a control environment such as a humidor generally made of moisture absorbing wood, such as Spanish Cedar or Mahogany maintain freshness of cigars without imparting undesirable flavours. measurement of relative humidity is generally by means of mechanical hygrometer and/or chemical or electronic moisture sensor.
Humidity maintenance within a humidor can be active or passive. Active humidity control uses a humidity sensor as feedback to a fan circulating air over a moisture source. Relative humidity lower than a set point results in evaporation of water and increase in humidity within the humidor. One limitation to such a humidifier system is an inability to remove excess moisture. If the relative humidity within a humidor is greater than desired, humidifier only systems provide no relief. Passive humidity control systems do not provide circulation within a humidor and use physical-chemical properties of materials, e.g., propylene glycol solutions, silica gel, salts and other compounds to regulate relative humidity in stagnant air. Changes in relative humidity within a humidor, i.e., either increase or decrease result in acceptance or rejection of water to maintain an equilibrium with air. These materials have an ability to both to acts a both humectant and desiccant. Limitations of passive materials, mixtures and/or solution result from constant equilibrium humidity at constant solution concentrations, mixture proportions or moisture content, an equilibrium relative humidities may be higher or lower than desired and as these materials, solutions and/or mixtures modulate humidity within a humidor the equilibrium relative humidity may change. Thus, both active and passive systems have significant shortcomings, and systems employing a multitude of conventional valves is impractical due to cost and complexity.
According to another example, conventional in-home oxygen concentrators have sophisticated designs capable of providing purity or oxygen at 95% or better, variable oxygen flowrates up to six liters per minute, reliable components and warranty of five years or more and ease of product maintenance.
The number of components in an in-home oxygen concentrator can exceed one-hundred. In general, systems include an air compressor, and a typical valving scheme including many independently-controlled valves to direct gas flow in conduits, several separate process fluid flow conduits, check valves, tubing connectors, fittings and the like are necessary as well as a heat exchanger to expel compressive heat, a fan to circulate cooling air and disperse oxygen deplete air, an intake air and output bacterial filter are all fit within a cabinet enclosure with control panel. A flow valve regulates patient flow and in some cases electronic circuitry controls process cycle time and process step time. The in-home oxygen concentrator generally consumes about 400 watts electrical power, emits 40 to 48 decibels relative sound pressure, weighs nearly 60 pounds and occupies at least two cubic feet of volume.
Accordingly, there is a need in the art for a valve assembly that can be adjusted to provide variable cycle times and process step time, for example. The valve assembly can be a low-cost, simple design that can be operated manually, semi-automatically, automatically, or any combination thereof, as desired. Alternately, the valve assembly can optionally permit variable process fluid flow directions without requiring changes to existing process plumbing configurations.
BRIEF SUMMARY OF THE INVENTIONIn summary, the invention is a rotary valve and method of valving. The rotary valve includes a first valve member having a first aperture. The rotary valve also includes a second valve member having a second aperture. The first aperture and the second aperture are at least partially aligned to define an extent of overlap for receiving and guiding a fluid stream. The rotary valve also includes a first driving mechanism. The rotary valve also includes a third valve member having a third aperture and disposed between the first valve member and the second valve member. The first driving mechanism drives the third valve member in movement such that the third aperture travels along a path across and beyond the extent of overlap and thereby cooperates with the first aperture and the second aperture for receiving and guiding a fluid stream. The third valve member blocks a passage of fluid between the first aperture and the second aperture through the extent of overlap when the third aperture is at a position along the path spaced from the extent of overlap. The rotary valve also includes a second driving mechanism engaged with one of the first valve member and the second valve member and operable to drive the one of the first valve member and the second valve member in movement to change the extent of overlap.
The invention may take physical form in certain parts and arrangement of parts, embodiments of which will be described in detail in this specification and illustrated in the accompanying drawings which form a part hereof, and wherein:
Certain terminology is used herein for convenience only and is not to be taken as a limitation on the present invention. Relative language used herein is best understood with reference to the drawings, in which like numerals are used to identify like or similar items. Further, in the drawings, certain features may be shown in somewhat schematic form.
Although the discussion to follow is general to fluid flow control those skilled in the art will readily realize various applications of the present rotary valve for mixing, metering and flow reversal e.g., for separation process, e.g., pressure swing adsorption separations medical, industrial or agricultural oxygen or hydrogen separation from reformed carbon dioxide, refrigeration and heating cycles, e.g., heat pumps, air conditioners, refrigerators and freezers, dehumidification, e.g., cigar humidors, wine cellars and food preservers or moisture removal process gases like natural gas.
The novel rotary valve assembly described herein provides a means to optimize a process, decrease complexity of design and increase efficiency of a system. Such advantageous effects provide opportunity to lower capital equipment cost.
According to an aspect of the present invention, the rotary valve assembly can be combined with fluid flow conduits wherein adjustable valve members provide a means to vary process step times and a rotary member provides a means to vary overall process cycle time. The novel rotary valve assembly is versatile and applicable systems with a single or multiple inputs and multiple or no outputs, i.e., off setting. Simple positional adjustment provides variable alignment of an aperture or apertures of a first valve member and an aperture or apertures of a second valve member and thereby enable variable process step times as part of a process cycle. The overall cycle time is variable by means of adjustable speed control of a third rotary valve member and interconnection of a through aperture or through apertures thereof with variable position apertures of first and second valve members.
Adjustments of process steps and cycle times may be made manually as a system factory setting, service center or field maintenance or in situ as part of a closed-loop feedback provides a variable process step time and means of process optimization. Moreover, process cycle time becomes adjustable by means of variable speed rotation of a rotary valve member. Either simple manual adjustment or sophisticated closed-loop feedback provides a variable process cycle time and means of process optimization.
The novel variable process step time provides for simple continuous forward rotary drive means and a factory preset process step time or periodic service center or field adjustment or a more sophisticated approach with continuous rotation of one valve member and intermittent adjustment by a second rotary valve member by means of a closed-loop feed back provides a means of process optimization. The novel rotary valve assembly is readily adaptable to variable process cycle time by means of variable speed valve member rotation and closed loop feedback of process variable.
The communication time for each conduit depends upon the angular distance of each through aperture in first valve member, second valve member and third valve member and the relative angular speed of the third valve member to the first valve member and second valve member. Embodiments provide at least one aperture in a first valve member, at least one aperture of a second valve member and at least one through aperture of a third valve member and combinations thereof.
Preferable configurations with two through apertures of the third valve member are with through apertures of equal size and slightly greater in length than the distance between through apertures in the first valve member and/or second valve member to provide momentary interconnection of through apertures of first valve member or through apertures of second valve member. Momentary interconnection of through apertures of a valve member avoids outlet dead-head or inlet starvation resulting from respective disconnection of an inlet or outlet during transition from one through apertures to another. Transition from first aperture to second aperture of first valve member and transition for first aperture to second aperture of second valve member by means of interconnection of first through aperture and second through aperture of third valve member is simultaneous but gradual and avoids detrimental effects of instantaneous pressure changes on system and component performance e.g. power consumption, noise, vibration, component wear, system reliability and useful life.
Rotational speed of third valve member defines a process cycle time. Each aperture of first valve member interconnects with each aperture of second valve member by means of rotary through aperture of third valve member. Process cycle time is generally constant but may require adjustment from time to time to account from changes in compressor, blower or pump output. Factors affecting output include seal wear, altitude, filter occlusion and valve friction and the like. One advantage of a variable speed electric motor is an ability to easily adjust rotational speed. Speed variations arise from mechanical gear ratios or electric voltage, current and/or frequency. Alternate means of variable speed drives include pneumatic power, hydraulic power among others.
Continuous constant speed rotary motion of third valve facilitates low cost electric motor operation with a time control. However, various aperture size combinations along with variable and intermittent rotary speed may provide optimal performance in some configurations, conditions and/or control means. Rotation of the third valve member may be in forward or reverse direction, continuous or intermittent with constant or variable speed depending on desirous communication for each conduit.
The process cycle is independent of direction of rotation and as a result a third valve member may rotate clockwise or counterclockwise. Contrarily, process step time is dependent of direction of rotation for positional adjustment provided a 180° relative rotation limit. Rotation of first valve member or second valve member relative to second valve member or first valve member respectively beyond 180° does not provide unique process step times, rather repeats previously attainable setting. Generally, rotational limits of 0° to 180° provide simpler operation, but are not limitations to device design. Interconnection time of apertures of first valve member and second valve member depends on rotational speed of a third valve member.
According to other embodiments, the present rotary valve provides for manual rotation of a third valve member as in some flow reversal applications, e.g., reversal of a heat pump from heating to cooling. Another embodiment provides a low cost variable speed electric motor and a drive mechanism for a third valve member to control process cycle time. Such drive mechanisms are found in battery operated power screwdrivers and other power tools for example. Other simple embodiments use alternating current synchronous motors such as those commonly found in clocks and a drive mechanism to provide constant speed rotation. Whereas a more sophisticated embodiment provides a feedback loop and varies rotational speed accordingly to optimize process cycle time.
Relative rotational position of the first valve member to the second valve member provides means to adjust process step time. A simple embodiment provides manual adjustment by means of mechanical fastener or detent mechanism and a more sophisticated embodiment provides automatic adjustment by means of feedback loop and secondary drive mechanism to rotate first valve member relative to second valve member and optimize process step time.
Conduit attachments to a first valve member and a second valve member are by means of standard fluid fittings, connectors and seals. First valve member and second valve member are generally stationary with consideration of maximum 180° relative rotation of any combination of first valve member or second valve member or both as necessary for unique process step time adjustments. Another embodiment in a valved system provides relative rotation of a valve member with flow conduits to outlets and a stationary valve member with conduits to inlets e.g., a compressor, blower or pump.
Another embodiment of the novel rotary valve assembly provides easy inlet connection to compressor, blower or pump and outlet connection to control environment, ambient air or process vessel. First and second valve members are relatively stationary insofar as movement is limited to about 0° to about 180° angular degrees about a central axis for unique adjustments to optimize performance for a given application. Communication to compressor, blower or pump is by means of standard fittings, tubing, connectors and the like. A rotary third valve member axially between first and second valve member provides interconnections between conduits of first valve member and conduits of second valve member.
A first drive means connects to third valve member by means of a through hole in either first valve member or second valve member. A similar through hole may be included with other valve member to provide a reduction in surface area and resultant friction and ease of rotation. A shaft with a flat surface a “D” shape hole in third valve member and provides drive. Alternately, a gear may communicate directly to a geared circumference of a rotary third valve member and provide rotation thereof.
Flow passage from conduits of first valve member to conduits of second valve member result of the angular offset of apertures of first valve member and second valve member. Sequential alteration of flow passage interconnection of conduits of first valve member and conduits of second valve member results from the relative position of stationary apertures of first valve member to that of second valve member and rotating apertures of third valve member.
A second drive means may be employed to actuate the first or second valve member, or both the first and second valve members and adjust position of respective apertures. Such a second drive means may be a second motor, clutch attachment to first motor for automatic adjustments or threaded assembly, key-way or detent for manual adjustment.
Similarly, a separate drive mechanism may be applied to a first valve member, second valve member or both first and second valve members. The valve member without drive means transit of third valve member may facilitate component layout and assembly. A second drive mechanism provides a means to adjust manually or automatically the offset between through apertures of first valve member and second valve member and thereby determine process step times duration.
Apertures need only have sufficient surface engagement to provide adequate sealing and valve action. Use of non-reactive, non-volatile greases, e.g., silicone vacuum grease provide a viscous layer between engaged surfaces and increase seal efficacy. In some applications, valve materials may not require additional lubrication.
Such valve member need materials sufficient to maintain sealing surfaces during useful life of system. The surface must remain relatively flat to one another and be resistant to surface damage such as scratches from contaminants ejected by and through a compressor. Such contaminants include machining debris upon initial break-in of compressor, blower or pump or particulate from ambient surroundings. Such materials include ceramic, metal and plastic.
Means of manufacture include pressing, firing, grinding and polishing for ceramics, stamping or machining for metals and molding or machining for plastics. Metals may be cut from bas stock or casts in moulds.
Alternately, a gasket or seal material around apertures on sealing surface may be useful for a high pressure or vacuum application. Moreover, a ball bearing and bearing race on sealing surface may provide utility to decrease power consumption in some applications.
A support subassembly employs a means to maintain sealing surfaces of first valve member, second valve member and third valve member. Typically three springs reside in a non-sealing surface of the first valve member and a support ring to provide a constant axial force between first valve member sealing surface and first sealing surface of third valve member. A pliable gasket maintains contact between support ring and a housing. Anti-rotation pins connect a housing and first valve member and prevent rotation of first valve member relative to housing. Position pins are not fixed axially and allows the first valve member to move freely and accommodate undulations due to interactions with third valve member.
A detent subassembly provides recesses for a spring loaded ball to reside. Typically, three springs reside in non-sealing surface of second valve member with balls atop. A ring with recesses to accept these balls allows rotation of second valve member. A pliable gasket material resides between non-recess side of detent ring and housing. Position pins connect between housing and non-sealing surface of second valve member and prevent rotation of second valve member relative to housing. Removal of position pins allows rotation of second valve member from one detent position to another and thereby adjustment of valve. Positions pins are not fixed axially and allow the second valve member to move freely due and accommodate undulations due to interactions with third valve member. The springs provide a constant force and maintain sealing surfaces of second valve member and third valve member.
An alignment subassembly maintains first valve member, second valve member and third valve member in proper orientation. A pliable gasket material covers the radial surface of each the first valve member and second valve member. A rigid collar envelops first valve member, second valve member and third valve member and provides a stop to maintain spring loads on the assembly.
A housing subassembly consists of a top housing and a bottom housing. These housing parts interconnect to enclose the valve members, provide load to the springs by means of generally three bolts with accompanying nuts, a rigid stop for anti-rotation pins and position pins.
Prior art describe systems by which a series of independently actuated valves and control means permit flow in a system. This novel rotary valve assembly obviates a need for such a series of independently actionable valves and need for sophisticated control thereof. Moreover prior art rotary devices have fixed process step times as a function of flow passage and aperture geometry which do not readily provide adjustability or process optimization.
According to one aspect, the present invention provides a rotary valve assembly for controlling process fluid flow. The rotary valve comprises a first valve member disposed within a fluid flow path and including an aperture formed therein through which the process fluid introduced to the rotary valve can flow, a second valve member including an aperture formed therein that is at least partially aligned with the aperture formed in the first valve member within the fluid flow path and through which the process fluid can flow to be discharged from the rotary valve, and a third valve member disposed within the fluid flow path between the first valve member and the second valve member and including at least one aperture formed therein. An alignment of the aperture formed in the third valve member relative to at least one of the aperture formed in the first valve member and the aperture formed in the second valve member is adjustable to selectively establish a conduit through which the process fluid can flow.
According to another aspect, the first valve member of the rotary valve assembly includes a plurality of apertures formed therein and a separate input conduit in fluid communication with each of said apertures. At least one of the first and second valve members is rotatable about a primary axis to at least partially align the aperture formed in the second valve member with one or more of the plurality of apertures formed in the first valve member within the fluid flow path to establish a desired output from the rotary valve.
According to another aspect, a first input conduit is in fluid communication with one of the plurality of apertures formed in the first valve member to establish an internal passage between the rotary valve and a desiccant environment. A second input conduit can optionally be provided in fluid communication with another of the plurality of apertures formed in the first valve member to establish an internal passage between the rotary valve and a humid environment.
According to another aspect, the rotary valve of the present invention includes a first input conduit in fluid communication with one of the plurality of apertures formed in the first valve member to establish an internal passage between the rotary valve and a vacuum environment. A second input conduit can optionally also be provided in fluid communication with another of the plurality of apertures formed in the first valve member to establish an internal passage between the rotary valve and an environment in which a fluid is input at an elevated pressure. The vacuum environment can be established by an inlet of a compressor and the elevated pressure can be established by an output of the compressor.
According to another aspect, the second valve member includes a plurality of apertures formed therein and a separate output conduit in fluid communication with each of said apertures. At least one of the first and second valve members is rotatable about a primary axis to at least partially align the aperture formed in the first valve member with one or more of the plurality of apertures formed in the second valve member within the fluid flow path to establish a desired output from the rotary valve.
According to another aspect, the third valve member includes a plurality of apertures formed therein and an alignment of the plurality of apertures formed in the third valve member relative to at least one of the aperture formed in the first valve member and the aperture formed in the second valve member is adjustable to selectively establish a conduit through which the process fluid can flow through the first second and third valve members.
According to another aspect, the first valve member includes a plurality of apertures formed therein, each of said apertures being at least partially aligned with the aperture formed in the second valve member. A separate input can optionally be provided in fluid communication with each of the plurality of apertures formed in the first valve member and the alignment of the aperture formed in the third valve member relative to the plurality of apertures formed in the first valve member can optionally be adjustable to selectively establish fluid communication between the plurality of apertures formed in the first valve member and the aperture formed in the second valve member.
According to another aspect, the third valve member is rotatable about a central axis along which the first, second and third valve members are coaxially aligned. The rotary valve assembly can optionally further comprise a motor, such as an electric, hydraulic, pneumatic or other type of prime mover operatively coupled to the third valve member to drive rotation of the third valve member about the central axis.
According to another aspect, the third valve member includes a surface that engages a surface of the first valve member and a surface that engages the second valve member to interfere with process fluid flow through the valve when the aperture formed in the third valve member is not at least partially aligned with the apertures formed in the first and second valve members.
According to yet another aspect at least one of the first and second valve members is rotationally adjustable about a central axis to a plurality of discrete angular orientations. A detent ring can optionally be provided to the rotary valve assembly to define each of the plurality of discrete angular orientations.
According to yet another aspect, the present invention provides a humidity control apparatus for controlling humidity within a closed environment comprising a desiccant, a humidifier and the rotary valve assembly described herein.
According to yet another aspect, the present invention provides a heat pump for controlling a temperature within a closed environment comprising an evaporator, a condenser and the rotary valve assembly described herein.
According to yet another aspect, the present invention provides an oxygen concentrator comprising the rotary valve assembly described herein and at least one component selected from the group consisting of: an adsorbent bed, a compressor, a blower, and a pump.
According to yet another aspect, the present invention provides a water purification system for reducing a level of impurities in water to a reduced level that is less than an original level of said impurities in the water when the water was introduced to the water purification system, the water purification system comprising the rotary valve assembly described herein and an evaporator, a condenser, or both an evaporator and a condenser.
Rotary ValveThe novel rotary valve described herein combines variable process cycle time and variable process step time in an integral assembly for use with process fluid flow systems and thereby provides for a process optimization of any such system. Process applications include flow reversal, flow mixing, flow metering and the like without requiring significant alterations to existing process-fluid-flow conduits, as described in detail below.
According to an embodiment, a first valve member with a aperture, a second valve member with a aperture and a third valve member with a through aperture provides a variable on-off flow assembly with on input and one output.
(ii) in another embodiment a first valve member with a first aperture and a second aperture, a second valve member with a aperture and a third valve member with a through aperture provides a variable on-off flow assembly with two inputs and one output;
(iii) in another embodiment a first valve member with a first aperture and a second aperture, a second valve member with a first aperture and a second aperture and a third valve member with a through aperture provides a variable flow assembly with two inputs and two output;
(vi) in another embodiment a first valve member with a first aperture and a second aperture, a second valve member with a first aperture and a second aperture and a third valve member with a first through aperture and a second through aperture provides a variable flow assembly with two inputs and two outputs.
Drive mechanism adapts for variable speed by means of alternating or direct current electric motor or other power source. Transition between process steps in gradual and minimizes detrimental effects of rapid changes e.g., avoids compressor, blower or pump output dead-head or inlet starvation.
In another embodiment a system the novel rotary valve described herein provides adjustment of process step time to compensate for variable performance of process vessels. This unique and novel rotary valve assembly described herein provides a means to adjust process step time between 100% and 0% to the converse of 0% and 100% without need for expensive electronic circuitry.
As such the first valve member and second valve member offset of 90° angular degrees provides equal process step times. Adjustment of valve member aperture offset may be accomplished manually at factory, service center or in field or automatically with closed loop feed back of product gas concentration.
The first valve member (100) includes at least a first aperture (101) formed therein through which a fluid can travel, and optionally, a second aperture (102) formed therein. When at least one of the first aperture (101) and second aperture (102) become at least partially aligned with a first through aperture (301) of a third valve member (300) and at least a first aperture (201) or second aperture (202) of second valve member (200), this relative alignment enables communication of the fluid through a flow passage from conduit(s) in fluid communication with a first valve member (100) to one or more conduit(s) in fluid communication with a second valve member (200).
The second valve member (200) includes at least a first aperture (201) formed therein, and optionally a second aperture (202) that can each be at least partially aligned with a through aperture (301) formed in the third valve member (300) to establish fluid communication between the first and second valve members (100) and (200). When such fluid communication is established, there is at least partial alignment of at least a first through aperture (301) formed in the third valve member (300) and at least one aperture of the first and second valve members (100) and (200) which forms a flow passage through the first valve member (100), second valve member (200) and third valve member (300).
The third valve member (300) includes at least a first through aperture (301), and optionally a second through aperture (302) or a plurality of additional through apertures that can be selectively aligned with at least one aperture formed in each of the first and second valve members (100) and (200) to establish a fluid flow path.
According to the configuration embodiments shown in
A second valve member (200) with a first aperture (201) and a second aperture (202) in a form of arcuate slots diametrically opposed generally by 180°. A first surface (203) of second valve member (200) provides engagement to a third valve member. Conduits connect to these slots to provide flow passage means to outlets. The slots are separated by unslotted area sufficient for sealing and resulting in preferred flow by means of through aperture interconnection
First aperture (100) and second aperture (102) of first valve member (100) and first aperture (201) and second aperture (202) of second valve member (200) are radially coincident to provide flow passage means therethrough.
A third valve member (300) with a first through aperture (301) and a second through aperture (302) in a form of arcuate slots diametrically opposed generally by 180° and radially coincident to first aperture (100) and second aperture (102) of first valve member (100) and first aperture (201) and second aperture (202) of second valve member (200). A first surface (303) of the third valve member (300) engages the first surface (103) of first valve member (100) and a second surface (304) of third valve member (300) engages first surface (203) of the second valve member (200) to create preferential flow passages and sealing surfaces. Such sealing surfaces provide preferable flow passage to and from conduits by means of first aperture (101) and second aperture (102) of first valve member (100) and first aperture (201) and second aperture (202) second valve member (200) by means of interconnection of first through aperture (301) and second through aperture (302) of third valve member (300).
FIG. 1-(II) first aperture (101) and second aperture (102) of first valve member (100) interconnected with first aperture (201) of second valve member (200) by means of first through aperture (301) of third valve member (300) and first aperture (101) and second aperture (102) of first valve member (100) interconnected with second aperture (202) of second valve member (200) by means of second through aperture (302) of third valve member (300);
FIG. 1-(III) second aperture (102) of first valve member (100) interconnected with first aperture (201) of second valve member (200) by means of first through aperture (301) of third valve member (300) and first aperture (101) of first valve member (100) interconnected with second aperture (201) of second valve member (200) by means of second through aperture (302) of third valve member (300);
FIG. 1-(IV) first aperture (101) of first valve member (100) interconnected with first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) by means of second through aperture (302) of third valve member (300) and second aperture (102) of first valve member (100) interconnected with first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) by means of first through aperture (301) of third valve member (300);
FIG. 1-(V) first aperture (101) of a first valve member interconnected with a first aperture (201) of a second valve member (200) by means of a second through aperture (302) of a third valve member (300) and second aperture (102) of first valve member (100) interconnected with a second aperture (202) of a second valve member (200) by means of a first through aperture (301) of a third valve member (300);
FIG. 1-(VI) first aperture (101) and second aperture (102) of first valve member (100) interconnected with first aperture (201) of second valve member (200) by means of second through aperture (302) of third valve member (300) and first aperture (101) and second aperture (102) of first valve member (100) interconnected with second aperture (202) of second valve member (200) by means of first through aperture (301) of third valve member (300);
FIG. 1-(VII) second aperture (102) of first valve member (100) interconnected with first aperture (201) of second valve member (200) by means of second through aperture (302) of third valve member (300) and first aperture (101) of first valve member (100) interconnected with second aperture (202) of second valve member (200) by means of first through aperture (301) of third valve member (300);
FIG. 1-(VIII) first aperture (101) of first valve member (100) interconnected with first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) by means of first through aperture (301) of third valve member (300) and second aperture (102) of first valve member (100) interconnected with first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) by means of second through aperture (302) of third valve member (300).
In
A first driving mechanism drives the third valve member 300 in movement. Several figures show and several paragraphs herein describe driving mechanisms operable to drive the third valve member 300. One such driving mechanism is shown in
As will be set forth in more detail below, a second driving mechanism is engaged with either the first valve member 100 or the second valve member 200. Several figures show and several paragraphs herein describe driving mechanisms operable to drive one of the first and second valve members 100, 200. One such driving mechanism is shown in
The exemplary first valve member 100 shown in
The exemplary second extent of overlap 754 is positioned along the path 752. In one or more embodiments of the invention, the first driving mechanism drives the third valve member 300 in movement such that the third aperture 301 travels along all the path 752 and passes across and beyond the second extent of overlap 754 and thereby cooperates with the fourth aperture 102 and the fifth aperture 202 for receiving and guiding a fluid stream. The third valve member 300 blocks a passage of fluid between the fourth aperture 102 and the fifth aperture 202 through the second extent of overlap 754 when the third aperture 301 is at a position along the path 752 spaced from the second extent of overlap 754.
The exemplary first aperture 101 and the exemplary fifth aperture 202 can be at least partially aligned to define a third extent of overlap 756 for receiving and guiding a fluid stream. The third extent of overlap 756 is positioned along the path 752. The first driving mechanism drives the third valve member 300 in movement such that the third aperture 301 travels along the path 752 and passes across and beyond the third extent of overlap 756 and thereby cooperates with the first aperture 101 and the fifth aperture 202 for receiving and guiding a fluid stream. The fluid stream passing through the third extent of overlap 756 can be different from the fluid stream passing through the extent of overlap 750 and different from the fluid stream passing through the extent of overlap 754. The third valve member 300 blocks a passage of fluid between the first aperture 101 and the fifth aperture 202 through the third extent of overlap 756 when the third aperture 301 is at a position along the path 752 spaced from the third extent of overlap 756.
The exemplary fourth aperture 102 and the exemplary second aperture 201 can be at least partially aligned to define a fourth extent of overlap 758 for receiving and guiding a fluid stream. The fourth extent of overlap 758 is positioned along the path 752. The first driving mechanism drives the third valve member 300 in movement such that the third aperture 301 travels along all the path 752 and passes across and beyond the fourth extent of overlap 758 and thereby cooperates with the fourth aperture 102 and the second aperture 201 for receiving and guiding a fluid stream. The fluid stream passing through the fourth extent of overlap 758 can be different from each of the fluid streams passing through the extents of overlap 750, 754, 756. The third valve member 300 blocks a passage of fluid between the fourth aperture 102 and the second aperture 201 through the fourth extent of overlap 758 when the third aperture 301 is at a position along the path 752 spaced from the fourth extent of overlap 758.
The third valve member 300 can also include an aperture designated as a “sixth” aperture 302. It is noted that the sixth aperture 302 is not shown in
It is noted that there can be embodiments of the invention in which one of the first and second valve members 100, 200 have different numbers of apertures.
Embodiments of the rotary valve can be operated in numerous ways and in numerous operating environments. As set forth above, a first driving mechanism can drive the third valve member 300 in movement such that the third aperture 301 (and possibly the sixth aperture 302) travels along the path 752. The first driving mechanism can drive the third valve member 300 continuously such that the first aperture 101 and the second aperture 201 are repeatedly blocked from communicating with one another. The first driving mechanism can drive the third valve member 300 at a constant speed such that the first aperture 101 and the second aperture 201 are blocked from communicating with one another at regular intervals. The first driving mechanism can drive the third valve member 300 at different speeds such that the first aperture 101 and the second aperture 201 are repeatedly blocked from communicating with one another at irregular intervals.
FIG. 8-(I) further depicts through aperture alignment as follows: interconnection of first aperture (101) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of first through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) from (D) to (A) is 180° and interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) from (B) to (C) 180°;
FIG. 8-(II) interconnection of first aperture (101) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of first through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) within quadrant (A) is 135°, interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) within quadrant (C) 135°; interconnection of second aperture (102) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of second through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) within quadrant (B) is 45°, interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) within quadrant (D) 45°;
FIG. 8-(III) interconnection of first aperture (101) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of first through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) within quadrant (A) is 90°, interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) within quadrant (C) 90°; interconnection of second aperture (102) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or second through aperture (301) of third valve member (300) within quadrant (B) is 90°, interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) within quadrant (D) 90°;
FIG. 8-(IV) interconnection of first aperture (101) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of first through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) within quadrant (A) is 45°, interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) within quadrant (C) 45°; interconnection of second aperture (102) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of first through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) within quadrant (B) is 135°, interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) within quadrant (D) 135°;
FIG. 8-(V) interconnection of first aperture (101) of first valve member (100) with first aperture (201) of second valve member (200) by means of rotation of first through aperture (301) of third valve member (300) or second through aperture (302) of third valve member (300) from (D) to (A) is 0° and interconnection of second aperture (102) of first valve member (100) with second aperture (202) of second valve member (200) by means of rotation of second through aperture (302) of third valve member (300) or first through aperture (301) of third valve member (300) from (B) to (C) 0°;
FIG. 9-(I) further depicts relative rotation of rotary valve assembly as follows: a first valve member (100) to a second valve member (200) and independent of a third valve member (300);
relative position of a first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) to a first aperture (101) of a first valve member (100) and a second aperture (102) of a first valve member (100) at 0° offset;
FIG. 9-(II) relative position of a first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) to a first aperture (101) of a first valve member (100) and a second aperture (102) of a first valve member (100) at 45° offset;
FIG. 9-(III) relative position of a first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) to a first aperture (101) of a first valve member (100) and a second aperture (102) of a first valve member (100) at 90° offset;
FIG. 9-(IV) relative position of a first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) to a first aperture (101) of a first valve member (100) and a second aperture (102) of a first valve member (100) at 135° offset; and
FIG. 9-(V) relative position of a first aperture (201) of second valve member (200) and second aperture (202) of second valve member (200) to a first aperture (101) of a first valve member (100) and a second aperture (102) of a first valve member (100) at 180° offset;
In a preferred embodiment a first drive means (952) provides variable speed rotation of third valve member (300) and enable variable process cycle time. In a preferred embodiment a first drive means (952) is a variable speed electric motor. An alternating current motor provides speed as a function of current frequency, whereas a direct current motor provides speed as a function of current magnitude. A first drive mechanism provides a rotating shaft to a surface of third valve member (300) by means of through hole in first valve member. An alternate embodiment provides first drive mechanism (953) as a gear in communication with a geared circumferential surface of third valve member (300). An adjustment means (950) in communication with an adjustment mechanism (951) provides variable rotational position of first aperture (201) of a second valve member (200) and second aperture (202) of second valve member (200) to a first aperture (101) of a first valve member (100) and second aperture (102) of first valve member (100) and enables variable process step time. An adjustment means may be a manual turn engagement of second valve member (200) in combination with an adjustment mechanism (951) of a spring and ball engagement of a detent surface of second valve member (200) or a threaded engagement and positional fastener.
Rotational speed of third valve member defines a process cycle time. Aperture(s) of first valve member (100) interconnects with aperture(s) of second valve member (200) by means of rotary through aperture(s) of third valve member (300). Process cycle time is generally constant but may require adjustment from time to time to account from changes in input. Factors affecting input could be compressor, blower or pump seal wear, altitude, filter occlusion and valve friction. One advantage of a variable speed electric motor is an ability to easily adjust rotational speed. Speed variations arise from mechanical gear ratios or electric voltage, current and/or frequency. Alternate means of variable speed drives include pneumatic power among others.
Continuous constant speed rotary motion of third valve facilitates low cost electric motor operation with a time control. However, various slot size combinations along with variable and intermittent rotary speed may provide optimal performance in some configurations, conditions and/or control means. Rotation of the third valve member (300) may be in forward or reverse direction, continuous or intermittent with constant or variable speed depending on the communication desired for each conduit.
The rotary valve assembly can optionally be provided to a humidity control apparatus for use in a humidity-control process selectively establishing process fluid flow and variable conduit interconnection. Process cycle time is variable by means of rotational speed of through aperture(s) formed in the third valve member and respective alignment with aperture(s) of a first valve member and aperture(s) of a second valve member. Process steps of desiccation, humidification, or any combination thereof vary by means of adjustable position and alignment of aperture(s) of a first valve member and aperture(s) of a second valve member. The rotary valve assembly provides means for gradual transition and flow passage between process steps. A valved system with a control environment in combination with desiccant(s), humidifier(s) compressor(s), blower(s), pump(s) and/or adsorption process provides means to control humidity therein. A valved system provides means to alternate individually between desiccant and/or humidifier with or without mechanical flow circulation. A valved system in combination with adsorption process further provides a regenerative means of controlling humidity.
The present invention further comprises the rotary valve assembly included with a pressure swing adsorption system for gas separation and more particularly to air separation. For example, the rotary valve assembly can be employed for use with a single adsorbent bed or two or more adsorbent beds in vacuum-pressure swing adsorption and pressure swing adsorption systems for the recovery of oxygen from air and use thereof in industry, healthcare, agriculture and aquaculture among others; use of nitrogen recovered from air for food preservation, explosion and fire retardancy among others; and moisture removal from natural gas or a control environment, separation of hydrogen from carbon dioxide in natural gas reformation and other applications.
The discussion herein will be generally directed toward air separation and oxygen concentration for the sake of brevity. However, those skilled in the art will readily appreciate technology described herein for other applications.
Air is a mixture of gases most generally described as nitrogen 78.084±0.004%, oxygen 20.946±0.002%, argon 0.934±0.001%, carbon dioxide 0.033±0.001% exclusive of water vapor. In general, an oxygen-argon mixture results from preferred selective removal of nitrogen, carbon dioxide and water vapor from air. Although air generally has nitrogen, oxygen, argon, carbon dioxide and water vapor as primary constituents, in a selective adsorption process air is a binary mixture of more absorbable components, i.e., nitrogen, carbon dioxide and water vapor and less absorbable components, i.e., oxygen-argon. As a result the oxygen-argon ratio changes after removal of nitrogen and other components from 20.946% and 0.934% to 95.731% and 4.269% respectively. The nitrogen rich gas is 99.958% pure and 100% inert. The oxygen-rich fraction varies with system design and performance optimization.
Although the discussion to follow is specific to oxygen separation from air for the sake of brevity, those skilled in the art will readily realize other applications for separations from liquid or gas such as industrial or agricultural oxygen, moisture removal from natural gas or hydrogen separation from reformed carbon dioxide.
The product gas generally considered as oxygen is actually a binary mixture of oxygen and argon with up to about 95% oxygen purity. The system has a product tank to store produced oxygen-argon mixture and generally deliver between 0 and 6 liters per minute for patient use. A gas pressure regulator maintains output of five pounds per square inch nominal pressure. The adsorbent bed and product tank pressure ranges between 10 and 22 pounds per square inch nominal with adsorbent bed pressurization time of 8 to 30 seconds. Adsorbent bed(s) vent to atmosphere and require(s) from approximately one-half to one pound of adsorbent, typically five angstrom (5 Å) zeolite per liter per minute oxygen at 95% purity. In general the adsorbent requirement decrease with number of adsorbent beds operating sequentially in parallel.
As an adsorbent bed depressurizes a portion of the product gas flows back and displaces residual nitrogen-rich gas by occupying void space within the adsorbent bed with the remaining product gas flowing to a patient. In the event that patient demand exceeds purge gas requirement, the patient receives preferred flow albeit at lower oxygen concentration. The purge gas requirement can vary from a fraction to a multiple of patient flowrate depending on system design.
Control is generally open-loop feedback, i.e., the output variable oxygen content is not generally the feedback parameter, but rather product tank or adsorbent bed pressure or pressurization time. A pressure based control system discharges the nitrogen rich gas at a fixed pressure, e.g., 20 to 22 pounds per square inch gauge pressure. The rate of pressure increase from a lower pressure to a higher pressure depends on patient flowrate, compressor output, filter occlusion, altitude, leaks among other factors. Electronic controls provide defaults to begin desorption of adsorbent beds in the event of failure to reach a pressure setpoint after a pre-determined time period. Such failures may result from excessive patient flowrate, reduced compressor output, filter occlusion, high altitude or system leaks among other causes. Pressure based design requires a pressure sensor, electronic circuitry and means to actuate a valve or valves.
Time based control systems alternate from pressurization to depressurization of bed(s) at a preset time regardless of product tank or adsorbent bed pressure, generally 8 to 30 seconds. Time based control although simpler does not account for variables affecting adsorbent bed pressurization rate, e.g., compressor output, filter occlusion, patient flowrate, altitude among other variables. As a result time based control systems may need extra capacity to anticipate such variables else oxygen content may decrease as a result. Insufficient adsorbent bed pressure may result in poor adsorbent regeneration and low oxygen concentration and excess pressurize may result in nitrogen break-through, i.e., nitrogen contamination of product oxygen and low oxygen concentration. Time based control may be mechanical by means of electric motor and gear reduction or electronically actuated valves. A disadvantage of mechanical control timing systems is an inability to compensate for differences in process step times, e.g., variation in individual adsorbent bed performance or unequal and variable pressurization and depressurization times.
A closed-loop feedback alternates pressurization and depressurization based upon oxygen concentration. One difficulty in a closed-loop feedback control is sensor lag time in determining oxygen purity. Closed-loop feed back control systems require sophisticated electronic circuitry.
Oxygen separation in VPSA and PSA systems is batchwise, i.e. adsorbent bed produces oxygen-rich gas and then goes offline for regeneration, i.e., does not produce oxygen during regeneration. In practice a VPSA and PSA system requires only one adsorbent bed. With a single bed a sufficient amount of air for maximum product flow must be compressed in one cycle resulting in a large compressor, high power consumption, saw-tooth variation in both product tank pressure and output flowrate. However, advantages of a single bed system are simple design and low component cost.
Two adsorbent beds operating in parallel have alternate pressure and discharge cycles and require compression of only one-half the total air requirement for maximum patient flow. As a result compressor load is half that of a single adsorbent bed system. A three adsorbent bed system would theoretically cut a compressor load by one third and so on. Whiles advantages of multi-adsorbent bed systems include smaller compressors, less power and generally less adsorbent media the disadvantages include cost and complexity of redundant components.
The multiple adsorbent bed system includes a plurality of parallel groupings of adsorbent beds sequentially processed to effect an almost continuous cycle of pressurization, pressure stabilization, depressurization and purge. Such systems provide flow of product gas with very little pressure fluctuation and can eliminate a need for output pressure regulation.
The PSA system, in general, requires three steps: (1) Charge: Compressed air is introduced into an adsorbent bed for nitrogen removal from the gas stream, (2) Discharge: The bed pressure is rapidly released and nitrogen breaks a weak bond with the adsorbent media and flows out of the system and (3) Purge: Product gas flow back into a discharging adsorbent bed and displaces nitrogen-rich void gas. Sudden pressure change governs efficiency of discharge, i.e., greater pressure change in shorter time breaks more weak bonds between nitrogen molecules and adsorbent media.
In the PSA system, depressurization and concurrent or concurrent purge flows are simultaneous with discharge to atmospheric pressure or some intermediate pressure. The vacuum swing adsorption (“VSA”) system can operate entirely at sub-atmospheric pressure to reduce the amount of work required to compress air. In the VSA system a pump evacuates an adsorbent bed and low pressure purge gas and atmospheric pressure air recharges the adsorbent bed. A blower provides low pressure product gas for use downstream. The VPSA system provides pressurized air to the bed directly from atmosphere or a low pressure feed blower then vent to atmospheric pressure and evacuate to low pressure by vacuum pump. The vacuum-pressure swing adsorption (“VPSA”) system operates at super-atmospheric pressure, i.e., above atmospheric pressure and evacuate adsorbent bed with a vacuum pump or compressor inlet. Some embodiments of the VPSA system repressurize directly from a compressor air while others initially repressurize with atmospheric pressure and follow with compressed air and thereby reduce compressor load. In descriptions provided herein, PSA and VSA systems are equivalent, the only difference being the absolute pressure relative to atmospheric.
According to the present invention, a unique rotary valve assembly is provided, combined with a nominal pressure fluid, a high pressure fluid and a low pressure fluid wherein adjustable valve members provide a means to vary process step times, i.e., pressurization and depressurization and a rotary member provides a means to vary overall process cycle time. The rotary valve assembly is versatile and applicable to VPSA, PSA or VSA systems with a single adsorbent bed or pair of adsorbent beds. Simple positional adjustment provides variable alignment of through apertures of a first valve member and a second valve member and thereby enable variable process step times as part of a process cycle. The overall cycle time is variable e by means of adjustable speed control of a third rotary valve member.
For example, in a single adsorbent bed system pressurization may require more time than depressurization as a result of compressor output, filter occlusion, altitude among other factors. Likewise in a paired adsorbent bed system variations in adsorbent bed performance may be offset by providing different pressurization times for each adsorbent bed. Such adjustment may be made manually as a factory setting, service center or field maintenance or in situ as part of a closed-loop feedback provides a variable process step time and means of process optimization. Moreover, process cycle time becomes adjustable by means of variable speed rotation of a rotary valve member. Either simple manual adjustment or sophisticated closed-loop feedback provides a variable process cycle time and means of process optimization.
The variable process step time provides for simple continuous forward rotary drive means and a factory preset process step time or periodic service center or field adjustment or a more sophisticated approach with continuous rotation of one valve member and intermittent adjustment by a second rotary valve member by means of a closed-loop feed back provides a means of production optimization for single or paired adsorbent bed PSA or VPSA systems. The rotary valve assembly is readily adaptable to variable process cycle time by means of variable speed valve member rotation and closed loop feedback of adsorbent bed pressure.
The communication time for each conduit, i.e., ambient air, higher pressure air, lower pressure air, and adsorbent bed(s) depends upon the angular distance of each through aperture in first valve member, second valve member and third valve member and the relative angular speed of the third valve member to the first valve member and second valve member. A preferred embodiment for an adsorptive separation process provides two equal size apertures in a first valve member and second valve member.
The through apertures of the third valve member equal in size and slightly greater in length than the distance between apertures in the first valve member and second valve member provide momentary interconnection of apertures of first valve member or apertures of second valve member. Momentary interconnection of apertures of a valve member avoids compressor outlet dead-head or compressor inlet starvation resulting from respective disconnection of an adsorbent bed or ambient air during transition from one through apertures to another and as a result partially unloads a compressor and reduces power consumption. Transition from first apertures to second apertures of first valve member and transition for first aperture to second aperture of second valve member by means of interconnection of first through aperture and second through aperture of third valve member is simultaneous but gradual and avoids detrimental effects of instantaneous pressure changes on system and component performance e.g. noise, vibration, component wear, system reliability and useful life.
Rotational speed of third valve member defines a process cycle time. Each aperture of first valve member interconnects with each aperture of second valve member by means of rotary through aperture of third valve member. Process cycle time is generally constant but may require adjustment from time to time to account from changes in compressor output. Factors affecting compressor output include seal wear, altitude, filter occlusion and valve friction. One advantage of a variable speed electric motor is an ability to easily adjust rotational speed. Speed variations arise from mechanical gear ratios or electric voltage, current and/or frequency. Alternate means of variable speed drives include pneumatic power among others.
Continuous constant speed rotary motion of third valve facilitates low cost electric motor operation with a time control. However, various through aperture size combinations along with variable and intermittent rotary speed may provide optimal performance in some configurations, conditions and/or control means. Rotation of the third valve member may be in forward or reverse direction, continuous or intermittent with constant or variable speed depending on the communication desired for each conduit.
The process cycle is independent of direction of rotation and as a result a third valve member may rotate clockwise or counterclockwise. Contrarily, process step time is dependent of direction of rotation for positional adjustment provided a 180° relative rotation limit. Interconnection time of through apertures of first valve member and second valve member depends on rotational speed of a third member.
A simple embodiment provides a low cost variable or constants speed electric motor and a drive mechanism for a third valve member to control process cycle time. Whereas a more sophisticated embodiment provides a feedback and varies rotational speed accordingly to optimize process cycle time.
Relative rotational position of first valve member to second valve member provide means to adjust process step time. A simple embodiment provides manual adjustment by means of mechanical fastener or detent mechanism and a more sophisticated embodiment provides automatic adjustment by means of a feedback and secondary drive mechanism to rotate first valve member relative to second valve member and optimize process step time.
Conduit attachments to a first valve member and a second valve member are by means of standard fluid fittings, connectors and seals. First valve member and second valve member are generally stationary with consideration of maximum 180° relative rotation of any combination of first valve member or second valve member or both as necessary for unique process step time adjustments. A preferred embodiment in a single adsorbent bed system provides relative rotation of a valve member with conduits to adsorbent bed and ambient air or individually to paired adsorbent beds and a stationary valve member with conduits to a compressor inlet and compressor outlet. Likewise another preferred embodiment for a paired adsorbent bed system is relative rotation of a valve member with conduits to adsorbent beds and a stationary valve member with conduits to a first compressor inlet and a second compressor outlet or a compressor outlet and ambient air.
A surge vessel provides both a buffer for sudden pressure changes and reservoir for low purity product gas used in purge. A purge vessel provides sufficient volume product purity gas for cleansing the void volume of the adsorbent bed. The product vessel maintains product purity gas for further use and check valve between product vessel and purge vessel reduces product gas loss during adsorbent bed evacuation.
In another embodiment the intake port connects to a conduit wherein a “T” fitting and two check valves provide preferential flow from a filter for feed air and exhaust muffler for discharge gas. These two elements are separate so that exhaust does not re-enter the feed stream and preferable in a single adsorbent bed VPSA system wherein a single aperture provides communication for both intake and exhaust. A single or paired adsorbent bed PSA and paired bed VPSA provide separate conduits for intake and exhaust and reduce potential for reintroduction of processed fluid.
A preferred embodiment of rotary valve assembly provides easy connection to compressor inlet and outlet, ambient air and adsorbent bed. First and second valve member are relatively stationary insofar as movement is limited to 0° to 180° angular degrees for unique adjustments to optimize performance. Communication to compressor, air and adsorbent bed is by means of standard fittings, tubing, connectors and the like. A rotary third valve member axially between first and second valve member provides interconnections between conduits of first valve member and conduits of second valve member.
In one embodiment of a single bed VPSA system a utility of this rotary valve assembly is an ability to alternate a simultaneous change of compressor inlet to compressor outlet and air intake to adsorbent bed exhaust by means of continuous forward rotation and provide gradual transition between process step of pressurization and depressurization while avoiding compressor output dead-head or inlet starvation.
In another embodiment of a single bed PSA system a utility of this rotary valve assembly is direction of a compressor outlet to adsorbent and compressor inlet to air intake during pressurization and alternately redirects compressor outlet to ambient air during depressurization and thereby unloads compressor and reduces power consumption.
In another embodiment of a pair bed VPSA system the rotary valve assembly described herein combines with a twin-head Wobble Piston compressor to provide adjustment of pressurization time of each adsorbent bed to compensate for variable adsorbent bed performance and depressurizes to vacuum pressure. In such a configuration one compressor chamber as a compressive element and a second chamber as a vacuum element. Similarly, separate pressure and vacuums sources may connect to first valve member. The intake air and exhaust gas conduits remain constant and do not alternately switch as in a single bed system.
In yet another advantage of the rotary valve assembly in combination with a system is an ability to reduce power requirements. By flowing pressurized gas into a compressor inlet with compressor outlet at atmospheric pressure energy the system recovers energy from previous compressive work on the evacuation step. Likewise, flowing atmospheric pressure air into an evacuated adsorbent bed provides for expansion work and electric motor power reductions. Similarly in a twin cylinder embodiment both compressive and expansive energy recovery are simultaneous and work on the other cylinder, i.e., compressive work imparted to compressor and expansive work imparted to vacuum pump.
In another embodiment a paired bed PSA system the rotary valve assembly described herein provides adjustment of pressurization time of each adsorbent bed to compensate for variable adsorbent bed performance and depressurizes to atmospheric pressure. This unique and rotary valve assembly described herein provides a means to adjust process step time between nearly 100% pressurization and nearly 0% depressurization to the converse of nearly 0% pressurization and nearly 100% depressurization without need for expensive electronic circuitry. In yet another embodiment of a rotary valve assembly described herein two adsorbent beds attach to second valve member. As such the first valve member and second valve member may be offset by 90° angular degrees so that each adsorbent bed has equal pressurization and evacuation time or otherwise to compensate for individual performance of each bed. As in a single bed system, adjustment of the second valve member aperture offset may be accomplished manually at factory, service center or in field or automatically with closed loop feed back of product gas concentration.
The rotary valve assembly system described herein provides use void space gas for initial pressurization of adsorbent bed(s) and thereby increases the overall adsorption efficiency and decreases the size of a system by means of a purge vessel and a surge vessel(s). Surge vessels provide additional system volume for (1) a filter to capture particulates from air source that tend to occlude flow and damage valve components, (2) a sound muffler wherein a sudden changes form a small volume to a large volume dampens sound pressure energy waves, and (3) a heat exchanger wherein additional surface area expels heat of compression in pressurized gas.
Strategic placement of surge vessel includes surrounding rotary valve assembly, i.e., filter vessel for incoming feed fluid between fluid source and valve assembly, between compressor inlet and valve assembly, between compressor outlet and valve assembly and between adsorbent bed and valve assembly.
The rotary valve assembly described herein combines a need for variable process cycle time and variable process step time in an integral assembly for use with PSA or VPSA systems of single or paired adsorbent beds and thereby provides a means for process optimization of any such system.
Yet another advantage of the rotary valve assembly in combination with such a system is the ability to reduce power requirements compared to existing technology. By flowing pressurized gas into a compressor inlet with compressor outlet at atmospheric pressure energy the system recovers energy from previous compressive work on the evacuation step. Likewise, flowing atmospheric pressure air into an evacuated adsorbent bed provides for expansion work and electric motor power reductions. Similarly in a twin cylinder embodiment both compressive and expansive energy recovery are simultaneous and work on the other cylinder, i.e., compressive work imparted to compressor and expansive work imparted to vacuum pump.
Single adsorbent bed vacuum-pressure swing adsorption process, from a starting setting a compressor inlet communicates with ambient air by means of (1) a first aperture of a first valve member, (2) a first aperture of a second valve member and (3) a first through aperture of a third valve member and thereby provides a source of feed gas to the system; and a compressor outlet communicates with an adsorbent bed by means of (1) a second aperture of first valve member, (2) a second aperture of second valve member and (3) a second through aperture of third valve member and thereby provides pressurized air to adsorbent bed.
Upon relative rotation of third valve member to first valve member and second valve member wherein positional coincidence of apertures of first valve member and second valve member are greater than 0° and less than 180° angular degrees, interconnection and communication simultaneously changes and compressor inlet communicates with adsorbent bed by means of (1) second aperture of first valve member, (2) first aperture of second valve member, and (3) first through aperture of third valve member thereby evacuates oxygen depleted gas from adsorbent bed; and compressor outlet communicates with ambient air by means of (1) first aperture of first valve member, (2) second aperture of second valve member and (3) second through aperture of third valve member and thereby provides pressurized oxygen depleted gas to ambient air.
The cycle repeats upon further rotation of third valve member and compressor inlet communicates with ambient air by means of (1) a first aperture of a first valve member, (2) a first aperture of a second valve member and (3) a second aperture of third valve member and thereby provides a source of feed gas; and a compressor outlet communicates with adsorbent bed by means of (1) second aperture of first valve member, (2) and second aperture of second valve member and (3) first through aperture of third valve member and thereby provides pressurized air to an adsorbent bed once again.
A further description provides through apertures of a first valve member and through apertures of second valve member at 45° angular degrees from coincidence of adsorbent bed and compressor outlet interconnection and ambient air compressor inlet interconnection whereby the adsorbent bed aperture of first valve member predominately coincides with the compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 135° angular degrees for pressurization by means of interconnection of first through aperture of third valve member with ambient air and compressor inlet and interconnection of second through aperture of third valve member with adsorbent bed and compressor outlet followed by 45° angular degrees for depressurization wherein first through aperture of third valve member interconnects compressor inlet with adsorbent bed and compressor outlet with ambient air. As a result of adjustable position first valve member and second valve member preference is to the pressurization process step with 75% pressurization and 25% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the compressor outlet with the adsorbent bed and first through aperture of third valve member interconnects compressor inlet with ambient air.
Another description provides through apertures of a first valve member and through apertures of second valve member at 90° angular degrees from coincidence of adsorbent bed and compressor outlet interconnection and ambient air compressor inlet interconnection whereby the adsorbent bed aperture of first valve member equally coincides with the compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 90° angular degrees for pressurization by means of interconnection of first through aperture of third valve member with ambient air and compressor inlet and interconnection of second through aperture of third valve member with adsorbent bed and compressor outlet followed by 90° angular degrees for depressurization wherein first through aperture of third valve member interconnects compressor inlet with adsorbent bed and compressor outlet with ambient air. As a result of adjustable position first valve member and second valve member no preference is to the pressurization process step with 50% pressurization and 50% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the compressor outlet with the adsorbent bed and first through aperture of third valve member interconnects compressor inlet with ambient air.
Another further description provides through apertures of a first valve member and through apertures of second valve member at 135° angular degrees from coincidence of adsorbent bed and compressor outlet interconnection and ambient air compressor inlet interconnection whereby the adsorbent bed aperture of first valve member predominately coincides with the ambient air through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 45° angular degrees for pressurization by means of interconnection of first through aperture of third valve member with ambient air and compressor inlet and interconnection of second through aperture of third valve member with adsorbent bed and compressor outlet followed by 135° angular degrees for depressurization wherein first through aperture of third valve member interconnects compressor inlet with adsorbent bed and compressor outlet with ambient air. As a result of adjustable position first valve member and second valve member preference is to the depressurization process step with 25% pressurization and 75% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the compressor outlet with the adsorbent bed and first through aperture of third valve member interconnects compressor inlet with ambient air.
Example 2Single adsorbent bed pressure swing adsorption process, from a starting setting a compressor inlet communicates with ambient air and a compressor outlet communicates with adsorbent bed by means of (1) a first aperture of first valve member, (2) a first aperture of second valve member and (3) a first through aperture of third valve member and thereby provides pressurized air to an adsorbent bed; and ambient air communicates with ambient air by means of (1) a second aperture of first valve member, (2) a second aperture of second valve member and (3) a second through aperture of third valve member and thereby provides an idle setting.
Upon relative rotation of third valve member to first valve member and second valve member wherein positional coincidence of through apertures of first valve member and second valve member are greater than 0° and less than 180° angular degrees, interconnection and communication simultaneously changes and compressor outlet communicates with ambient air by means of (1) first aperture of first valve member, (2) second aperture of second valve member and (3) first through aperture of third valve member and thereby unloads compressor; and adsorbent bed communicates with ambient air by means of (1) second aperture of first valve member, (2) first aperture of second valve member and (3) second through aperture of third valve member thereby discharges pressurized oxygen deplete gas from adsorbent bed.
The cycle repeats upon further rotation of third valve member and compressor outlet communicates with adsorbent bed by means of (1) a first aperture of first valve member, (2) a first aperture of second valve member and (3) second through aperture of third valve member and thereby provides pressurized air to an adsorbent bed once again; and ambient air communicates with ambient air by means of (1) second aperture of first valve member, (2) second aperture of second valve member and (3) first through aperture of third valve member and thereby provides an idle setting.
A further description provides through apertures of a first valve member and through apertures of second valve member at 45° angular degrees from coincidence of adsorbent bed and compressor outlet interconnection and ambient air and ambient air interconnection whereby the adsorbent bed aperture of first valve member predominately coincides with the compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 135° angular degrees for pressurization by means of interconnection of first through aperture of third valve member with adsorbent bed and compressor outlet and interconnection of second through aperture of third valve member with ambient air and ambient air followed by 45° angular degrees for depressurization wherein first through aperture of third valve member interconnects ambient air with adsorbent bed and compressor outlet with ambient air. As a result of adjustable position first valve member and second valve member preference is to the pressurization process step with 75% pressurization and 25% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the compressor outlet with the adsorbent bed and first through aperture of third valve member interconnects ambient air with ambient air.
Another further description provides through apertures of a first valve member and through apertures of second valve member at 90° angular degrees from coincidence of adsorbent bed and compressor outlet interconnection and ambient air and ambient air interconnection whereby the adsorbent bed aperture of first valve member equally coincides with the compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 90° angular degrees for pressurization by means of interconnection of first through aperture of third valve member with adsorbent bed and compressor outlet and interconnection of second through aperture of third valve member with ambient air and ambient air followed by 90° angular degrees for depressurization wherein first through aperture of third valve member interconnects ambient air with adsorbent bed and compressor outlet with ambient air. As a result of adjustable position first valve member and second valve member no preference is to the pressurization process step with 50% pressurization and 50% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the compressor outlet with the adsorbent bed and first through aperture of third valve member interconnects ambient air with ambient air.
Another further description provides through apertures of a first valve member and through apertures of second valve member at 135° angular degrees from coincidence of adsorbent bed and compressor outlet interconnection and ambient air and ambient air interconnection whereby the adsorbent bed aperture of first valve member predominately coincides with the ambient through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 45° angular degrees for pressurization by means of interconnection of first through aperture of third valve member with adsorbent bed and compressor outlet and interconnection of second through aperture of third valve member with ambient air and ambient air followed by 135° angular degrees for depressurization wherein first through aperture of third valve member interconnects ambient air with adsorbent bed and compressor outlet with ambient air. As a result of adjustable position first valve member and second valve member preference is to the depressurization process step with 25% pressurization and 75% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the compressor outlet with the adsorbent bed and first through aperture of third valve member interconnects ambient air with ambient air.
Example 3Paired adsorbent bed vacuum-pressure swing adsorption process, from a starting setting a first compressor inlet communicates with ambient air, a first compressor outlet communicates with a first adsorbent bed by means of (1) a first aperture of a first valve member, (2) a first aperture of a second valve member and (3) a first aperture of a third valve member and thereby provides pressurized air to a first adsorbent bed; a second compressor inlet communicates with a second adsorbent bed by means of (1) a second aperture of first valve member, (2) a second aperture of second valve member, and (3) a second through aperture of third valve member and thereby evacuates oxygen deplete gas from a second adsorbent bed, and a second compressor outlet provides pressurized oxygen deplete gas from second adsorbent bed to ambient air.
Upon relative rotation of third valve member to first valve member and second valve member wherein positional coincidence of through apertures of first valve member and second valve member are greater than 0° and less than 180° angular degrees, interconnection and communication simultaneously changes and first compressor outlet communicates with second adsorbent bed by means of (1) a first aperture of a first valve member, (2) a second aperture of a second valve member, and (3) a first aperture of a third valve member and thereby provides pressurized air to second adsorbent bed; a second compressor inlet communicates with first adsorbent bed by means of (1) a second aperture of first valve member, (2) a first aperture of second valve member, and (3) a second through aperture of third valve member and thereby evacuates oxygen deplete gas from first adsorbent bed; and second compressor outlet provides pressurized oxygen deplete gas from first adsorbent bed to ambient air.
The cycle repeats upon further rotation of third valve member and first compressor inlet communicates with ambient air, a first compressor outlet communicates with a first adsorbent bed by means of (1) a first aperture of a first valve member, (2) a first aperture of a second valve member, and (3) a second aperture of a third valve member and thereby provides pressurized air to a first adsorbent bed once again; a second compressor inlet communicates with a second adsorbent bed by means of (1) a second aperture of first valve member, (2) a second aperture of second valve member, and (3) a first through aperture of third valve member and thereby evacuates oxygen deplete gas from a second adsorbent bed once again; and a second compressor outlet provides pressurized oxygen deplete gas from second adsorbent bed to ambient air once again.
A further description provides through apertures of a first valve member and through apertures of second valve member at 45° angular degrees from coincidence of first adsorbent bed and first compressor outlet interconnection and second adsorbent bed and second compressor inlet interconnection whereby the first adsorbent bed aperture of first valve member predominately coincides with first compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 135° angular degrees for pressurization of first adsorbent bed by means of interconnection of first through aperture of third valve member with first adsorbent bed and first compressor outlet and interconnection of second through aperture of third valve member with second adsorbent bed and second compressor inlet followed by 45° angular degrees for first adsorbent bed depressurization wherein first through aperture of third valve member interconnects first adsorbent bed with second compressor inlet and second through aperture of third valve member interconnects second adsorbent bed with first compressor outlet. As a result of adjustable position first valve member and second valve member preference is to a first adsorbent bed pressurization process step with 75% pressurization and 25% depressurization and a second adsorbent bed pressurization process step with 25% pressurization and 75% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the first compressor outlet with first adsorbent bed and first through aperture of third valve member interconnects second compressor inlet with second adsorbent bed.
Another further description provides through apertures of a first valve member and through apertures of second valve member at 90° angular degrees from coincidence of first adsorbent bed and first compressor outlet interconnection and second adsorbent bed and second compressor inlet interconnection whereby the first adsorbent bed aperture of first valve member equally coincides with first compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 90° angular degrees for pressurization of first adsorbent bed by means of interconnection of first through aperture of third valve member with first adsorbent bed and first compressor outlet and interconnection of second through aperture of third valve member with second adsorbent bed and second compressor inlet followed by 90° angular degrees for first adsorbent bed depressurization wherein first through aperture of third valve member interconnects first adsorbent bed with second compressor inlet and second through aperture of third valve member interconnects second adsorbent bed with first compressor outlet. As a result of adjustable position first valve member and second valve member no preference is to a first adsorbent bed pressurization process step with 50% pressurization and 50% depressurization or a second adsorbent bed pressurization process step with 50% pressurization and 50% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the first compressor outlet with first adsorbent bed and first through aperture of third valve member interconnects second compressor inlet with second adsorbent bed.
Another further description provides through apertures of a first valve member and through apertures of second valve member at 135° angular degrees from coincidence of first adsorbent bed and first compressor outlet interconnection and second adsorbent bed and second compressor inlet interconnection whereby the first adsorbent bed aperture of first valve member predominately coincides with second compressor inlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 45° angular degrees for pressurization of first adsorbent bed by means of interconnection of first through aperture of third valve member with first adsorbent bed and first compressor outlet and interconnection of second through aperture of third valve member with second adsorbent bed and second compressor inlet followed by 135° angular degrees for first adsorbent bed depressurization wherein first through aperture of third valve member interconnects first adsorbent bed with second compressor inlet and second through aperture of third valve member interconnects second adsorbent bed with first compressor outlet. As a result of adjustable position first valve member and second valve member preference is to a first adsorbent bed depressurization process step with 25% pressurization and 75% depressurization and a second adsorbent bed pressurization process step with 75% pressurization and 25% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects the first compressor outlet with first adsorbent bed and first through aperture of third valve member interconnects second compressor inlet with second adsorbent bed.
Example 4Paired adsorbent bed pressure swing adsorption process, from a starting setting a compressor inlet communicates with ambient air and a compressor outlet communicates with a first adsorbent bed by means of (1) a first aperture of first valve member, (2) a first aperture of second valve member and (3) a first through aperture of third valve member and thereby provides pressurized air to first adsorbent bed; and ambient air communicates with a second adsorbent bed by means of (1) a second aperture of first valve member, (2) a second aperture of second valve member, and (3) a second through aperture of third valve member and thereby provides a means to discharge oxygen deplete gas from second adsorbent bed.
Upon relative rotation of third valve member to first valve member and second valve member wherein positional coincidence of through apertures of first valve member and second valve member are greater than 0° and less than 180° angular degrees, interconnection and communication simultaneously changes and compressor outlet communicates with second adsorbent bed by means of (1) first aperture of first valve member, (2) second aperture of second valve member, and (3) first through aperture of third valve member and thereby pressurizes second adsorbent bed; and first adsorbent bed communicates with ambient air by means of (1) second aperture of first valve member, (2) first aperture of second valve member, and (3) second through aperture of third valve member and thereby discharges pressurized oxygen deplete gas from first adsorbent bed.
The cycle repeats upon further rotation of third valve member and compressor outlet communicates with first adsorbent bed by means of (1) a first aperture of first valve member, (2) a first aperture of second valve member and (3) second through aperture of third valve member and thereby provides pressurized air to first adsorbent bed once again; and ambient air communicates with second adsorbent bed by means of (1) second aperture of first valve member, (2) second aperture of second valve member, and (3) first through aperture of third valve member and thereby discharges oxygen deplete gas to ambient air.
A further description provides through apertures of a first valve member and through apertures of second valve member at 45° angular degrees from coincidence of first adsorbent bed and compressor outlet interconnection and second adsorbent bed and ambient air interconnection whereby the first adsorbent bed aperture of first valve member predominately coincides with compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 135° angular degrees for pressurization of first adsorbent bed by means of interconnection of first through aperture of third valve member with first adsorbent bed and compressor outlet and interconnection of second through aperture of third valve member with second adsorbent bed and ambient air followed by 45° angular degrees for first adsorbent bed depressurization wherein first through aperture of third valve member interconnects first adsorbent bed with ambient air and second through aperture of third valve member interconnects second adsorbent bed with compressor outlet. As a result of adjustable position first valve member and second valve member preference is to a first adsorbent bed pressurization process step with 75% pressurization and 25% depressurization and a second adsorbent bed pressurization process step with 25% pressurization and 75% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects compressor outlet with first adsorbent bed and first through aperture of third valve member interconnects ambient air with second adsorbent bed.
A further description provides through apertures of a first valve member and through apertures of second valve member at 90° angular degrees from coincidence of first adsorbent bed and compressor outlet interconnection and second adsorbent bed and ambient air interconnection whereby the first adsorbent bed aperture of first valve member equally coincides with compressor outlet through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 90° angular degrees for pressurization of first adsorbent bed by means of interconnection of first through aperture of third valve member with first adsorbent bed and compressor outlet and interconnection of second through aperture of third valve member with second adsorbent bed and ambient air followed by 90° angular degrees for first adsorbent bed depressurization wherein first through aperture of third valve member interconnects first adsorbent bed with ambient air and second through aperture of third valve member interconnects second adsorbent bed with compressor outlet. As a result of adjustable position first valve member and second valve member no preference is to a first adsorbent bed pressurization process step with 50% pressurization and 50% depressurization or a second adsorbent bed pressurization process step with 50% pressurization and 50% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects compressor outlet with first adsorbent bed and first through aperture of third valve member interconnects ambient air with second adsorbent bed.
A further description provides through apertures of a first valve member and through apertures of second valve member at 135° angular degrees from coincidence of first adsorbent bed and compressor outlet interconnection and second adsorbent bed and ambient air interconnection whereby the first adsorbent bed aperture of first valve member predominately coincides with ambient air through aperture of the second valve member. Rotation of the of third valve member provides coincidence of 45° angular degrees for pressurization of first adsorbent bed by means of interconnection of first through aperture of third valve member with first adsorbent bed and compressor outlet and interconnection of second through aperture of third valve member with second adsorbent bed and compressor outlet followed by 135° angular degrees for first adsorbent bed depressurization wherein first through aperture of third valve member interconnects first adsorbent bed with ambient air and second through aperture of third valve member interconnects second adsorbent bed with compressor outlet. As a result of adjustable position first valve member and second valve member preference is to a first adsorbent bed depressurization process step with 25% pressurization and 75% depressurization and a second adsorbent bed pressurization process step with 75% pressurization and 25% depressurization of a process cycle time respectively. The cycle then repeats as the second through aperture of third valve member interconnects compressor outlet with first adsorbent bed and first through aperture of third valve member interconnects ambient air with second adsorbent bed.
Water PurifierAlthough various fluids may be suitable for operation of this device, for the purposes of this discussion water shall be the thermodynamic fluid and air the working fluid and zeolite the adsorbent.
Zeolite and water undergo a chemical reaction as follows:
NaxAlx(SiO2)z+nH2O→NaxAlx(SiO2)z.nH2O;
ΔH=−1800 kilojoule per pound zeolite at room temperature; and
ΔG=ΔH−TΔS
ΔH=f(T)
K=−nRT ln [ΔG]
K=[Activity NaxAlx(SiO2)z.nH2O]/([Activity NaxAlx(SiO2)z].[Pressure H2O].
and,
work=−RT ln([P1H2O]/[P2H2O]); where,
R=Gas Constant
T=Temperature
P1H2O=Initial water vapour pressure
P2H2O=Final water vapour pressure.
ΔH=cpΔT
where,
ΔH=change in enthalpy,
cp=heat capacity at constant pressure,
and
ΔT=change in temperature.
Heat requirement to bring zeolite to a temperature where the reaction equilibrium favours formation of water vapour from hydrated zeolite. At such temperature chemical reaction requires addition heat for transformation from hydrate to vapour phase TΔS.
Therefore, through experimentation the equilibrium water vapour pressure and the temperature at which the reaction is no longer spontaneous. Assuming the change in enthalpy is not a strong function of temperature provides a constant value for ΔH of (−1800) kJ per kilogram zeolite for an exothermic reaction between zeolite and water.
Exposing a water source to dry zeolite by means of an evaporator results in energy flow from the surroundings to the system and cooling of the surroundings. When the system reaches equilibrium, the zeolite is saturated and the reaction is complete, thereby stopping evaporation. The zeolite material can be reversibly dried by supplied enough heat to raise the temperature and change the equilibrium of reaction to zeolite and water vapour. The equilibrium temperature depends upon the desired moisture content of the dry zeolite. Elevation of temperature raises the system pressure and enables heat expulsion by means of condensation. Collection of condensate enables use of purified liquid.
Use of the heat of reaction ΔH to support drying of zeolite significantly reduces the total energy requirement. Even if there were no heat losses to the surroundings the ΔH is not enough to complete the reaction as free energy to do work is defined by Gibbs as ΔG=ΔH−TΔS, where ΔH is the sensible irreversible heat of reaction and TΔS the reversible heat of formation of a product species. The entropy of reaction TΔS must also be supplied to the system to complete a reverse or drying reaction. Therefore the thermal inefficiency plus a latent heat are necessary to reverse the reaction. The amount of total heat required to the amount of purified liquid derived is known as the overall efficiency.
The working fluid circulates and facilitates heat transfer but does not enter into the reaction. The evaporative fluid changes state between liquid and vapour in the working fluid and these spontaneous changes result in purification.
Said first adsorbent bed (201c) communicates with said feed reservoir (1011c) by means of an evaporator (101c), a first conduit (410c), a rotary valve assembly (300c) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), first aperture (201) of second valve member (200) and a second conduit (420c).
A second adsorbent bed (202c) communicates to feed reservoir (1011c) by means of a condenser (102c), heat exchanger (103c), a third conduit (430c), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440c) and interconnection of said second aperture (102) of said first valve member (100), second aperture (202) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440c), an expansion valve (501c) with product discharge by means of fifth conduit (450c).
Heat recycles through the system by means of a blower (601c) of in communication with said first adsorbent bed (201c) and second adsorbent bed (202c) and condenser (102c) in communication with feed reservoir (1011c). The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln ([P2H2O]/[P1H2O]). The Coefficient of Performance (“COP”) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said second adsorbent bed (202c) communicates with said feed reservoir (1011c) by means of an evaporator (101c), a first conduit (410c), a rotary valve assembly (300c) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), second aperture (202) of second valve member (200) and a third conduit (430c).
A first adsorbent bed (201c) communicates to feed reservoir (1011c) by means of a condenser (102c), heat exchanger (104c), a second conduit (420c), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440c) and interconnection of said second aperture (102) of said first valve member (100), first aperture (201) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440c), an expansion valve (501c) with product discharge by means of fifth conduit (450c).
Heat recycles through the system by means of a blower (601c) of in communication with said first adsorbent bed (201c) and second adsorbent bed (202c) and condenser (102c) in communication with feed reservoir (1011c). The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln ([P2H2O]/[P1H2O]). The Coefficient of Performance (“COP”) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said first adsorbent bed (201c) communicates with said feed reservoir (1011c) by means of an evaporator (101c), a first conduit (410c), a rotary valve assembly (300c) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), first aperture (201) of second valve member (200) and a second conduit (420c).
A second adsorbent bed (202c) communicates to feed reservoir (1011c) by means of a condenser (102c), heat exchanger (103c), a third conduit (430c), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440c) and interconnection of said second aperture (102) of said first valve member (100), second aperture (202) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440c), a first blower (601c), a fifth conduit (450c), an expansion valve (501c) with product discharge by means of a sixth conduit (460c).
Heat recycle and cooling of the system by means of a first blower (601c) of in communication with said first adsorbent bed (201c) or second adsorbent bed (202c) to assist mass diffusion mechanically. Heat transfer increases by means of direct flow from adsorbing bed to desorbing bed.
The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln([P2H2O]/[P1H2O]). The Coefficient of Performance (COP) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said second adsorbent bed (202c) communicates with said feed reservoir (1011c) by means of an evaporator (101c), a first conduit (410c), a rotary valve assembly (300c) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), second aperture (202) of second valve member (200) and a third conduit (430c).
A first adsorbent bed (201c) communicates to feed reservoir (1011c) by means of a condenser (102c), heat exchanger (103c), a second conduit (420c), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440c) and interconnection of said second aperture (102) of said first valve member (100), first aperture (201) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440c), a first blower (601c), a fifth conduit (450c), an expansion valve (501c) with product discharge by means of a sixth conduit (460c).
Heat recycle and cooling of the system by means of a first blower (601c) of in communication with said first adsorbent bed (201c) or second adsorbent bed (202c) to assist mass diffusion mechanically. Heat transfer increases by means of direct flow from adsorbing bed to desorbing bed.
The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln([P2H2O]/[P1H2O]). The Coefficient of Performance (“COP”) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said first adsorbent bed (201d) communicates with said condensate reservoir (1011d) by means of an evaporator (101d), a first conduit (410d), a rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), first aperture (201) of second valve member (200) and a second conduit (420d).
A second adsorbent bed (202d) communicates to condensate reservoir (1011d) by means of a condenser (102d), heat exchanger (103d), a third conduit (430d), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440d) and interconnection of said second aperture (102) of said first valve member (100), second aperture (202) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440d), an expansion valve (501d) and fifth conduit (450d).
Heat recycles through the system by means of a blower (601d) of in communication with said first adsorbent bed (201d) and second adsorbent bed (202d). The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln([P2H2O]/[P1H2O]). The Coefficient of Performance (“COP”) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said second adsorbent bed (202d) communicates with said condensate reservoir (1011d) by means of an evaporator (101d), a third conduit (430d), a rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), second aperture (202) of second valve member (200) and a first conduit (410d).
A first adsorbent bed (201d) communicates to condensate reservoir (1011d) by means of a condenser (102d), heat exchanger (104d), a second conduit (420d), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440d) and interconnection of said second aperture (102) of said first valve member (100), first aperture (201) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440d), an expansion valve (501d) and fifth conduit (450d).
Said first adsorbent bed (201d) communicates with said condensate reservoir (1011d) by means of a first conduit (410d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), first aperture (201) of second valve member (200), a second conduit (420d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with first through aperture (731d) interconnection of said first aperture (711d) of said first valve member (710d), first aperture (721d) of second valve member (720d), a third conduit (430d), a first heat exchanger (101d) acting as an evaporator and a fourth conduit (440d).
Said second adsorbent bed (202d) communicates with said condensate reservoir (1011d) by means of a fifth conduit (450d), a heat exchanger (103d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with second through aperture (302) interconnection of said second aperture (102) of said first valve member (100), second aperture (202) of second valve member (200), a sixth conduit (460d), a first blower (601d), a seventh conduit (470d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with second through aperture (732d) interconnection of said second aperture (712d) of said first valve member (710d), second aperture (722d) of second valve member (720d), an eighth conduit (480d), a heat exchanger (102d) acting as a condenser, an expansion valve (501d) and a ninth conduit (490d).
Said first rotary valve (300d) communicates with adsorbent beds (201d) and (202d) and provides means to reverse flow as necessary for periodic regeneration of a saturated bed. Said second rotary valve (700d) communicates with said heat exchanger (101d) and heat exchanger (102d) and provides a variable and adjustable means to alternate heat exchanger function from evaporator to condenser. Such alternation of function provides effective means to create a hot or cold space, frost-free evaporator operation and maintain optimal COP.
Process cycle time decreases by means of a first blower (601d) in communication with first adsorbent bed (201d) or second adsorbent bed (202d) to assist mass diffusion mechanically. Heat recycle and cooling of the system by means of a second blower (602d) in communication with said first adsorbent bed (201d) and second adsorbent bed (202d). The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln([P2H2O]/[P1H2O]). The Coefficient of Performance (COP) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said second adsorbent bed (202d) communicates with said condensate reservoir (1011d) by means of a fifth conduit (450d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), second aperture (202) of second valve member (200), a third conduit (430d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with first through aperture (731d) interconnection of said first aperture (711d) of said first valve member (710d), first aperture (721d) of second valve member (720d), a third conduit (430d), a first heat exchanger (101d) acting as an evaporator and a fourth conduit (440d).
Said first adsorbent bed (201d) communicates with said condensate reservoir (1011d) by means of a first conduit (410d), a heat exchanger (103d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with second through aperture (302) interconnection of said second aperture (102) of said first valve member (100), first aperture (201) of second valve member (200), a sixth conduit (460d), a first blower (601d), a seventh conduit (470d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with second through aperture (732d) interconnection of said second aperture (712d) of said first valve member (710d), second aperture (722d) of second valve member (720d), an eighth conduit (480d), a heat exchanger (102d) acting as a condenser, an expansion valve (501d) and a ninth conduit (490d).
Said first adsorbent bed (201d) communicates with said condensate reservoir (1011d) by means of an evaporator (101d), a first conduit (410d), a rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), first aperture (201) of second valve member (200) and a second conduit (420d).
A second adsorbent bed (202d) communicates to condensate reservoir (1011d) by means of a condenser (102d), heat exchanger (103d), a third conduit (430d), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440d) and interconnection of said second aperture (102) of said first valve member (100), second aperture (202) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440d), a first blower (601d), a fifth conduit (450d), an expansion valve (501d) and a sixth conduit (460d).
Heat recycle and cooling of the system by means of a first blower (601d) of in communication with said first adsorbent bed (201d) or second adsorbent bed (202d) to assist mass diffusion mechanically. Heat transfer increases by means of direct flow from adsorbing bed to desorbing bed.
The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ηΔH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln([P2H2O]/[P1H2O]). The Coefficient of Performance (COP) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said second adsorbent bed (202d) communicates with said condensate reservoir (1011d) by means of an evaporator (101d), a third conduit (430d), a rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), second aperture (202) of second valve member (200) and a first conduit (410d).
A first adsorbent bed (201d) communicates to condensate reservoir (1011d) by means of a condenser (102d), heat exchanger (103d), a second conduit (420d), a first rotary valve member (100), a second rotary valve member (200), a third rotary valve (300) member, a fourth conduit (440d) and interconnection of said second aperture (102) of said first valve member (100), first aperture (201) of second valve member (200), second through aperture (302) of third valve member (300), a fourth conduit (440d), a first blower (601d), a fifth conduit (450d), an expansion valve (501d) and a sixth conduit (460d).
Said first adsorbent bed (201d) communicates with said condensate reservoir (1011d) by means of a first conduit (410d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), first aperture (201) of second valve member (200), a second conduit (420d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with first through aperture (731d) interconnection of said first aperture (711d) of said first valve member (710d), first aperture (721d) of second valve member (720d), a third conduit (430d), a heat exchanger (101d) acting as and evaporator and a fourth conduit (440d).
Said second adsorbent bed (202d) communicates with said condensate reservoir (1011d) by means of a fifth conduit (450d), a heat exchanger (103d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with second through aperture (302) interconnection of said second aperture (102) of said first valve member (100), second aperture (202) of second valve member (200), a sixth conduit (460d), a first blower (601d), a seventh conduit (470d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with second through aperture (732d) interconnection of said second aperture (712d) of said first valve member (710d), second aperture (722d) of second valve member (720d), an eighth conduit (480d), a second heat exchanger (102d) acting as a condenser, an expansion valve (501d) and a ninth conduit (490d).
Said first rotary valve (300d) communicates with adsorbent beds (201d) and (202d) and provides means to reverse flow as necessary for periodic regeneration of a saturated bed. Said second rotary valve (700d) communicates with said heat exchanger (101d) and heat exchanger (102d) and provides a variable and adjustable means to alternate heat exchanger function from evaporator to condenser. Such alternation of function provides effective means to create a hot or cold space, frost-free evaporator operation and maintain optimal COP.
Heat recycle and cooling of the system by means of a first blower (601d) of in communication with said first adsorbent bed (201d) or second adsorbent bed (202d) to assist mass diffusion mechanically. Heat transfer increases by means of direct flow from adsorbing bed to desorbing bed.
The thermal efficiency of this system defined as the amount of heat retention from exothermic reaction or ΔηH, where η is thermal efficiency and ΔH the enthalpy of reaction. The heat addition to the system is the reversible heat of chemical reaction TΔS, where T is the temperature of reaction and ΔS the entropy change of reaction, the work of compression of adsorbate vapour and make-up for thermal inefficiency (1−η)ΔH, i.e., Q=(1−η)ΔH+TΔS+RT ln([P2H2O]/[P1H2O]). The Coefficient of Performance (COP) is the cooling or heating power to the input power, Qcondensation/Q or Qevaporation/Q.
Said second adsorbent bed (202d) communicates with said condensate reservoir (1011d) by means of a fifth conduit (450d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with first through aperture (301) interconnection of said first aperture (101) of said first valve member (100), second aperture (202) of second valve member (200), a second conduit (420d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with first through aperture (731d) interconnection of said first aperture (711d) of said first valve member (710d), first aperture (721d) of second valve member (720d), a third conduit (430d), a heat exchanger (101d) acting as and evaporator and a fourth conduit (440d).
Said first adsorbent bed (201d) communicates with said condensate reservoir (1011d) by means of a first conduit (410d), a heat exchanger (103d), a first rotary valve assembly (300d) with a first valve member (100) and a first aperture (101) and second aperture (102) with a rotational angle to a second valve member (200) with a first aperture (201) and second aperture (202) to provide a variable and adjustable process cycle time, a third rotary valve (300) member with second through aperture (302) interconnection of said second aperture (102) of said first valve member (100), first aperture (201) of second valve member (320), a sixth conduit (460d), a first blower (601d), a seventh conduit (470d), a second rotary valve assembly (700d) with a first valve member (710d) and a first aperture (711d) and second aperture (712d) with a rotational angle to a second valve member (720d) with a first aperture (721d) and second aperture (722d) to provide a second variable and adjustable process cycle time, a third rotary valve (730d) member with second through aperture (732d) interconnection of said second aperture (712d) of said first valve member (710d), second aperture (722d) of second valve member (720d), an eighth conduit (480d), a second heat exchanger (102d) acting as a condenser, an expansion valve (501d) and a ninth conduit (490d).
Illustrative embodiments have been described, hereinabove. It will be apparent to those skilled in the art that the above devices and methods may incorporate changes and modifications without departing from the general scope of this invention. It is intended to include all such modifications and alterations in so far as they come within the scope of the appended claims.
Claims
1. A rotary valve comprising:
- a first valve member having a first aperture;
- a second valve member having a second aperture, said first aperture and said second aperture at least partially aligned to define an extent of overlap for receiving and guiding a fluid stream;
- a first driving mechanism;
- a third valve member having a third aperture and disposed between said first valve member and said second valve member, wherein said first driving mechanism drives said third valve member in movement such that said third aperture travels along a path across and beyond said extent of overlap and thereby cooperates with said first aperture and said second aperture for receiving and guiding a fluid stream and wherein said third valve member blocks a passage of fluid between said first aperture and said second aperture through said extent of overlap when said third aperture is at a position along said path spaced from said extent of overlap; and
- a second driving mechanism engaged with one of said first valve member and said second valve member and operable to drive said one of said first valve member and said second valve member in movement to change said extent of overlap.
2. The rotary valve of claim 1 wherein said path is arcuate.
3. The rotary valve of claim 2 wherein said path is circular.
4. The rotary valve of claim 3 wherein said first driving mechanism is operable to selectively drive said third valve member in movement such that said third aperture travels along said path in opposite directions.
5. The rotary valve of claim 4 wherein said extent of overlap is less than half of said path.
6. The rotary valve of claim 1 wherein:
- said first valve member further comprises a fourth aperture;
- said second valve member further comprises a fifth aperture, said fourth aperture and said fifth aperture at least partially aligned to define a second extent of overlap for receiving and guiding a fluid stream;
- said second extent of overlap is positioned along said path; and
- said first driving mechanism drives said third valve member in movement such that said third aperture travels along all said path and passes across and beyond said second extent of overlap and thereby cooperates with said fourth aperture and said fifth aperture for receiving and guiding a fluid stream and wherein said third valve member blocks a passage of fluid between said fourth aperture and said fifth aperture through said second extent of overlap when said third aperture is at a position along said path spaced from said second extent of overlap.
7. The rotary valve of claim 6 wherein further
- said first aperture and said fifth aperture are at least partially aligned to define a third extent of overlap for receiving and guiding a fluid stream;
- said third extent of overlap is positioned along said path; and
- said first driving mechanism drives said third valve member in movement such that said third aperture travels along all said path and passes across and beyond said third extent of overlap and thereby cooperates with said first aperture and said fifth aperture for receiving and guiding a fluid stream and wherein said third valve member blocks a passage of fluid between said first aperture and said fifth aperture through said third extent of overlap when said third aperture is at a position along said path spaced from said third extent of overlap.
8. The rotary valve of claim 7 wherein:
- said fourth aperture and said second aperture are at least partially aligned to define a fourth extent of overlap for receiving and guiding a fluid stream;
- said fourth extent of overlap is positioned along said path; and
- said first driving mechanism drives said third valve member in movement such that said third aperture travels along all said path and passes across and beyond said fourth extent of overlap and thereby cooperates with said fourth aperture and said second aperture for receiving and guiding a fluid stream and wherein said third valve member blocks a passage of fluid between said fourth aperture and said second aperture through said fourth extent of overlap when said third aperture is at a position along said path spaced from said fourth extent of overlap.
9. The rotary valve of claim 8 wherein said third valve member further comprises a sixth aperture and wherein said first driving mechanism drives said third valve member in movement such that said sixth aperture travels along said path and thereby places one of said first and fourth apertures in fluid communication with one of said second and fifth apertures.
10. The rotary valve of claim 1 wherein said second valve member further comprises a seventh aperture, said first valve member being moveable by said first driving mechanism to selectively position said first aperture and said second aperture into at least partial alignment to define said extent of overlap or to position said first aperture and said seventh aperture into at least partial alignment to define a fifth extent of overlap for receiving and guiding a fluid stream.
11. The rotary valve of claim 1 wherein said first and second apertures are C-shaped in cross-section.
12. The rotary valve of claim 1 wherein said second driving mechanism includes a reversible electric motor.
13. The rotary valve of claim 1 wherein said second driving mechanism includes a synchronous electric motor.
14. The rotary valve of claim 1 wherein said second driving mechanism is further defined as including a detent mechanism.
15. The rotary valve of claim 1 wherein said second driving mechanism is further defined as including a clutch operably engaged with said first driving mechanism.
16. A method of valving comprising the steps of:
- at least partially aligning a first aperture of a first valve member with a second aperture of a second valve member to define an extent of overlap for receiving and guiding a fluid stream;
- disposing a third valve member having a third aperture between the first valve member and the second valve member;
- driving the third valve member for movement with a first driving mechanism such that the third aperture travels along a path across and beyond the extent of overlap and thereby cooperates with the first aperture and the second aperture for receiving and guiding a fluid stream and wherein the third valve member blocks a passage of fluid between the first aperture and the second aperture through the extent of overlap when the third aperture is at a position along the path spaced from the extent of overlap; and
- driving one of the first valve member and the second valve member in movement with a second driving mechanism engaged with one of the first valve member and the second valve member to change the extent of overlap.
17. The method of claim 16 wherein said driving the third valve member is further defined as:
- driving the third valve member continuously such that the first aperture and the second aperture are repeatedly blocked from communicating with one another.
18. The method of claim 17 wherein said driving the third valve member is further defined as:
- driving the third valve member at a constant speed such that the first aperture and the second aperture are blocked from communicating with one another at regular intervals.
19. The method of claim 16 wherein said driving the third valve member is further defined as:
- driving the third valve member at different speeds such that the first aperture and the second aperture are repeatedly blocked from communicating with one another at irregular intervals.
20. A combination comprising:
- said rotary valve of claim 1;
- a first fluid passageway extending between first and second ends with at least one of said first and second ends disposed in fluid communication with said rotary valve;
- at least one fluid flow generators disposed at a position along said first fluid passageway;
- a second fluid passageway extending between first and second ends with at least one of said first and second ends disposed in fluid communication with said rotary valve;
- a first reservoir disposed at a position along said first fluid passageway;
- a third fluid passageway extending between first and second ends with at least one of said first and second ends disposed in fluid communication with said rotary valve; and
- a second reservoir disposed at a position along said first second passageway.
Type: Application
Filed: May 25, 2012
Publication Date: Nov 15, 2012
Inventor: Gregory A. Michaels (Seven Hills, OH)
Application Number: 13/480,593
International Classification: F16K 5/00 (20060101);