Metering Pump
A fluid metering pump is provided having reciprocating pumps including a first fluid displacer and a second reciprocating pump include a second fluid displacer. A transmission and stroke adjuster assembly for couples a prime mover to each of said first and said second fluid displacers and converting a rotary movement of the prime mover into a reciprocating stroke movement of said first and said second fluid displacers resulting in a continuous fluid flow free of fluid pulsing.
This application claims the benefit of U.S. Provisional Application No. 61/381,996, filed Sep. 12, 2010, the entire of which is incorporated herein by reference.
FIELD OF THE INVENTIONThe present invention relates generally to positive displacement pumps, and more particularly, metering pump that provides a continuous fluid flow of an adjustable volume.
BACKGROUND OF THE INVENTIONMetering pumps are commonly used to pump fluids when fluid flow rate must be precise and adjustable. The term “metering pump” is based more on the use of the pump rather than the actual type of the pump used. There are several classes of pumps that are typically used to meter fluids, including piston, diaphragm and peristaltic pumps. Each of these classes of pumps include a pump head and a motor that is operatively connected to the pump head to drive the pump head to pump or meter a fluid to a desired delivery location at a precise and adjustable flow rate. Further, pump heads may be classified as a loss-motion type or a no loss motion type. A loss-motion pump has a discontinuous positive fluid displacement during a fluid displacer's discharge stroke, whereas a no loss motion pump has a continuous positive fluid displacement. For the purpose herein, the invention is generally concerned with piston or diaphragm no loss motion type pumps or the like.
Conventional piston or diaphragm metering pump are well known in the art, and accordingly, a complete description of such is not warranted here for an understanding of the embodiments of the invention. However, in the basic concept a piston or diaphragm or the like may be termed as a fluid displacer that is moved within a housing having a pump cavity into which the fluid displacer is disposed. The displacer is reciprocated within the pump housing to create and collapse the volumetric size of the cavity. There is set of check valves or other form of valves located on the suction and discharge sides of the pump housing. The valves are so designed to allow the creation and collapsing of the cavity or chamber to create liquid displacement. The valve operational timing is so designed to isolate the differential pressure across the pump housing during its normal operation. The displacer within the pump housing is mechanically or mechanically hydraulically connected to some of transmission. Typically an electric motor applies rotary motion to the transmission to operate the metering pump and cause displacement.
Conventionally, the transmission includes an eccentric member that converts rotary motion to reciprocating motion. The transmission will have a form of mechanics for speed ratio and torque adjustment. There are other various ancillary components of common art within the pump to make a fully operational metering pump. They will have some form of mechanics or hydraulics to change the stroke length. Conventional no-loss pumps typically utilize eccentric members that create sinusoidal motion or similar to a sinusoidal motion for their reciprocating motion. These forms of reciprocating motion when applied to a duplex pump design cannot create sufficient substantially continuous non-pulsating displacement. The liquid being pumped always has period of zero velocity across the pump. This will cause undesirable pulsating liquid flow rates. They typically do not create the preferred continuous displacement motion of the invention.
Various electronic solutions have been proposed and utilized to reduce or eliminate the undesirable pulsating liquid flow rate. In one solution a synchronous motor is used to driver the displacers which are modulated through control electronics to control the fluid flow rate and reduce pulsing. Other solutions include digital controlled solenoid driven pumps which have been successful to a point in producing non-pulsating liquid flow rates. However, they have limited flow rates and pressures limitations due to the limitations of solenoid technology. They cannot create true continuous fluid flow at certain flow rates and fluid pressure.
There are a number of duplex mechanical metering pumps that incorporate continuous non-pulsating flow rate and incorporate mechanical stroke length modulation. A few use barrel cams, because they can create substantially uniform constant velocity stroke motion. When applied to two or more displacers they can create substantially uniform liquid flow rates. One example of a duplex pump utilizes a form of barrel cam style mechanical member. It can create continuous low pulsating flow rates. The stroke modulation is not integral. It is an added mechanical hydraulic mechanism. This adds extra components and complexity to its design and has not been readily accepted by the market. Another mechanical pumps may utilize a barrel cam, but do not have a stroke adjustor. As discussed above, there is exists digitally controlled synchronous motor driven metering pumps that have accomplished non-pulsating flow rates. They can create substantially non-pulsating flow rates, but current commercially offerings do not create substantially continuous flow rate delivery. They can achieve wide flow rate turn down creation as required for metering pumps They tend to be limited by cost and complexity. Embodiments, of a duplex version of the invention can deliver substantially or sufficient continuous flow rate delivery and low pulsations being imposed upon the pumped liquid. This preferred flow delivery is sustained through its zero to 100% stroke length modulation.
Various manufacturers produce pumps with single “simplex” or multiple pump heads “duplex”. Each pump head has a batch delivery of liquid displacement. Each batch is always defined by a two moments of zero liquid displacement with liquid displacement between those moments. These zero liquid displacement moments for each batch causes the liquid being displaced across the pump to go from a position of rest to high rates of velocity over very small increments of time back to a position of rest.
The all mechanical single and duplex pumps of common art typically create non-linear, non-proportional and non-continuous liquid flow rates during their normal operation. The more commonly sold pumps of common state of art require at least three or more displacers to create continuous liquid flow rates. Pumps that utilize three or more displacers can be phased to create a more substantially constant velocity across the pump at any given rotational speed. There is prior art for two displacers creating continuous flow rates. The invention can be designed for three or more displacers with integral stroke length modulation.
The physics of metering pumps is that they create batch flow rates. Each displacer displaces a given batch volume of liquid for each displacement cycle. The current state of art typically has the liquid being pumped going from zero velocity at the beginning of a batch to peak velocity and back to zero at the end of the batch. This causes negative pulsating liquid flow rates. This is transferred to the liquid up-stream and down-stream of the pump. This sudden change in liquid velocity creates mass acceleration problems applied to the liquid being pumped. It can create what is commonly called water hammer or cavitation. This is due to the sudden stopping of the liquid on the suction side of the pump at an end of a batch cycle. This causes a resultant high pressure to be enacted upon the pumped liquid on the suction side of the pump. This is due to the liquid on the suction side being a mass in motion that wants to stay in motion, but is suddenly stopped. At the end of a batch cycle the liquid pumped to the discharge side of the pump goes to zero velocity. The liquid has motion and tends to continue in motion. The sudden loss in liquid velocity causes a low pressure to be enacted upon the liquid at the discharge side of the pump. This process is repeated many times per minute. This occurs on the majority of applications of the current state of art for simplex and duplex metering pumps. A typical duplex pump has two batch liquid flows per revolution, but the pulsating flow remains. These negative flow characteristics are imparted to the liquid being pumped from the source to the point of application. Typically the source is a tank at a given distance to the pump. The application point is at given distance from the pump. These negative hydraulics characteristics created by the pump are transferred to the entire pumping system. The result is pulsating flow rates are transferred to the entire pumping system. This cause many negative issues. The invention shares these negative liquid hydraulics characteristics local at its suction and discharge at each of its reciprocating pump. Unlike the common art, the invention with two displacers can create substantially net constant liquid velocity across the pump. This is unlike the typical common art for a duplex pump with integral mechanical stroke adjustor. The overall pumping system is exposed minimal or virtually no pulsating liquid flow rates.
Typically the manufacturers of current state of art metering pumps recommend accessories to remedy the associated problems created by pulsating flow rates. If these accessories are not applied the pump may not operate properly and could cause a failure of the pump and pumping system. The typical solution to pulsating flow rates is the addition of peripheral equipment such as a back pressure valve and pulsation dampener or accumulator. They typically sufficiently mitigate the severity of the pulsating liquid flow rate. The addition of the pulsation dampener adds costs and complexity for a complete installation of a pumping system. It also adds its own set of maintenance issues. This same pulsating flow typically inherent in the current state of art of duplex metering pumps can cause liquid siphoning across the pump. This tends to negate the proper functioning of the check valves. It also can create the discharge piping to vibrate and be mechanically stressed. The recommend accessory to mitigate the problem is a back pressure valve. The valve is located on the discharge side of the pump. This creates enough pressure resistance to force the check valves to properly seat and to assure a satisfactorily operating pump. The back pressure valve reduces the potential for liquid siphoning across the pump. Some process applications have sufficient minimum back pressure to negate the requirement for a back pressure valve. It is typical for the pump manufacture to recommend the installation of the back pressure valve as a precaution of the potential problems. The back pressure valve adds costs and its own set of problems. The invention as a duplex pump creates sufficiently continuous low pulsating flow rates that it eliminates the need for pulsation dampeners or accumulators. In addition it further reduces the applications that would require a back pressure valve if certain minimum back pressure value is present.
There are process applications that utilize a flow meter in close proximity to these pumps that approximately verify that the pump is delivering the desired volumetric liquid required. They are at times used, but are more limited due to the typical pulsating flow for the duplex pumps of the current common art. Pulsating liquid is more difficult for a flow meter to accurately measure. Flow meters are typically calibrated with constant liquid head conditions at different constant liquid velocities. The typical state of art for duplex metering pumps with integral mechanical stroke adjustor do not create constant liquid velocities or constant head conditions. That is due to their pulsating flow rates that create variable liquid velocities. The variable liquid flow rate velocities cannot create constant head conditions on the suction and discharge sides of the pump. This virtually assures that the flow meter cannot measure the pumped liquid output to the stated accuracy and repeatability of the flow meter. This assures an accuracy offset that cannot be fully resolved. It would be desirable to pair a flow meter for verification, certification and calibration to national and international standards of a duplex metering pump. That is to match the flow rate creation of the metering pump to the flow meter. These international bodies such as the National Institute of Standards and Technology “NIST” a US based third party and outside the US such as DKD, NABL and others. Most manufacturers of higher accuracy flow meters calibrate to one or more of these recognized third party standards. All of these international flow calibration institutes, which certify to traceable internationally accepted standards, require constant liquid velocities. This constant liquid velocity is consistent with constant positive pressure of the inlet flow that is constant head of the source liquid. These third parties have developed measurement standards that allow manufacturers to assign quality controlled traceability of their calibration procedures. The manufacture can then state that their flow meters conform to a specific body of standards. Their flow meters will have a traceable accuracy and repeatability to a specific standard. The flow meter can claim a pedigree to a transferable standard. For example the flow meter would state that their flow meters are NIST traceable. The pulsating flow characteristics of the common art for duplex pumps tend to limit the use of flow meters, although they are used. The invention as a duplex pump can be calibrated to NIST or one of the other standards organizations requirements for transferability of pedigree. That is done by paring the suction or discharge side of the pump to a traceable flow meter. The invention as a duplex pump will be operated at fixed speeds and stroke length. The momentary produced flow creation of the invention will be compared to the momentary flow rate of the calibration flow meter. This comparison will create a calibration curve data sheet that will be certifying the traceability of the invention to a pedigree flow meter. The pedigree of the flow meter is transferred to the invention. No duplex metering pump of current art is claiming the ability to be calibrated to NIST, DKD, NSBL or any other like type standard. The invention with two displacers creates sufficiently continuous non-pulsating flow rates at substantially constant liquid velocities. These created substantially constant liquid velocities by the invention allow for a constant head creation in a close loop calibration rig. This means that the calibration requirement to these international bodies' standards for flow meter calibrations is transferrable to the invention. This compatibility of hydraulics allows the invention to be certified to any one of these standards and will be so claimed. This will give a more accurate and true verification of the pump's accumulated liquid flow rates over time as compared to the state of art. This also allows for more accurate momentary flow rate verification between the invention and a properly installed flow meter. There seems to be no traceable certified metering pump commercially available as of this filing.
A typical scenario for use of a metering pump is to add one liquid to another at a controlled desired continuous proportional ratio. Proper mixing allows for the optimum homogeneity and combines the two or more liquids. As common to the state of art for metering pumps they deliver pulsating liquid flow rates even with two displacers. This reduces the ability to achieve highly homogenous blends between two or more constituents or chemicals. The invention would allow for an optimum ratio of two or more liquids. This is due to the ability to have virtually one constant liquid velocity being combined to another virtually constant velocity liquid. The invention can maintain a fixed pumped flow rate delivery. The flow rate delivery by the pump is constant and if the primary chemical flow rate is constant then the invention can maintain a substantially constant fixed ratio. This is not achieved in the current state of art for duplex metering pumps. There are many industries that desire this ability.
Common to all metering pumps as with the invention is the need for some form of valves to be used to operate. The most common are ball check valves. Other types substitute the ball for cones or discs. Under certain conditions the check valves the balls, cones or discs can float off their seats when the pump is not operating. This allows for the source liquid to the suction side of the pump to flow across the pump. The source liquid is typically from a tank and under certain conditions the pump will drain the tank. This is commonly due to an operator error. The invention has an option for seating the diaphragms in their respective pump housing. This can be manually activated by an operator or automatically activated. This option is most effective when it is on the invention that has the smart electronics with the motor driven stroke adjustor. This automatic option would be programmed into the pump so that when the pump is shut-off or in stand-by it will seat its diaphragms before stopping. This assures that the pump will not allow the liquid to leak across the pump.
There does not seem to be common art for the ability of duplex or more displacer metering pump to mechanically engage and disengage a displacer in the field. This ability would allow for greater flow rate turn down, flexibility in manufacturing and field modification. The invention incorporates allow for an optional mechanical diaphragm engagement pin and mechanism for each driven diaphragm. This allows for a pump to be converted to a simplex pump to a duplex by adding a second pump housing in the field.
Any pump that does not produce continuous flows will have non-continuous torque demand to operate. This means that the torque demand will have peaks that require greater torque to operate at the peaks. For example a pump of common art that produces a sinusoidal volumetric displacement will have that peak torque of the sine curve. This means that a larger motor will be required to meet peak torque demands. The larger motor will require more current to operate. The non-continuous flow rate pumps will typically consume more power to operate than a continuous flow rate pump during its normal operation. The invention would typically have a smaller motor for any given volumetric displacement over the state of art of metering pumps
SUMMARY OF THE INVENTIONEmbodiments of the present invention address and overcome the drawback of existing no-loss motion reciprocating metering pump by providing a metering pump including a transmission and stroke modulation assembly that provides a continuous and adjustable fluid flow without fluid pulsation.
Embodiments of the present invention also provide a metering pump including a transmission and stroke modulation assembly including three-dimensional, variable profile conjugate cams.
Embodiments of the present invention also provide a metering pump including a transmission and stroke modulation assembly that permits conversion between simplex and duplex pump configurations.
Embodiments of the present invention also provide a metering pump including a transmission and stroke modulation assembly that prevents fluid flow across the pump during non-operational periods
Embodiments of the present invention also provide a metering pump including a transmission and stroke modulation assembly that can be calibrated to a flow meter with constant head at a given constant velocity.
Embodiments of the present invention also provide a metering pump that can be calibrated to a flow meter with constant head at a given constant velocity
To achieve these and other advantages, in general, in one aspect, a fluid metering pump is provided. The fluid metering pump includes a first reciprocating pump have a first fluid displacer, a second reciprocating pump having a second fluid displacer and a transmission and stroke adjuster assembly for coupling a prime mover to each of the first and the second fluid displacers and converting a rotary movement of the prime mover into a reciprocating stroke movement of the first and the second fluid displacers. The transmission and stroke adjuster assembly includes a driven shaft rotatable about an axis of rotation, first and second three-dimensional cam members mounted to the driven shaft for conjoined rotation therewith, the first and second cam members are congruent with respect to one another, a first pair of followers in contact with the first cam member on opposite sides thereof, the first pair of followers connected to the first fluid displacer and imparting a reciprocating motion on the first fluid displacer during rotation of the driven shaft, a second pair of followers in contact with the second cam member on opposite sides thereof, the second pair of followers connected to the second fluid displacer and imparting a reciprocating motion on the second fluid displacer during rotation of the driven shaft, and, wherein the first cam member and the second cam member each have a non-cardioid shape cam profile that results in a constant velocity reciprocation motion of the first and second pair of followers during rotation of the driven shaft.
There has thus been outlined, rather broadly, the more important features of the invention in order that the detailed description thereof that follows may be better understood and in order that the present contribution to the art may be better appreciated.
Numerous objects, features and advantages of the present invention will be readily apparent to those of ordinary skill in the art upon a reading of the following detailed description of presently preferred, but nonetheless illustrative, embodiments of the present invention when taken in conjunction with the accompanying drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein are for the purpose of descriptions and should not be regarded as limiting.
The following drawings illustrate by way of example and are included to provide further understanding of the invention for the purpose of illustrative discussion of the embodiments of the invention. No attempt is made to show structural details of the embodiments in more detail than is necessary for a fundamental understanding of the invention, the description taken with the drawings making apparent to those skilled in the art how the several forms of the invention may be embodied in practice. Identical reference numerals do not necessarily indicate an identical structure. Rather, the same reference numeral may be used to indicate a similar feature of a feature with similar functionality. In the drawings:
In
Each reciprocating pump 101a and 101b include fluid suction ports 150a and 150b, respectively, and fluid discharge ports 152a and 152b, respectively. Fluid suction ports 150a and 150b are configured to be connected to a source of fluid by suitable fluid carrying conduits or the like. Fluid discharge ports 152a and 152b are configured to be connected suitable fluid carrying conduits for the delivery of the pumped fluid. As it will be further described below, reciprocating pumps 101a and 101b include access ports 110a and 110b, respectively, that permit an operator access to the driven shaft connected to each respective fluid displacer for either the engagement or disengagement of the fluid displacer from its driven shaft to enable or disable the operation of the respective fluid displacer. To this end, the representatively illustrated duplex pump head 114 may be converted between a simplex configuration and a duplex configuration.
In
With initial reference to
Further illustrated in
Turning to
The transmission and stroke assembly 90 of pump 114 utilizes aspects of co-pending U.S. patent application Ser. No. 13/084,086, the entirety of which is incorporated herein by reference. In
Each cam 52 and 54 are congruent geometries that are properly integrated to create a conjugate cam assembly 50. The cam surface areas 53 of cams 52 and 54 have an area along the dimension “Y” that is expanded from a position of no displacement to maximum displacement to one direction along “Y”. To the opposite direction from a position of no displacement for both cams 52 and 54 begins a tapered outward area 107 about the center 36. These two tapered areas 107 expand their surface areas 53 and gradually expand to approach the surface areas 112 for each congruent cam 52 and 54. The cams 52 and 54 circular surface areas 112 are expanded surface areas about the center 36. This surface area of 112 for each cam 52 and 54 shall have a radius greater than the most eccentric position along the cam profile 53. These surface areas 112 expand the
The stroke adjustor frame 70, stroke adjustor rod 76 and arms 72 comprise the stroke adjustor assembly 94 that fits into the cam assembly frame 68. The cam stroke adjustor shaft 76 has a drive gear 121. That drive gear has internal threads 123 not detailed. Gear 121 interacts with a worm gear and shaft 119. The stroke adjustor knob 104 not shown is connected to the shaft 119. The cam assembly 50, drive gear 62 and the motor drive shaft 58 comprise the major components for the driven cam assembly 92. The drive shaft gear 62 meshes with the worm gear drive shaft 116. The worm gear drive shaft is connected to the drive motor (not shown) that is mounted to motor flange mount 105 not shown. There would be some form of coupling between 116 and the motor shaft not shown. The follower assembly 88 is comprised of 82a and 82b of 82, diaphragm drive shafts 12a and 12b, spherical bearings two 84a and two 84b, springs 127 and four bolts 96. In addition the sphere bearings 84a and 84b shown as detail “D” are constrained by contact to small ball bearings 126 that are held in place the flat bearing race 125. That is held in place by flanged diaphragm shafts 12a and 12b. This supports the sphere bearings 82a and 82b and allows them to rotate.
The follower holder assembly 82 has two pieces 82a and 82b. The holder assembly 82 confines the four bearings of two pairs of 84a and 84b. When the bolts 96 attach the two cam follower haves 82a and 82b the four bolts 96 pass through springs 127 through both 82a and 82b and 12a and 12b. There are four or eight springs 127 depending on design and are held in compression between each cam follower plates 12a or 12b and the head of bolt heads 96 and their nuts (not shown). Certain designs may incorporate external springs to accomplish the same effect of springs 127. This configuration maintains the sphere bearings 84a and 84b to stay in contact with the cam surface 50. The sphere bearings 84a and 84b are mechanical connected to each cam follower half 82a and 82b that is positively connected to flanged diaphragms shafts 12a and 12b. This is true when each cam follower 82a or 82b is expanding away from the center 36 and a diaphragm 106 is displacing. When a diaphragm 106 is in return and creating a cavity the spring 127 forces have to be sufficient to pull back the diaphragms 106 as if 12a or 12b were joined rigid. That is that the follower 82 was one solid piece. The springs 127 allow for manufacturing tolerances and to allow the diaphragms to be expanded outward during hydraulic shut-off. As depicted in the drawings the spherical ball 84a and 84b are incorporated in this design, but it can be of a different design, such as rollers. The spherical geometry is the simplest to design, but may have practical design limitations that a cylindrical roller would solve. The follower assembly holder 88 encapsulates the cam assembly 50.
The cam follower assembly 88 is continuously constrained by its tangents 44 to the surface area profiles 53 of the conjugate cams 52 and 54. The cam follower assembly 88 is further constrained by the connector shafts 12a and 12b being held in rigid alignment within the linear bearings 64. This combination of two defined mechanical constraints holds the cam follower 88 assembly in proper position. As shown on
Operationally when the Pump's motor not shown rotates the worm gear drive shaft 116 it turns the geared drive shaft 62 that in turn rotates its integral drive shaft 58 that in turn rotates the cam assembly 50. The shaft 58 and the cam assembly 50 are constrained to rotate together due to their splined relationship of 57 and 59. The follower assembly 88 is encapsulating the cam assembly 50 to assure constant tangents of the sphere bearings 84a and 84b to cam assembly 50. The cam assembly 50 is free to laterally move on shaft 58. The rotation of the cam assembly 50 will impart the reciprocating motion to the follower assembly 88. This reciprocating motion would be prescribed by the conjugate cam's 52 and 54 profiles 53. That is the resultant tangents of sphere bearings 84a and 84b at that cam profile 53 at planes 100 will impart a prescribed reciprocating motion to the follower 88. The theoretical planes 100 move lateral with the centers of bearings 84a and 84b. The form of reciprocating motion will be as described herein this writing. The motion will be transferred to the diaphragm shafts 12a and 12b. In turn transferred to the diaphragms 106. As the motor drives the invention each diaphragm 106 creates batch displacement. The properly phased summation of the two batch displacements will create very low or non-pulsating continuous liquid flow rates. The pump 114 liquid displacement will be as shown and described in
From the above description advantages of embodiments of the invention herein are readily recognized by those skilled in the field of the invention. Alternative embodiments are possible. In an alternative embodiment, conventional prime mover control electronics and prime mover control methods may be employed. In such an embodiment, the stroke control of the diaphragms may be automated by replacing the control knob 104 with an electric motor that is interfaced with the prime mover control electronics. To this end, the stroke length may be adjust remotely in a similar manner to conventional methods of remotely controlling the prime mover through the control electronics and an established communication link between the control electronics and a remotely located controller or computer interface. In another alternative embodiment, the diaphragms could be replaced with pistons or other reciprocating displacement mechanisms. In another alternative embodiment, three or reciprocating pump containing displacers (diaphragms, pistons, or the like) may be phased about the pump in order to overlap suction and discharge phases, e.g. to have 240° of suction and 120° of discharge for each diaphragm. It would be provide continuous non-pulsating flow rates. It can be built as a four diaphragm pump for additional capacity with the same features as the duplex embodiment. Other embodiments are also possible within the scope of the invention and the claims.
Claims
1. A fluid metering pump comprising:
- a first reciprocating pump including a first fluid displacer;
- a second reciprocating pump include a second fluid displacer
- a transmission and stroke adjuster assembly for coupling a prime mover to each of said first and said second fluid displacers and converting a rotary movement of the primer mover into a reciprocating stroke movement of said first and said second fluid displacers;
- said transmission and stroke adjuster assembly including:
- a driven shaft rotatable about an axis of rotation;
- first and second three-dimensional cam members mounted to said driven shaft for conjoined rotation therewith, said first and second cam members are congruent with respect to one another;
- a first pair of followers in contact with said first cam member on opposite sides thereof, said first pair of followers connected to said first fluid displacer and imparting a reciprocating motion on said first fluid displacer during rotation of said driven shaft;
- a second pair of followers in contact with said second cam member on opposite sides thereof, said second pair of followers connected to said second fluid displacer and imparting a reciprocating motion on said second fluid displacer during rotation of said driven shaft; and
- wherein said first cam member and said second cam member each have a non-cardioid shape cam profile that results in a constant velocity reciprocation motion of said first and second pair of followers during rotation of said driven shaft.
2. The metering pump of claim 1, wherein said first and second pair of followers are longitudinally positional across the cam profile of said first cam member and across the cam profile of said second cam member, respectively, and wherein the longitudinal position of said first and said second pair of followers relative to the cam profile of said first cam member and the cam profile of said second cam member, respectively, varies the stroke length of said first and said second pair of followers between a minimum stroke length and a maximum stroke length.
3. The metering pump of claim 1, further comprising:
- a first intermediate shaft connecting said first pair of followers and said first fluid displacer; and
- a second intermediate shaft connecting said second pair of followers and said second fluid displacer.
4. The metering pump of claim 3, wherein said first intermediate shaft is split shaft comprising two interconnectable shaft portions; and wherein said second intermediate shaft is a split shaft comprising two interconnectable shaft portion.
5. The metering pump of claim 1, wherein said first and said second fluid displacers are each diaphragms.
6. The metering pump of claim 2, wherein said first and second cam members are mounted to said driven shaft for axial translation along said driven shaft; and
- wherein transmission and stroke adjuster assembly further includes:
- a stroke adjuster frame supported for translation in a direction along said rotational axis of said driven shaft, said stroke adjuster frame connected to said first and said second cam members for conjoined translational movement therewith, wherein translational movement of said stroke adjuster frame causes an equal translational movement of said first and second cam members along said driven shaft.
Type: Application
Filed: Sep 12, 2011
Publication Date: Mar 15, 2012
Inventor: Dennis Parker (Lakeland, FL)
Application Number: 13/230,032
International Classification: F04B 49/12 (20060101);