Heat exchanger
Disclosed herein is a heat exchange apparatus, which comprises a hollow blade member having a first fluid inlet and a first fluid outlet and a first fluid passageway for a first fluid that extends between the inlet and the outlet. The blade member is sized and shaped to be located in a second fluid passageway for a second fluid. The blade member is configured to enhance thermal energy transfer between the fluids as they flow along their respective passageways.
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This application claims the benefit of the filing dates of U.S. provisional patent application Ser. No. 60/964,658, filed Aug. 14, 2007; U.S. provisional patent application Ser. No. 60/994,039, filed Sep. 17, 2007; U.S. provisional patent application Ser. No. 61/008,766, filed Dec. 21, 2007; and U.S. provisional patent application Ser. No. 61/134,666, filed Jul. 11, 2008, the disclosures of which are hereby incorporated herein by reference.
FIELD OF THE INVENTIONThe present invention concerns heat exchangers, and more particularly to blade-type heat exchangers for recovering heat from fluids.
BACKGROUND OF THE INVENTIONHeat exchangers are well-known and widely used in a number of environments to recover thermal energy from fluids. The thermal energy, if not recovered, would be lost to the environment. Generally speaking, heat exchangers work by transferring heat from one fluid to another via a solid wall, which separates the two fluids. This straightforward principle has been used to recover heat from waste water (so called “grey water”) in, for example, household shower and bath systems. A number of designs of heat exchangers that have been used with household shower/bath systems are described as follows.
U.S. Pat. No. 5,143,149 issued to Kronberg on Sep. 1, 1992 concerns a heat recovery system that includes a heat exchanger and a mixing valve. The heat exchanger appears to include a drain trap with an inner coiled tube, a baffle plate and a waste water outlet. The inner coiled tube includes a cold water inlet and a pre-heated water outlet in fluid communication with each other and is coiled around the inside wall of a cylindrical member. A waste water inlet is located in the drain trap such that waste water enters the cylinder through the inlet, contacts the baffle plate and is deflected away from a solid central portion towards a perforated outer region such that the waste water gradually moves downwardly through the cylinder until it reaches the bottom. Cold water located in the coiled tube moves in a generally upward direction opposite to the waste water as it flows downwardly over the coiled tube to heat the cold water. Heat exchange appears to take place through the walls of the coiled tube. The heated water then exits the heat exchanger via the outlet. The design is simple and relies on the counter-flow principal of heat exchange across a thermally conductive wall of the coiled pipe. While this apparatus uses the heat from waste drain water to heat cold water via a heat exchanger, it does so by direct contact of the waste water with the coiled cold water tube.
U.S. Pat. No. 4,821,793 issued to Sheffield on Apr. 18, 1989 discloses a tub and shower floor heat exchanger in which a heat exchanger cover is supported on the tub floor by a number of supports, each having an opening therein. The heat exchanger cover is disposed away from the tub floor and includes a gap between the cover and the tub floor. A heat exchange tube is connected to a cold water supply line, the heat exchange tube being arranged directly beneath the heat exchanger cover. Water flowing from a shower head strikes the tub bottom and, as waste water flows towards a drain hole, it is forced back and forth over an extended path by means of the supports which serve as a baffle system. As the waste water moves through the baffle system it moves through the openings and is maintained in a heat exchange relationship with the heat exchange tube over an extended period of time, thereby heating the cold water in the heat exchange tube, which is then fed back to a water line. Disadvantageously, a user of the tub may trip over the raised heat exchanger cover. The tub may also be difficult to clean and maintain.
U.S. Pat. No. 4,619,311 issued to Vasile et al. on Oct. 28, 1986 discloses a counter-flow heat exchanger system in which waste water exits a shower tub via an essentially vertical waste pipe. A lower portion of the waste pipe is surrounded by a jacket into which is fed cold water in a coaxial counter-flow orientation such that waste water travelling down the waste water pipe exchanges its heat with the cold water travelling up the jacket thereby heating the cold water by heat transfer across the waste water pipe wall. The heated water exits directly to the shower system or moves to a hot water heater tank.
U.S. Pat. No. 4,472,372 issued to Hunter on Feb. 8, 1983 discloses a heat exchanger that is located in a drain pipe of a shower bath. A cylindrical member is in communication with the drain hole and includes, on the interior, a coiled heat conducting conduit. The coiled conduit includes a coiled copper tube which extends the full length of the cylindrical housing and a second heat conducting coil that is disposed within the annulus of the first heat conducting coil. The coils are each fed by a common inlet conduit which feeds cold water through the coiled conduits such that waste water flowing into the cylindrical member heats the cold water flowing through the coils which then exits via a common outlet towards the mixing valve of the shower unit. A baffle in the form of a central core member is disposed within the annulus of the central coil and appears to cause the water flowing from the drain pipe to be maintained in contact with both coils so as to maximize heat transfer. The heat exchange in this design takes place by direct contact of the waste water with the cold water conduit.
U.S. Pat. No. 4,304,292 issued to Cardone et al. on Dec. 8, 1981 discloses a shower unit in which a U-shaped conduit as part of a heat exchange apparatus. A heat exchange conduit is coiled around the exterior of the U-shaped conduit. Cold water flows through the coiled conduit and is heated by the waste water flowing through the U-shaped conduit, although there is no indication as to the nature of the contact between the coils and the U-shaped conduit. It is possible that the heat exchange is occurring across the walls of the two conduits. The coiled cold water conduit may also be located internally of the U-shaped conduit. Heat exchange appears to take place by direct contact of the waste water with the coiled cold water conduit.
U.S. Pat. No. 4,300,247 issued to Berg on Nov. 17, 1981 discloses a heat exchanger integral with the base of a shower unit in which a drain hole is in communication with the heat exchanger. The heat exchanger has a pair of so-called drain water flow through compartments, which are separated by a heat conducting material from a pair of cold water flow through compartments. Cold water is fed into the compartments and, after absorbing heat from the drain water, exits via an output. The heat exchange appears to occur by direct contact of water with the surface of a supply of cold water; in this case, however, instead of being a conduit, the cold water is located in compartments. Waste water fills one side of a number of serpentine compartments up to a line and exchanges heat across the folded layers of heat conductive material into complementary cold water containing compartments. Presumably, this folded arrangement of the heat conductive material allows for a great surface area over which the heat exchange can take place. The heat exchange takes place by direct contact of waste water on the container of cold water.
U.S. Pat. No. 6,722,421 issued to MacKelvie on Apr. 20, 2004 discloses a rather complex arrangement of either vertical or horizontal heat exchangers which have built-in heat storage for continuous heat recovery from waste drain water. A vertical heat exchanger includes a drain conduit connected to a drain water source, a water reservoir surrounding the drain conduit and a cold water conduit coiled around the water reservoir. A number of nested convection chambers are located on the external wall of the drain conduit and hold a volume of water adjacent to the wall of the drain conduit. In operation, drain water in the drain conduit heats the volume of water in the chambers, which through convention flows into the reservoir thereby heating same and the cold water flowing through the coiled conduit. The horizontal version of the heat exchanger has a convention chambers that appears to “cup” the central drain conduit and operate on the same convection principle as described for the vertical design. Interestingly, simultaneous flow of cold water in the coiled conduit and waste water in the drain conduit is not necessary. There is no contact between the drain conduit and the cold water conduit.
U.S. Pat. No. 5,791,401 issued to Nobile on Aug. 11, 1998 discloses a portion of a waste water conduit which is U-shaped. The drain conduit includes a number of axially disposed consecutive solid wall ridges and depressions, which are located around the entire inner surface of the drain conduit. A cold water conduit is coiled around the waste water conduit and includes a smooth, arcuate thermal transfer surface complementary to the curvature of the cold water conduit sidewall. This design appears to operate when the void in the U-shaped portion of the waste water drain conduit is entirely filled with waste water.
U.S. Pat. No. 5,740,857 issued to Thompson et al., Apr. 21, 1998 discloses a heat recovery and storage device useful to recover heat from warm waste water in which a generally horizontal waste water conduit is surrounded by a cold water reservoir. The waste water conduit includes a number of projections made of a high thermally conductive material located on a lower external surface of the conduit and which project into the cold water reservoir so as to transfer heat to same. The upper portion of the conduit is made of a material which limits heat re-conduction. The cold water is in direct contact with the outer wall of the drain water conduit.
U.S. Pat. No. 4,256,170 issued to Crump on Mar. 17, 1981 discloses a liquid-to-liquid heat exchanger which includes a number of fins located at a lower portion of the waste water conduit. The fins are arranged to define a generally serpentine fluid pathway within a jacket of cold water, which surrounds the waste water conduit. The fins are also used to transfer heat to the cold water and induce turbulence in the cold water flow.
Thus, there is a need for an improved heat exchange apparatus, in which the fluids do not contact each other and which provides efficient thermal energy transfer across the heat exchanger walls over a short pathway, and in which debris and maintenance tooling can pass through the heat exchange apparatus.
SUMMARY OF THE INVENTIONWe have designed a novel, blade-type, passive fluid-to-fluid heat exchange apparatus, which uses turbulators to induce and maintain turbulent flow to provide unexpectedly high efficiency heat recapture from waste water (also known as “grey water”) commonly found in household shower and bath systems. Moreover, the blade members are self-supporting and do not require additional frames for support as is typically required in existing heat exchange designs.
Accordingly, in one aspect there is provided a heat exchange apparatus, the apparatus comprising: a hollow blade member having a first fluid inlet and a first fluid outlet and a first fluid passageway for a first fluid extending therebetween, the blade member being sized and shaped for location in a second fluid passageway for a second fluid, the blade member being configured to enhance thermal energy transfer between the fluids as they flow along their respective passageways.
Accordingly in another aspect, there is provided a blade heat exchange apparatus, the apparatus comprising: at least one blade member having a first fluid inlet and a first fluid outlet, and a first fluid passageway for a first fluid extending therebetween, the blade member having a longitudinal blade axis; a second fluid passageway for a second fluid, the second fluid passageway being sized and shaped to receive therein the blade member; the blade member has two blade walls, each blade wall having an inner and outer thermal transfer surface, the thermal transfer surfaces each having a plurality of spaced apart ridges and recesses, the ridges and recesses being substantially parallel to each other, the ridges and recesses of the first blade wall being angled in a first direction relative to the longitudinal axis, the ridges and recesses of the second blade wall being angled in a second direction relative to the longitudinal axis, the second direction being different from the first direction so as to induce cross flow in the first and second fluids as they travel along their respective passageways.
Accordingly in another aspect, there is provided a heat exchange apparatus, comprising: a central conduit having a conduit wall; an outer jacket substantially encasing the central conduit, the jacket being spaced apart from the conduit wall to define an enclosure and having a fluid inlet and a fluid outlet; a turbulator located in the enclosure, the turbulator having a first helical wire disposed in a clockwise orientation and a second helical wire disposed counterclockwise to the first helical wire so as to induce shear turbulent flow in a fluid as it flows through the enclosure and contacts the turbulator.
Accordingly in another aspect, there is provided a heat exchange apparatus, the apparatus comprising: a central conduit having a conduit wall; an outer jacket substantially encasing the central conduit, the jacket being spaced apart from the conduit wall to define an enclosure and having a fluid inlet and a fluid outlet; a mesh turbulator located in the enclosure, the mesh turbulator being configured to induce shear and turbulent flow in a fluid as it flows through the enclosure and contacts the turbulator.
Accordingly in one embodiment of the present invention there is provided a heat exchange apparatus, the apparatus comprising:
a) at least one hollow fin member having first and second thermal transfer surfaces, the first thermal transfer surface defining a first fluid passageway for a first fluid, which first fluid being flowable along the first passageway in contact with the first thermal transfer surface; and
b) a second fluid passageway for a second fluid, the second fluid passageway being located in intimate contact with the second thermal transfer surface, such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway.
Accordingly in another embodiment of the present invention there is provided a heat exchange apparatus, the apparatus comprising:
a) a channel member having first and second end portions, the channel member having a plurality of hollow fin members extending between the first and second end portions, the fin members having first and second thermal transfer surfaces, the first thermal transfer surface defining a first fluid passageway, the first end portion being connectable to a source of a first fluid, the first fluid entering the first end portion at a first temperature and flowable along the first thermal transfer surface, the first fluid exiting the second end portion at a second temperature; and
b) a second fluid passageway having an inlet and an outlet, the second fluid passageway being located in intimate contact with the second thermal transfer surface, the inlet being connectable to a source of a second fluid, the second fluid entering the inlet at a third temperature and flowable along the second fluid passageway, such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway, the second fluid exiting the outlet at a fourth temperature.
Accordingly in one embodiment of the present invention there is provided a heat exchange apparatus, the apparatus comprising:
a) a channel member having first and second thermal transfer surfaces, at least one thermal transfer surface being uneven and defining a first fluid passageway for a first fluid; and
b) a second fluid passageway for a second fluid, the second fluid passageway being located in intimate contact with the second thermal transfer surface, the flow of at least one of the fluids being disrupted such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway.
Accordingly in another embodiment of the present invention, there is provided a heat exchange apparatus, the apparatus comprising:
a) a fluid passageway having a fluid passageway sidewall of a membraneous material, the material having at least one heat conductive surface locatable in intimate contact with a portion of a conduit sidewall, the conduit having an inlet and an outlet, a first fluid entering the inlet at a first temperature and exiting the outlet at a second temperature, the fluid passageway sidewall being spreadable over an area of the conduit sidewall, the fluid passageway having a fluid passageway inlet and a fluid passageway outlet, a second fluid entering the fluid passageway inlet at a third temperature and exiting the fluid passageway outlet at a fourth temperature.
Accordingly, in another embodiment, there is provided a heat exchange apparatus, the apparatus comprising:
a) a conduit having an arcuate conduit member having first and second ends, and an arcuate heat exchanger having first and second connecting portions sealingly connectable to the respective first and second ends, the heat exchanger having first and second thermal transfer surfaces, an amount of a first fluid entering the conduit at a first temperature and being in contact with the first thermal transfer surface and exiting the conduit at a second temperature; and
b) a fluid passageway having a fluid passageway sidewall of a membraneous material, the material having at least one heat conductive surface locatable in intimate contact with the second thermal transfer surface, the fluid passageway sidewall being spreadable over an area of the second thermal transfer surface, the fluid passageway having a fluid passageway inlet and a fluid passageway outlet, a second fluid entering the fluid passageway inlet at a third temperature and exiting the fluid passageway outlet at a fourth temperature.
Accordingly in another embodiment of the present invention, there is provided a heat exchange apparatus for use with a P-Trap having an inlet and an outlet, the P-Trap having a first drain portion disposed orthogonal to the ground and connectable to a drain, a second drain portion being disposed away from the ground in a downward gradient, and a U-shaped drain portion interconnecting the first and second drain portions, the apparatus comprising:
a) a fluid passageway having a fluid passageway sidewall of a membraneous material, the material having at least one heat conductive surface locatable in intimate contact with a sidewall of first drain portion, the second drain portion and the U-shaped portion, a first fluid entering the inlet at a first temperature and exiting the outlet at a second temperature, the fluid passageway sidewall being spreadable over an area of the first drain portion, the second drain portion and the U-shaped portion sidewall, the fluid passageway having a fluid passageway inlet and a fluid passageway outlet, a second fluid entering the fluid passageway inlet at a third temperature and exiting the fluid passageway outlet at a fourth temperature.
Accordingly in another embodiment of the present invention, there is provided a drainage apparatus for use with a drain trap, the apparatus comprising:
a) a P-Trap having an inlet and an outlet, the P-Trap having a first drain portion being disposed orthogonal to the ground and connectable to the drain trap, a second drain portion being disposed away from the ground in a downward gradient and a U-shaped drain portion interconnecting the first and second drain portions;
b) the second drain portion comprising:
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- i) an arcuate conduit member having first and second ends, and an arcuate heat exchanger having first and second connecting portions sealingly connectable to the respective first and second ends, the heat exchanger having first and second thermal transfer surfaces, an amount of a first fluid entering the second drain portion at a first temperature and being in contact with the first thermal transfer surface and exiting the second drain portion at a second temperature; and
- ii) a fluid passageway having a fluid passageway sidewall of a membraneous material, the material having at least one heat conductive surface locatable in intimate contact with the second thermal transfer surface, the fluid passageway sidewall being spreadable over an area of the second thermal transfer surface, the fluid passageway having a fluid passageway inlet and a fluid passageway outlet, a second fluid entering the fluid passageway inlet at a third temperature and exiting the fluid passageway outlet at a fourth temperature.
Accordingly in another embodiment of the present invention, there is provided a drainage apparatus for use with a drain trap, the apparatus comprising:
a) a P-Trap having a drain portion disposed orthogonal to the ground and connectable to the drain trap and a U-shaped drain portion;
b) a heat exchanger in fluid communication with the U-shaped portion, the heat exchanger having a channel member having first and second end portions, the channel member having a plurality of hollow fin members extending between the first and second end portions, the fin members having first and second thermal transfer surfaces, the first thermal transfer surface defining a first fluid passageway, a first fluid entering the first end portion from the U-shaped portion at a first temperature and flowable along the first thermal transfer surface, the first fluid exiting the second end portion at a second temperature; and
c) a second fluid passageway having an inlet and an outlet, the second fluid passageway being located in intimate contact with the second thermal transfer surface, the inlet being connectable to a source of a second fluid, the second fluid entering the inlet at a third temperature and flowable along the second fluid passageway, such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway, the second fluid exiting the outlet at a fourth temperature.
Accordingly in one embodiment of the present invention there is provided a drainage apparatus for use with a drain trap, the apparatus comprising:
a) a P-Trap having a drain portion being disposed orthogonal to the ground and connectable to the drain trap and a U-shaped drain portion;
b) a heat exchange apparatus in fluid communication with the U-shaped portion, the apparatus having a channel member having first and second thermal transfer surfaces, at least one thermal transfer surface being uneven and defining a first fluid passageway for a first fluid received from the U-shaped portion; and
c) a second fluid passageway for a second fluid, the second fluid passageway being located in intimate contact with the second thermal transfer surface, the flow of at least one of the fluids being disrupted such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway.
Accordingly, in another embodiment there is provided a heat exchange apparatus, as described in the embodiments above, for use with a drain trap of a bath tub or a shower tub in a household drainage system.
Accordingly, in another embodiment there is provided a turbulator for inducing turbulent flow in a fluid, the turbulator comprising: a hollow blade member having a fluid inlet and a fluid outlet, and a fluid passageway for the fluid extending therebetween, the fluid passageway being configured to induce turbulent flow in the fluid as it flows therealong.
Accordingly, in yet another embodiment, there is provided a heat exchange apparatus, the apparatus comprising: a plurality of turbulators for inducing turbulent flow in a first fluid, each turbulator having a hollow blade member having a fluid inlet and a fluid outlet, and a first fluid passageway for the first fluid extending therebetween, the first fluid passageway being configured to induce turbulent flow in the first fluid as it flows therealong; and a second fluid passageway for a second fluid, the second fluid passageway being sized and shaped to receive the turbulators therein and configured to induce turbulent flow in the second fluid as it flows along the second fluid passageway.
These and other features of the invention will become more apparent from the following description in which reference is made to the appended drawings wherein:
Unless otherwise specified, the following definitions apply:
The singular forms “a”, “an” and “the” include corresponding plural references unless the context clearly dictates otherwise.
As used herein, the term “comprising” is intended to mean that the list of elements following the word “comprising” are required or mandatory but that other elements are optional and may or may not be present.
As used herein, the term “consisting of” is intended to mean including and limited to whatever follows the phrase “consisting of”. Thus the phrase “consisting of” indicates that the listed elements are required or mandatory and that no other elements may be present.
As used herein, the term “turbulator” when referring to either a surface or to an insert having a surface that acts as a turbulator, is intended to mean that the surface has a plurality of projections extending away therefrom. Surface turbulators and inserted turbulators are used to increase convenction rates and heat transfer coefficients at heat exchange surfaces in fluid passageways in order to provide high performance in compact heat exchange assemblies, and to orientate fluids into a pre-defined direction often resulting in chaotic paths. Examples of types of turbulators include, but are not limited to, corrugations, peaks and troughs, nubbins, raised chevrons having a gap between, fish scales, raised zigzag moldings, meshes, criss cross oriented wires, porous materials, and the like. Turbulators may comprise uniform or non-uniform surface profiles, textures, open cell structures, and shapes. Porosity and fluid passageway geometry allow control of fluid flow via solid or semi-solid mechanical structures and may be constructed from laminate composites, molded parts, and even mesh of plastics, ceramics, metals or other materials.
As used herein the term “fluid” is intended to mean gas or liquid. Examples of liquids suitable for use with the heat exchangers described herein include, but are not limited to, water, hydraulic fluid, petroleum, glycol, oil and the like. Examples of gases include, for example, combustion engine exhaust gases and steam.
The invention features a novel heat exchange apparatus in which hollow fin members or hollow blade members with or without surface patterns can be used to promote efficient thermal energy transfer between fluids across thermal energy transfer surfaces. The flow of fluids can be passive, i.e. by gravity or can flow under the influence of pressure, either above or below atmospheric pressure. The heat exchange apparatuses described herein are also self-draining. Moreover due to their design, the blade members can be located directly in a grey water pathway with or without the use of pre-filtration to remove particulate debris. In one example, the efficiency of heat recapture is 40-60% when compared to 25% heat recapture efficiency of conventional systems. To achieve this, in one example, we use a channel with plurality of hollow blades to move, by gravity, grey water along a pathway such that it exchanges its heat (typically about 40° C.) to a source of cold water flowing through another passageway located in intimate contact with the channel. In other examples, higher fluid temperatures (>100° C.) can also exchange their thermal energy to cold water so as to generate steam. The heat exchange takes place across a thin (typically from about 1/1000 inch to about ⅕ inch thickness) double wall arrangement. Furthermore, thermal energy transfer occurs along a significantly shorter pathway between thermal transfer surfaces when compared to thermal transfer across solid fins. The cold water is heated to produce warmed water, which may then be stored in a storage tank or communicated to a mixing valve in a shower or bath system. Advantageously, the heat exchanger apparatus is constructed from inexpensive materials and when installed is essentially maintenance-free. The grey water conduits (pipes) used are standard 1.5 to 4 inch and are universally retrofittable into existing plumbing systems with the minimum of disruption to the household. The apparatus may also be connectable to active heat exchange apparatus such as, for example, a Peltier Module. The various designs of heat exchange apparatus will now be described in detail.
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The first and second fluids flow in a contra-flow manner through the heat exchange apparatus 10. It is also possible to have the fluids flow in a parallel flow manner. The first temperature T1 of the first fluid 28 entering the first fluid passageway 36 can be greater than or less than the second temperature T2 of the first fluid 28 as it exits the first fluid passageway 36. Similarly, the third temperature T3 of the second fluid 25 can be greater than or less than the fourth temperature T4 of the second fluid 25 as it exits the second passageway 46. In the examples illustrated herein, the first temperature T1 of the first fluid 28 entering the first fluid passageway 36 is greater than the second temperature T2 of the first fluid 28 as it exits the first fluid passageway 36. The third temperature T3 of the second fluid 25 is less than the fourth temperature T4 of the second fluid 25 as it exits the second fluid passageway 46. By way of example, T1 is typically 40° C. for grey water (the first fluid), T2 is typically 30° C. for grey water exiting the heat exchanger 10, T3 is typically 10° C. for cold water (the second fluid), and T4 is typically 24° C. for warmed water entering the warm water line 22 from the heat exchanger 10. To measure the efficiency of the heat exchange apparatus, the following equation is used:
where T denotes temperature in ° C.
At least one of the fluids flows through its respective passageway under pressure, the other fluid flowing through its respective passageway at atmospheric pressure. Typically, the second fluid (the cold water) flows under pressure at approximately 50 psi along the second fluid passageway 46.
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Built-in options may be included within any of the heat exchange apparatuses described herein in order to increase overall system performance and durability. These options include thin wall elements; laminar flow disruptor elements; check valve systems; one or more external level indicators; anti scaling capabilities such as, for example, mechanical devices and passage configurations to reduce scaling, anti-scaling coatings, vibration, chemical, and electrical means; anti corrosion means such as, for example, electrical, chemical, anodic, cathodic, and coatings; and water hammer protection such as, for example, shock absorbers, flexible or relatively soft and elastic cold water circuit components. Additional features may include use of an insulating shell on the systems and subsystems. System leaks and malfunctions can be detected in a variety of ways using, for example, relative flow measurement and/or pressure transducers and gauges located at strategic points in the heat exchange apparatus. Extrudable capillary fin geometry, as well as flow disruptors and other structural elements can be made of glass or Pyrex. The heat exchangers may be self draining in both horizontal and vertical positions. Individual heat exchanger modules or cylinders or heat exchanger bundles can be positioned at the top or at the bottom of larger vessels, such as with the vessels 530 described above, depending on heat exchange requirements in a given application. If electric power is required for monitoring or control equipment, power sources such as batteries, thermoelectric, or micro-turbines can be advantageously used in combination or alone.
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It is to be noted that in the heat exchange apparatuses 10, 76, 100, 200, 300, 500, and 600 described above, the grey water was described as the “first fluid” and the cold water was described as the “second fluid”. In the following embodiments, for ease of description of the heat exchangers, the cold water is now referred to as the “first fluid” and the grey water is now referred to as the “second fluid”
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It is known that greater thermal transfer performance and ease of manufacturing are obtained by using a thin formed sheet material in the manufacturing process of the heat exchanger components. Using thin wall stainless steel composite sheets of approximately 0.015″ to 0.035″ thicknesses in heat exchanger apparatuses provides low resistance to burst due to possible excessive high internal cold water pressure, such as those commonly used in household or industrial plumbing systems.
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Cross-connection of plumbing devices is ruled by strict, but variable, local regulations, where grey water and fresh cold water are present within the same heat exchanger apparatus. Universally, a double wall design is preferred over any other protection means to prevent fresh water contamination by grey water in the event of system failure, such as if the heat exchanger wall is ruptured or pierced.
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The shell 802 of the blade assembly is essentially the same as in the single wall construction described above except for the fact that a plurality of atmospheric venting ports 860 are present in order to immediately evacuate any fluid penetrating into the defined inter-surface zone space 856. Leaking fluid immediately evacuates to the atmosphere either by gravity or by water pressure, whichever is greater, and depending on the origin of the leak. Leaking fluid evacuation is, however, increased by the textures described above. The inner pressure of the cold water compresses the bladder 850 with great force against the pressure bearing surface of the external shell 802 to provide acceptable heat transfer rates between the grey water and cold water. A suitable thermal paste or porous filler material may be optionally used to fill the inter-surface zone space 856 to further enhance the thermal transfer rate.
Blade surface dimensions and shapes, areas and thicknesses, wall and surface compositions and the nature of the material used to construct the blades, as well as surface treatment, macroscopic and microscopic surface shape and texture, all determine the blade's ability to transfer heat and become non-adhesive, or self-cleaning. Additionally, non adhesion of dirt, soap, scum, hair and debris to all heat exchanger walls and surface features, can be controlled by fluid flow management by fluid velocity and surface turbulence control, as well as chemical anti-fouling and surfaces geometrical self-cleaning properties.
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It should be noted that the wall materials, shapes, thicknesses, widths and heights, surface textures and cross sections of the blade members and of their inner components do not need to be symmetrical, fixed or constant in any manner with respect to given geometrical axes of the assembly. For example, it is possible to use a blade with a large “front-end” and a slimmer “tail-end”, in order to precisely control heat transfer surface dimensions and corresponding heat transfer rates between two fluids in cross-flow configurations. Variations where the effective cross section and the height and width of a blade or inter-blade spacing varies according to a mathematical function along the length of the blade or blade bundle assemblies are also contemplated to further enhance performance.
One of the advantages of the blade assembly is that whole assembly or even an individual blade can be removed for cleaning, inspection and maintenance and replaced if necessary. Moreover, the grey water can flow unfiltered along its passageway. Specialized cleaning tools such as wire brushes or enzyme or bacteria based solutions, as well as chemical cleaners, or combinations thereof can be periodically applied via the floor drain of the shower in order to dissolve any dirt accumulated over time on the heat exchanger grey water walls within the drainage system in order to maintain optimal said grey water flow characteristics and thermal transfer rates of the system, without affecting the environment or the drainage components in any significant matter. A strainer located at the grey water floor drain will also advantageously reduce debris entering the drain.
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When the ridges and recesses 844, 845 are disposed diagonally, the relative “criss cross” configuration of the ridges on the walls of the blade members causes high levels of fluid shear, turbulence and cross flow within both the grey water and the cold water. However, it is to be understood that the ridges and recesses may be orientated at any angle relative to the longitudinal axis of the blade member, and may also interdigitate, or contact with each other at the central cross area, or they may be spaced apart from each other. In the example shown, the manifolds 622 for receiving the cold water are disposed generally orthogonal to the longitudinal axis 878 of the blade members and downwardly away from the longitudinal axis, as best shown in
Ridges can be evenly spaced and shaped (depth and 3D forms) or follow a pattern defined mathematically along the blade walls, to increase blade surfaces and generate turbulent flow for various grey water and cold water flow conditions, thereby maximizing heat transfer. Fluid shear inducing ridges may be located at the bottom of the grey water passageway 847. Additionally, scale-type/shaped ridges can be used to create turbulent flow at the bottom of the grey water passageway 847, with a reduced risk for clogging. The same scales structure may be useful for location on the periphery of vertical heat exchange embodiment, as described below.
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In the previously described examples of the blade-like heat exchange apparatus, the manifolds are disposed downwardly away from the longitudinal axis 878 of the blades to facilitate maintenance. This design is for use in household shower arrangements in which water typically drains at 10 litres/hour. For commercial applications, however, the manifolds may be disposed upwardly away from the longitudinal axis 878 of the blades. In larger applications, the larger blades are rigidified by welds and can also provide a double wall arrangement. The bladder is punctured and sealed around each structural weld. Moreover, if required, a section of the blade can be enlarged by adding additional sections of blade thereto. The additional blade sections can be embossed with flow disrupters. Alternatively, one can use a turbulator insert to induce flow turbulence inside the blades.
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Referring now to
An alternative to the double helical wire criss cross turbulator is a double slinky wire criss cross turbulator which consists of an insertion of a single clockwise slinky wire into a counter-clockwise patterned corrugated tube (club grip) or even into an axial internal finned tube or any other criss cross generating wire pattern.
Compact Heat ExchangersAs best illustrated in
The suitably dimensioned blade can be located inside a tubular pipe 1002 for heat exchange of calibrated or known volumes of grey water and cold water. The heat exchange apparatus 1000 can also be located externally of the tubular pipe 1002. In another example, the tubular pipe 1002 may be manufactured such that the arcuate heat exchange apparatus is integral with the pipe sidewall.
The arcuate blade heat exchanger apparatus 1000 can be used singly for applications in which a small volume of grey water is traveling along the pipe 1002 and located adjacent the area of the pipe where heat is to be exchanged. The arcuate design of the heat exchange apparatus means that multiple arcuate heat exchange apparatuses can be used to fully or partially encase the pipe 1002. Two or three or more arcuate blade heat exchange apparatuses 1000 can be used to fully encase the pipe 1002. Also, if the arcuate blades are located inside the pipe, the arcuate blades are typically constructed from metal with the turbulators 1001 located on one or both sides of the blade. If located outside the pipe, the blade is manufactured with metal on one side and the turbulators 1001 on one or both sides or inserted. Metal surfaces on both sides of the arcuate blade along with turbulators is a favoured construction for the blades.
Sections of the compact designs are particularly useful for drain pipe heat exchange applications where drains are installed in a position other than vertical relative to the ground, and where one side of the pipe carries the energy to be exchanged.
Although in the examples described above, hollow, planar blades and hollow arcuate blades have been described, it is to be understood that the blades can be of any three-dimensional shape, such as cylindrical, conical, triangular, disk-like, and the like. Moreover, we also contemplate that planar hollow blades having surface projections and recesses can be formed into a tube, the tube being optionally open along the longitudinal axis in order to be attached and clamped onto a central grey water drain.
Referring now to
In addition to monitoring the heat exchange apparatuses, it is possible to use the system 700 to monitor and compute tariffs and fees based on heat exchanger workload and efficiency or other measurable physical workloads performed by the systems over time. Energy savings provided by the heat exchanger and peripheral systems can be evaluated, charged and billed to the user.
OTHER EMBODIMENTSFrom the foregoing description, it will be apparent to one of ordinary skill in the art that variations and modifications may be made to the invention described herein to adapt it to various usages and conditions. Such embodiments are also within the scope of the present invention.
Claims
1. A heat exchange apparatus, the apparatus comprising:
- a hollow blade member having a first fluid inlet and a first fluid outlet and a first fluid passageway for a first fluid extending therebetween, the blade member being sized and shaped for location in a second fluid passageway for a second fluid, the blade member being configured to enhance thermal energy transfer between the fluids as they flow along their respective passageways.
2. The apparatus, according to claim 1, in which the enhancement of thermal energy transfer is caused by turbulent flow.
3. The apparatus, according to claim 1, in which the enhancement of thermal transfer is caused by reduction of laminar flow.
4. The apparatus, according to claim 1, in which the enhancement of thermal transfer is caused by shear within the first and second fluids.
5. The apparatus, according to claim 1, in which the blade member has an inner and an outer thermal transfer surface, the inner thermal transfer surface having a plurality of spaced apart inner surface projections to induce thermal energy transfer in the first fluid, the outer thermal transfer surface being located to contact the second fluid flowing along the second fluid passageway.
6. The apparatus, according to claim 5, in which the inner thermal transfer surface further includes a plurality of spaced apart inner surface recesses.
7. The apparatus, according to claim 5, in which the outer thermal surface has a plurality of spaced apart outer surface projections located to induce thermal energy transfer in the second fluid as it flows along the second fluid passageway in contact with the outer thermal transfer surface.
8. The apparatus, according to claim 5, in which the outer thermal transfer surface further includes a plurality of spaced apart outer surface recesses.
9. The apparatus, according to claim 5, in which the inner and outer thermal transfer surfaces each have a plurality of spaced apart projections and recesses, the projections and recesses being disposed substantially parallel to each other.
10. The apparatus, according to claim 1, in which the blade member has a longitudinal blade axis and two blade walls, each blade wall having an inner and an outer thermal transfer surface, each thermal transfer surface having a plurality of ridges and recesses disposed substantially parallel to each other.
11. The apparatus, according to claim 10, in which the outer thermal transfer surfaces are located to contact the second fluid flowing along the second fluid passageway.
12. The apparatus, according to claim 10, in which the ridges and recesses of the first blade wall being angled in a first direction relative to the longitudinal axis, the ridges and recesses of the second blade wall being angled in a second direction relative to the longitudinal axis, the second direction being different from the first direction so as to induce cross flow in the first and second fluids as they travel along their respective passageways.
13. The apparatus, according to claim 10, in which the ridges located on opposing inner thermal transfer surfaces contact each other to induce cross flow in the first fluid as it travels along the first fluid passageway.
14. The apparatus, according to claim 10, in which the ridges located on opposing inner thermal transfer surfaces are spaced apart from each other to induce cross flow in the first fluid as it travels along the first fluid passageway.
15. The apparatus, according to claim 10, in which the ridges located on opposing inner thermal transfer surfaces are interdigitated to induce cross flow in the first fluid as it travels along the first fluid passageway.
16. The apparatus, according to claim 10, in which the ridges located on opposing inner thermal transfer surfaces contact each other to induce turbulence in the first fluid as it travels along the first fluid passageway.
17. The apparatus, according to claim 10, in which the ridges located on opposing inner thermal transfer surfaces are spaced apart from each other to induce turbulence in the first fluid as it travels along the first fluid passageway.
18. The apparatus, according to claim 10, in which the ridges located on opposing inner thermal transfer surfaces are interdigitated to induce turbulence in the first fluid as it travels along the first fluid passageway.
19. The apparatus, according to claim 1, in which the second fluid passageway is configured to induce thermal energy-transfer between the fluids.
20. The apparatus, according to claim 1, in which the first and second fluids flow in a contraflow direction.
21. The apparatus, according to claim 1, in which the first and second fluids flow in a parallel flow configuration.
22. The apparatus, according to claim 1, in which the first and second fluids flow in a cross flow configuration.
23. The apparatus, according to claim 1, in which each blade wall has a sealable blade edge to allow the blade member to be pressurized.
24. The apparatus, according to claim 23, in which the blade member is pressurized to above atmospheric pressure or to below atmospheric pressure.
25. The apparatus, according to claim 1, in which the blade member has a longitudinal blade axis, the first fluid inlet and the first fluid outlet being disposed orthogonal relative to the longitudinal blade axis.
26. The apparatus, according to claim 1, in which the blade member has a longitudinal axis, the second fluid passageway has a second fluid inlet and a second fluid outlet, the second fluid inlet and the second fluid outlet being disposed coaxial to the longitudinal axis.
27. The apparatus, according to claim 26, in which the second fluid inlet and the second fluid outlet are disposed orthogonal to the longitudinal axis of the blade member.
28. The apparatus, according to claim 1, in which the blade member is double-walled.
29. The apparatus, according to claim 28, in which the double wall is a lining located in intimate contact with an inner thermal transfer surface of the blade member.
30. The apparatus, according to claim 29, in which the lining is spaced apart from the inner thermal transfer surface, a thermal transfer filler being located between the lining and the inner thermal transfer surface.
31. The apparatus, according to claim 29, in which the lining is a bladder.
32. The apparatus, according to claim 31, in which the bladder is made from a membraneous heat conductive material.
33. The apparatus, according to claim 1, in which the blade member is ventable to the atmosphere.
34. The apparatus, according to claim 1, in which the blade member further comprises a lining located in intimate contact with an inner thermal transfer surface of the blade member, the lining defining a double wall, the blade member being configured to allow the first fluid to drain away from the first passageway or the second fluid from the second fluid passageway, if either of the passageways breaks.
35. The apparatus, according to claim 1, in which the first or second fluids flow by gravity.
36. The apparatus, according to claim 1, in which a turbulator is located in the first fluid passageway.
37. The apparatus, according to claim 1, in which a turbulator is located in the second fluid passageway.
38. The apparatus, according to claim 1, in which the second fluid passageway is pressurized to above atmospheric pressure or below atmospheric pressure.
39. The apparatus, according to claim 1, in which the first fluid is cold water and the second fluid is grey water.
40. A blade heat exchange apparatus, the apparatus comprising:
- at least one blade member having a first fluid inlet and a first fluid outlet, and a first fluid passageway for a first fluid extending therebetween, the blade member having a longitudinal blade axis;
- a second fluid passageway for a second fluid, the second fluid passageway being sized and shaped to receive therein the blade member;
- the blade member has two blade walls, each blade wall having an inner and outer thermal transfer surface, the thermal transfer surfaces each having a plurality of spaced apart ridges and recesses, the ridges and recesses being substantially parallel to each other, the ridges and recesses of the first blade wall being angled in a first direction relative to the longitudinal axis, the ridges and recesses of the second blade wall being angled in a second direction relative to the longitudinal axis, the second direction being different from the first direction so as to induce cross flow in the first and second fluids as they travel along their respective passageways.
41. The heat exchange apparatus, according to claim 40, the ridges located on the inner thermal transfer surfaces of the blade walls contact each other, are spaced apart from each other, or are interdigitated.
42. The heat exchange apparatus, according to claim 40, in which the second fluid passageway is a channel located in a tray.
43. The heat exchange apparatus, according to claim 40, in which a plurality of blade members are mounted substantially parallel to each other.
44. The heat exchange apparatus, according to claim 40, in which a plurality of the blade members are stacked on top of each other and define a plate.
45. The heat exchange apparatus, according to claim 40, in which a plurality of the plates are mounted in a housing, the housing having a first fluid inlet and a first fluid outlet.
46. The heat exchange apparatus, according to claim 40, in which the blade member is double walled.
47. The heat exchange apparatus, according to claim 40, in which the blade member is ventable to the atmosphere.
48. The heat exchange apparatus, according to claim 40, is located downstream of a drain trap.
49. The heat exchange apparatus, according to claim 40, in which the first fluid passageway includes a turbulator.
50. The heat exchange apparatus, according to claim 40, in which the second fluid passageway includes a turbulator.
51. A heat exchange apparatus, comprising:
- a central conduit having a conduit wall;
- an outer jacket substantially encasing the central conduit, the jacket being spaced apart from the conduit wall to define an enclosure and having a fluid inlet and a fluid outlet;
- a turbulator located in the enclosure, the turbulator having a first helical wire disposed in a clockwise orientation and a second helical wire disposed counterclockwise to the first helical wire so as to induce turbulent flow in a fluid as it contacts the turbulator.
52. The heat exchange apparatus, according to claim 51, in which the first and second helical wires cross each other and induce cross flow in the fluid as it contacts the helical wires.
53. The heat exchange apparatus, according to claim 51, in which grey water flows along the central conduit.
54. The heat exchange apparatus, according to claim 51, in which cold water contacts the turbulator.
55. The heat exchange apparatus, according to claim 54, in which the cold water flows by gravity.
56. A heat exchange apparatus, the apparatus comprising:
- a central conduit having a conduit wall;
- an outer jacket substantially encasing the central conduit, the jacket being spaced apart from the conduit wall to define an enclosure and having a fluid inlet and a fluid outlet;
- a mesh turbulator located in the enclosure, the mesh turbulator being configured to induce turbulent flow in a fluid as it contacts the turbulator.
57. The apparatus, according to claim 56, in which the mesh turbulator includes a first plurality of helical wires disposed in a clockwise orientation and a second plurality of helical wire disposed counterclockwise to the first plurality of helical wire.
58. The apparatus, according to claim 56, in which the mesh turbulator includes a plurality of orthogonally disposed wires.
59. The apparatus, according to claim 56, in which the central conduit and the enclosure further include turbulators.
60. A heat exchange apparatus, the apparatus comprising:
- at least one hollow fin member having first and second thermal transfer surfaces, the first thermal transfer surface defining a first fluid passageway for a first fluid, which first fluid being flowable along the first passageway in contact with the first thermal transfer surface; and
- a second fluid passageway for a second fluid, the second fluid passageway being located in intimate contact with the second thermal transfer-surface, such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway.
61. The apparatus, according to claim 60, in which the fin members are disposed substantially parallel to each other.
62. The apparatus, according to claim 60, further including a turbulator disposed on the first thermal surface to induce turbulent flow in the first fluid
63. The apparatus, according to claim 60, further including a turbulator disposed on the second thermal surface to induce turbulanet flow in the second fluid.
64. The apparatus, according to claim 60, in which the fin members are configured as an H-shaped channel member having first and second end portions, the first end portion being connectable to a source of a first fluid, the first fluid entering the first end portion at a first temperature and flowable along the first thermal transfer surface, the first fluid exiting the second end portion at a second temperature and a second fluid passageway having an inlet and an outlet, the second fluid passageway being located in intimate contact with the second thermal transfer surface, the inlet being connectable to a source of a second fluid, the second fluid entering the inlet at a third temperature and flowable along the second fluid passageway, such that the first fluid when flowing along the first fluid passageway exchanges thermal energy with the second fluid flowing along the second fluid passageway, the second fluid exiting the outlet at a fourth temperature.
65. The heat exchange apparatus, according to claim 60, in which the fin members are circumferentially disposed about a conduit.
66. A heat exchange apparatus, the apparatus comprising:
- a conduit having an arcuate conduit member having first and second ends, and an arcuate heat exchanger having first and second connecting portions sealingly connectable to the respective first and second ends, the heat exchange having first and second thermal transfer surfaces, an amount of a first fluid entering the conduit at a first temperature and being in contact with the first thermal transfer surface and exiting the conduit at a second temperature; and
- a fluid passageway having a fluid passageway sidewall of a membraneous material, the material having at least one heat conductive surface locatable in intimate contact with the second thermal transfer surface, the fluid passageway sidewall being spreadable over an area of the second thermal transfer surface, the fluid passageway having a fluid passageway inlet and a fluid passageway outlet, a second fluid entering the fluid passageway inlet at a third temperature and exiting the fluid passageway outlet at a fourth temperature.
67. The apparatus, according to claim 1, in which the blade member is self-supporting.
Type: Application
Filed: Aug 14, 2008
Publication Date: Mar 5, 2009
Applicant: Prodigy Energy Recovery Systems Inc. (Montreal)
Inventors: Marc Hoffman (Saint-Lambert), Gilbert Demedeiros (Beaconsfield)
Application Number: 12/228,667
International Classification: F28F 13/12 (20060101); F28D 7/00 (20060101);