Patent Grant
6904963
The present invention relates generally to a heat exchanger and a method of forming the heat exchanger.
It is generally desirable for heat exchangers to exhibit efficient transfer of heat. It is also generally desirable for fluids to flow through the heat exchangers without requiring unduly larger pressure drops for driving that flow. Additionally, and particularly in the automotive industry, it has become increasingly desirable to combine multiple functions in a single heat exchanger assembly. Additionally, multi-port tubes have been widely used in the automotive industry for high thermal efficiency and compactness reasons. Accordingly, the present invention seeks to provide an improved heat exchanger that exhibits one or more of these desirable characteristics. In heat exchangers, this desirability for fluids to flow through the heat exchangers without requiring unduly larger pressure drops for driving that flow, in addition to the desirability of more viscous liquids to flow through part or all of the heat exchangers, have led to tube designs of relatively large hydraulic diameters and led the automotive industry away from using tubes that have hydraulic diameters of lower ranges. In practice, one way suggested to design heat exchanges, such as condenser, has been to employ tube designs of a certain hydraulic diameter while restricting the number of passes or changes of fluid direction, for example, of fluid refrigerant, within the heat exchanger. In automotive applications, the number of passes often is limited to between 3 to 6 passes, thereby permitting internal pressure drop to remain limited to an acceptable level. General teaching has been against further reducing hydraulic diameter size, even though this could provide slight improvements in heat transfer, as it may, as well, have the undesired effect of greatly increasing refrigerant side pressure drop in such an exchanger.
The present invention exhibits desired characteristics by providing an improved heat exchanger having a first end tank and a second end tank opposite the first end tank. One or more first tubes are in fluid communication with the first and second end tanks and the one or more first tubes are adapted to have a first fluid flow therethrough. One or more second tubes are also in fluid communication With the first and second end tanks and the one or more second tubes are adapted to have the first fluid flow therethrough after the first fluid flows through the one or more first tubes. Although the first and second tubes may be similar or identical to each other, it is preferable that they be similar under certain circumstances. Preferably, this is the case when such tubes have hydraulic diameters of less than about 1.00 mm. More preferably all tubes have hydraulic diameters of less than about 0.60 mm. Also more preferably, the tubes have hydraulic diameters of less than or equal to about 0.50 mm. Even more preferably, one or both of the first and second tubes has hydraulic diameters of less than 0.40 and greater than or equal to about 0.15 mm.
It is further contemplated that the heat exchanger may include one or more third tubes in fluid communication with the first and second end tanks. Preferably, the one or more third tubes are adapted to have a second fluid, different from the first fluid, flow therethrough. Typically, a plurality of fins is disposed between the first tubes, the second tubes, the third tubes or any combination thereof. Preferably, the fins have a fin height less than or equal to about 10.0 mm, more preferably less than or equal to about 9.0 mm, even more preferably less than or equal to about 8.0 mm. In an even more preferred embodiment, fin height is equal to about 5.00-7.00 mm.
Preferably, the tubes and the fins are generally co-planar relative to each other although not required. Return tubes, such as those that are part of a condenser, are also found in preferred embodiments of the present invention. Such tubes generally have larger hydraulic diameters and cross sections than the second set of tubes, as they do not primarily perform heat transfer functions.
In one preferred embodiment, the heat exchanger is a single pass exchanger. In such an embodiment, the first fluid is a refrigerant such that the first and second tubes are part of a condenser and the second fluid is an oil such that the one or more third tubes are part of an oil cooler. The third tubes comprise a return tube that normally has a cross sectionally fluid area larger than that of the smaller first and second tubes, to provide easier assembly and to reduce internal pressure drop. In another preferred embodiment, the one or more third tubes are above or below the one or more first and second tubes. In another preferred embodiment, the oil cooler includes an inlet supported by the first end tank and the inlet is below an outlet that is also supported by the first end tank. In still another preferred embodiment, the oil cooler is a single pass oil cooler with a lower tube, a higher tube and an inlet located nearer the lower tube than the higher tube. In yet another preferred embodiment, the heat exchanger includes a receiver having a bottom portion located below a lowest tube of the one or more second tubes.
The features and inventive aspects of the present invention will become more apparent upon reading the following detailed description, claims, and drawings, of which the following is a brief description:
Generally, the present invention relates to a heat exchanger and to a method of forming the heat exchanger. The heat exchanger may be a single fluid or multi-fluid (e.g., 2, 3 or 4 fluid) heat exchanger. The heat exchanger may also be a single pass or multi-pass heat exchanger. Preferably, the heat exchanger in preferred embodiments of the present invention has fewer than three passes, more preferably the heat exchanger being a single pass or two pass heat exchanger. In preferred embodiments, where tube hydraulic diameter is less than or equal to about about 0.50 mm, the number of passes is preferably limited to one. In more preferred embodiments where in number of passes is limited to one, hydraulic diameter is most preferably less than about 0.40 mm. In a most preferred embodiment, where inlet and outlet are on the same side of the manifold/end tank, the heat exchanger is more preferably a two pass heat exchanger. Although the heat exchanger according to the present invention may be used for a variety of articles of manufacture (e.g., air conditioners, refrigerators or the like), the heat exchanger has been found particularly advantageous for use in automotive vehicles. For example, the heat exchanger may be used for heat transfer of one or more various fluids within a vehicle such as air, oil, transmission oil, power steering oil, radiator fluid, refrigerant, combinations thereof or the like.
According to one embodiment of the invention, the heat exchanger is configured such that a fluid flows through tubes that have a hydraulic diameter similar throughout. Also preferred is where the heat exchanger is configured such that a fluid flows through one or more first tubes and then through one or more second tubes wherein the first tubes have a hydraulic diameter that is similar throughout. Preferably, although not required, the fluid is a refrigerant that is substantially a gas as it enters the one or more first tubes. Advantageously, the embodiment can provide for relatively good heat transfer while assisting in lowering the pressure drop required or desired for flowing the fluid through the first and second tubes.
According to another embodiment, there is contemplated a multi-fluid heat exchanger that includes a condenser in combination with an oil cooler selected from a power steering oil cooler, a transmission oil cooler, a combination thereof or the like. Preferably, the component of the heat exchanger are arranged in a manner that allows for more effective heat exchange, minimal interference between the oil cooler and the condenser, combinations thereof or the like.
As an another preferred embodiment, a heat exchanger of the present invention comprises a first end tank; a second end tank opposite the first end tank; a plurality of first tubes in fluid communication with the first and second end tanks, the plurality of first tubes adapted to have a first fluid flow therethrough, the plurality of first tubes having a hydraulic diameter less than about 1.00 mm; a plurality of second tubes in fluid communication with the first and second end tanks, the plurality of second tubes adapted to have the first fluid flow therethrough after the first fluid flows through the plurality of first tubes, the plurality of second tubes each having a hydraulic diameter less than about 1.00 mm; a one or a plurality of third tubes in fluid communication with the first and second end tanks, the third tubes adapted to have a fluid flow therethrough; and a plurality of fins disposed between the pluralities of first and second tubes and the plurality of fins being generally co-planar relative to each other.
In a highly preferred embodiment, a heat exchanger of the present invention comprises a first end tank; a second end tank opposite the first end tank; a plurality of first tubes in fluid communication with the first and second end tanks, the plurality of first tubes adapted to have a first fluid flow therethrough, the plurality of first tubes having a hydraulic diameter less than about 0.40 mm and greater than or equal to about 0.15 mm; a plurality of second tubes in fluid communication with the first and second end tanks, the plurality of second tubes adapted to have the first fluid flow therethrough after the first fluid flows through the plurality of first tubes, the plurality of second tubes each having a hydraulic diameter less than about 1.0 mm and greater than or equal to about 0.15 mm; and a plurality of fins disposed between the pluralities of first and second tubes, with the pluralities of first and second tubes and the plurality of fins being generally co-planar relative to each other. Other embodiments include heat exchangers comprising a first end tank, a second end tank opposite the first end tank, a plurality of first tubes in fluid communication with the first and second end tanks, the plurality of first tubes adapted to have a first fluid flow therethrough, the plurality of first tubes each having a hydraulic diameter less than about 1.00 mm, a plurality of second tubes in fluid communication with the first and second end tanks, the plurality of second tubes adapted to have the first fluid flow therethrough after the first fluid flows through the plurality of first tubes, the plurality of second tubes each having a hydraulic diameter less than about 1.00 mm, and at least one fin contacting the one or the plurality of first tubes and at least one of the plurality of second tubes, with the first and second tubes and the fins being generally co-planar relative to each other; and wherein the fin height is less than or equal to about 10.0 mm, or similar embodiments.
The heat exchanger may be installed in a variety of locations relative the article of manufacture to which the heat exchanger is applied. For an automotive vehicle, the heat exchanger is preferably located under a hood of the vehicle. According to one highly preferred embodiment, the heat exchanger may be attached to a radiator of the vehicle. Exemplary methods and assemblies for attaching a heat exchanger to a radiator are disclosed in U.S. Pat. No. 6,158,500 and co-pending U.S. provisional patent application Ser. No. 60/355,903, titled “A Method and Assembly for Attaching Heat Exchangers”, filed on Feb. 11, 2002 both of which are fully incorporated herein by reference for all purposes.
According to one aspect of the invention, the heat exchanger will comprise a plurality of components that are assembled together by suitable joining techniques. In one preferred embodiment, one or more of the components of the heat exchanger such as the baffles, the end tanks, the tubes, fins, the inlets, the outlets, a bypass or combinations thereof may be attached to each other using brazing techniques. Although various brazing techniques may be used, one preferred technique is referred to as controlled atmosphere brazing. Controlled atmosphere brazing typically employs a brazing alloy for attaching components wherein the components are formed of materials with higher melting points than the brazing alloy. The brazing alloy is preferably positioned between components or surfaces of components to be joined and, subsequently, the brazing alloy is heated and melted (e.g., in an oven or furnace, and preferably under a controlled atmosphere). Upon cooling, the brazing alloy preferably forms a metallurgical bond with the components for attaching the components to each other. According to one highly preferred embodiment, the brazing alloy may be provided as a cladding on one of the components of the heat exchanger. In such a situation, it is contemplated that the components may be formed of a material such as a higher melting point aluminum alloy while the cladding may be formed of a lower melting point aluminum alloy.
Heat exchangers of the present invention will typically include one or more tubes, one or more end tanks, one or more inlets and outlets, one or more baffles, one or more fins or a combination thereof. They also typically include one or more inlets and outlets in their respective manifolds or end tanks. Depending upon the embodiment of the heat exchanger, various different shapes and configurations are contemplated for the components of the heat exchanger. For example, and without limitation, the components may be integral with each other or they may be separate. The shapes and sizes of the components may be varied as needed or desired for various embodiments of the heat exchanger. Additional variations will become apparent upon reading of the following description.
In general, a preferred heat exchanger contemplates at least two spaced apart end tanks bridged together in at least partial fluid communication by a plurality of generally parallel tubes, with fins disposed between the tubes. Optional end plates, or more preferably, end tubes enclose the assembly in a generally co-planar configuration.
More specifically, referring to
Depending upon the configuration of the heat exchanger, it may be possible to provide common end tanks that are divided to accommodate more than one fluid or separate end tanks for accommodating plural fluids. It is also possible that end plates can be employed to bridge the end tanks in accordance with the present invention. However, it is particularly preferred that the heat exchanger employs end tubes in lieu of end plates. In this manner, weight savings and improved efficiency is possible owing to a reduced variety of component types.
As mentioned, one advantageous feature of the present invention is the ability to integrate a plurality of different fluid heat exchangers. Though the specification will make apparent that alternatives are possible (e.g. side by side) one particularly preferred approach is to effectively stack a first fluid heat exchanger upon at least a second fluid heat exchanger in a single generally co-planar assembly.
In the preferred embodiment shown, the heat exchanger 10 includes a plurality of a first set of tubes 28 extending between and in fluid communication with a first portion 22 (e.g. an upper portion) of the end tanks 12 and a plurality of a second set of tubes 30 in fluid communication with the second portion 24 (e.g. a lower portion) of the end tanks 12. Moreover, the first portion 22 of one of the end tanks 12 and the second portion 24 of the other of the end tanks 12 are separated into an inlet portion 38 in fluid communication with one of the inlets 14 of the heat exchanger 10 and an outlet portion 40 in fluid communication with one of the outlets 16 of the heat exchanger 10. Preferably, as shown best in
The heat exchanger 10 is formed by attaching the tubes 28, 30 to the end tanks 22 either sequentially or simultaneously with one or more fins 34 between each of the opposing tubes 28, 30. The tubes 28, 30 may be attached to the end tanks with fasteners (mating or otherwise), by welding, brazing or the like. Additionally, the fins 34 may be attached or fastened to the tubes 28, 30, the end tanks 22 or both.
In a highly preferred embodiment, although not required, the tubes 28, 30 may be formed with arcuate edges 54 connecting the body walls 44 and side walls 46 of the tubes 28, 30. The arcuate edges 54 may be separate from or may form at least part of the body and side walls 44, 46 of the tubes 28, 30. In the preferred embodiment shown, the radius of curvature for each of the arcuate edges 54 is substantially identical. However, the radius may vary from edge to edge. Also in the highly preferred embodiment, the fins 34 are formed with edge projections 56, such as is shown in FIG. 2A. In this manner, the fins are adapted for providing a drop resistant structure that helps retain the fins 34 stable relative to the tubes 28, 30 particularly during assembly (e.g. during a brazing operation). In the preferred embodiment shown, the projections 56 include a surface 58 configured to generally overlap and complement the arcuate edges 54 of the tubes 28, 30. It is contemplated that each fin 34 may include one or a plurality of edge projections 56. For example, as illustrated, there are four projections 56. However, it will be appreciated that fewer may be employed provided that stability of fins relative to tubes can be maintained.
Advantageously, the substantially identically configured body walls 44 and the substantially identical radius of curvature of the edges 54 allows at least one of the larger upper tubes 28 to be separated from at least one of the smaller lower tubes 28, 30 by fins 34 that are substantially identical to the fins 34 separating the lower tubes 28 from each other, the fins 34 separating the upper tubes 28 from each other or both. Thus, in one highly preferred embodiment, each of the tubes 28, 30 is separated from each opposing tube by only one fin 34 and each of the fins 34 is substantially the same size, shape or a combination thereof. Fin size or shape, however, may vary from fin to fin also. Preferably, fin height is less than 10.0 mm.
In operation, a first fluid enters through the inlet 14 of the inlet portion 38 of a first of the end tanks 12 and flows through passageways 50 of one or more of the first set of tubes 28 to a first portion of a second of the end tanks 12. Thereafter, the first fluid flows through another passageway 50 of one or more of the first set of tubes 28 to the outlet portion 40 and through the outlet 16. Additionally, a second fluid enters the heat exchanger through the inlet 14 of the inlet portion 38 of the second portion 24 of the second of the end tanks 12 and flows through passageways 50 of the second set of tubes 30. The second fluid flows through the outlet 16 of the second portion 24 of the second of the end tanks 12. Of course, as discussed previously, the functions of both of the end tanks can be integrated into a single end tank.
During flow of the first and second fluids through the tubes 28, 30, an ambient fluid preferably flows by over outside of the tubes 28, 30, the fins 34 or both. In turn, heat may be transferred from the first and second fluids to the ambient fluid or from the ambient fluid to the first and second fluids. The first and second fluids may be of the same or a different viscosity. For example, in one preferred embodiment, the first fluid has a higher viscosity than the second fluid. For example, and without limitation, the first fluid may be transmission oil, coolant oil, engine oil, power steering oil or the like while the second fluid will typically be a refrigerant.
Advantageously, when similarly sized tubes are employed, the passageways 50 of the first set of tubes 28 are suitable for the flow of more viscous fluids without relatively large pressure drops across the tubes 28 while the similarly sized passageways 50 of the lower tubes are also suitable for lower viscosity fluids. It is also possible to switch the positioning of the tubes so that the first fluid is passed through the second portion or vice versa.
From the above, it will thus be appreciated that one preferred method of the present invention contemplates providing a multi-fluid heat exchanger assembled in a common assembly; passing a first fluid through one portion of the heat exchanger for heat exchange, and passing at least one additional fluid through at least one additional portion of the heat exchanger for heat exchange of the additional fluid.
It is contemplated that a heat exchanger formed in accordance with the present invention may include one or more tubes having various different internal configurations for defining passageways within the tubes. They may also have different external configurations defining one or more outer peripheral surfaces of the tubes. Further it is possible that the internal configurations, external configuration or both vary along the length of the tube.
It is also contemplated that the tubes may be formed of a variety of techniques and a variety of materials. Exemplary forming techniques include stamping, molding, extrusion, rolling or the like. Exemplary materials include metals such as aluminum, steel, magnesium, titanium, combinations therof or the like or polymeric materials such as plastic, thermoplastics or the like. The internal configuration of a tube may be the same or different from the external configuration. For instance, the walls of the tubes may have opposing sides that are generally parallel to or otherwise complement each other. Alternatively, they may have a different structure relative to each other. The external configuration of the tube may include grooves, ridges, bosses, or other structure along some or all of its length for assisting in heat transfer. Likewise, the internal configuration may include grooves, ridges, bosses or other structure.
It is also possible that the structure is provided for generating turbulence within the fluid, or for otherwise controlling the nature of the flow of fluid there-through.
The passageways of the tubes may be provided in a variety of shapes such as square, rectangular, circular, elliptical, irregular or the like. In preferred embodiments, the passageways of the tubes are essentially square, circular or rectangular. Most preferred are passageways of tubes that are essentially square or circular. In particularly preferred embodiments, the height of the passageway relates to the hydraulic diameter of the passageway. Preferably, the passageway height to hydraulic diameter ratio is between about 0.10 to about 4.0; more preferably from about 0.33 to about 3.0; even more preferably from about 0.45 to about 1.25; most preferably from about 0.75 to about 1.25. Passageways of tubes may include one or more partitions, fins or the like. As used herein, a partition for a passageway in a tube is a structure (e.g., a wall) that substantially divides at least part of the passageway into a first and second portion. The partition preferably is continuous (but may be non-continuous) such that the partition completely separates the first portion from the second portion or the partition may include openings (e.g., through-holes, gaps or the like) connecting the first and second portion.
As used herein, a fin for a passageway in a tube is intended, to encompass nearly any structure (e.g. a protrusion, a coil, a member or the like), which is located within the(passageway of the tube and is physically connected (e.g., directly or indirectly) to an outer surface of the tube that engages in heat exchange. The shape of each of the fins may be the same or different relative to each other. Further, the pitch angle of each fin may be the same or different relative to each other. It will also be appreciated that the configuration of a tube may vary along its length. One or both tube ends may be provided with fins but the central portion left un-finned. Likewise, the central portion may be provided with fins but one or both of the tube ends are left un-finned. Fin spacing may be constant within a passageway or may be varied as desired. Fin height is preferably less than or equal to about 10.0 mm; more preferably less than or equal to about 9.0 mm; even more preferably less than or equal to about about 8.0 mm, most preferably from about 5.0-7.00 mm.
For providing efficient heat transfer, the multi-fluid heat exchanger may be provided in a variety of configurations. For example, tube arrangements, inlet/outlet arrangements, tank arrangements, combinations thereof or the like may be configured to provide added efficiency or other advantages to the heat exchanger. Moreover, additional components may be added to the multi-fluid heat exchanger. Examples of such advantageous configurations are illustrated in
Referring to
Generally, it should be understood that the embodiments in
Referring to
While it is contemplated that the first tubes 178 and second tubes 180 may be similar or identical to each other, it is preferred that the first tubes 178 are essentially similar or identical to the second tubes 180. Preferably, at least one of the first tubes 178 has a hydraulic diameter that is less than or equal to 1.0 mm and that the hydraulic diameter of the second tube is less than or equal to 1.0 mm. More preferably, each of the first tubes 178 has the same hydraulic diameter as each of the second tubes 180. Even more preferably, the first tubes and the second tubes are essentially identical.
The hydraulic diameter of at least one, and preferably, each of the first tubes 178 is less than about 1.0 mm, more preferably less than about 0.60 mm and still more preferably less than about 0.50 mm, even more preferably less than about 0.40 mm (most preferably less than 0.30 mm). Accordingly, the hydraulic diameter of at least one; and preferably, each of the second tubes 180 is less than about 1.0 mm, more preferably less than about 0.06 mm and still more preferably less than about 0.50 mm, even more preferably less than about 0.40 mm (most preferably less than 0.3 mm). As used herein, hydraulic diameter (Dh) is determined according to the following equation:
Dh=4Ap/Pw
wherein
Each of the variables (Pw and Ap) for hydraulic diameter (Dh) are determinable for a tube according to standard geometric and engineering principles and will depend upon the configuration of a particular tube, surface roughness of inner tube walls and the aforementioned tube variables (i.e., the number of partitions, the number of portions, the size of the portions, the size of the passageways or a combination thereof).
Preferably, the plurality of first tubes 178 includes at least one, two or three more tubes 178 than the plurality of second tubes 180. As shown, the plurality of first tubes 178 includes five tubes 178, but may include fewer (e.g., two, three or four) or more (e.g., six, seven or more) tubes 178. The plurality of second tubes 180 includes four tubes 180, but may include fewer (e.g., two or three) or more (e.g., five, six or more) tubes 180. It is also contemplated that the heat exchanger 170 may include only one first tube 178, only one second tube 180 or both and that the first and the second tubes may be substantially identical to one another. There may be fewer second tubes 180 as compared to first tubes 178.
Preferably, each of the plurality of first tubes 178 is substantially identical to the other first tubes 178 and each of the plurality of second tubes 180 is substantially identical to the other second tubes 180, as well as being similar or substantially identical to the first tubes 178. It is contemplated however, that one or more of the first tubes 178 may be different from each other or one or more of the second tubes 180 may be different from each other. For example hydraulic diameters, geometries or the like may be different.
With additional reference to
As shown, there are twenty-two sub-passageways 194/204 that are substantially circular in shape. It is contemplated, however, that the shape of the sub-passageways may be varied as needed or desired, that the shape may be varied from sub-passageway to sub-passage and that there may be greater of fewer sub-passageways.
Preferably, the sub-passageways 194/204 are each dimensioned to have a cross-sectional area perpendicular to the length (L) that is between about 0.02 mm2 and about 1.00 mm2, more preferably between about 0.09 mm2 and about 0.60 mm2. It is contemplated, however, that the dimensions may be different from those mentioned.
In addition to varying the shapes, cross-sections, dimensions or the like of the tubes 178, 180, the surface roughness of inner walls of tubes 178, 180 that define the sub-passageways 194, 204 may also be varied. For example, the inner walls may be smooth, corrugated, contoured or the like. Advantageously, varying such roughness can assist in fine tuning the hydraulic diameters of the tubes as needed or desired. Preferably, the first end tank 172, the second end tank 174 or a combination thereof include at least one inlet 210 and at least one outlet 212 for respectively receiving and emitting a fluid. It is contemplated, however, that the inlet 210 and the outlet 212 may be alternatively located depending upon design considerations for a heat exchanger.
In operation, a fluid flows through the inlet 210 into the first end tank 172. In the particular embodiment shown, the first end tank 172 is divided into an inlet portion 214 and an outlet portion 216 and the fluid flows into the inlet portion 214. Thereafter, the fluid flows through the plurality of first tubes 178 to the second end tank 174.
During flow through the plurality of first tubes 178, it is preferable, although not required, that a substantial amount (e.g., more than 80% by weight) of the fluid change from a gas phase to a liquid phase. For facilitating such phase change, it is preferable that the fluid is a refrigerant such as those known to the skilled artisan as R134a and R22. It is contemplated, however, that any other suitable fluids (e.g., water, oil or the like) or CO2 gas may be used.
Once in the second tank 174, the fluid flows through the plurality of second tubes 180 to the outlet portion 216 of the of the first end tank 172. Preferably, the fluid remains in the liquid phase or more of the fluid becomes liquid during flow through the plurality of second tubes 180. Then the fluid flows through the outlet 212 to exit the heat exchanger 170.
In the preferred embodiment illustrated, at least a portion and preferably substantially all of the fluid must flow through at least one of the plurality of first tubes 178 and, thereafter, must flow through at least one of the plurality of second tubes 180. In alternative embodiments, however, it is contemplated that one or more bypasses (e.g., tubes, passageways or the like) may be employed such that a portion of the fluid does not flow through any of the first tubes 178, any of the second tubes 180 or both. It is also contemplated that the flow pattern described above may be altered.
For flowing the fluid through the tubes 178, 180 and end tanks 172, 174, a particular total pressure drop ΔPtot is typically required to drive the fluid from the inlet 210 or inlet portion 214 to the outlet 212 or outlet portion 216. Generally speaking, it is preferable to maintain that pressure drop ΔPtot below a certain predetermined amount for nearly all heat exchanger applications. Moreover, maintaining a relatively low ΔPtot is particularly desirable for automotive applications such as for automotive condensers.
In the embodiment shown, the total pressure drop ΔPtot is typically substantially equivalent to the sum of the pressure drop ΔP1 across the plurality of first tubes 178 and the pressure drop ΔP2 across the plurality of second tubes 180. Of course, in alternative embodiments, the total pressure drop ΔPtot may be minorly or more significantly effected by other pressure drops as well (e.g., from bypasses, additional tubes or the like).
Either way, the combination of the first tubes 178 and the second tubes 180 into the heat exchanger 170 advantageously can allow for greater heat exchange of lower total pressure drops ΔPtot when compared with traditional heat exchangers. As examples, it is contemplated that the total pressure drop ΔPtot may be less than 1.5 bar and more preferably less than 1.0 bar. (At operating conditions of the air condition system). Exemplary pressure drops ΔP1 across the first tubes 178 may be less than 0.75 bar and more preferably less than 0.5 bar. Moreover, exemplary pressure drops ΔP2 across the plurality of second tubes 80 may be less than about 0.75 bar and more preferably less than 0.5 bar. Of course, larger pressure drops may also be considered within the scope of the present invention.
In alternative embodiments, the heat exchanger of the present invention may include or be operated in conjunction with additional components such as bypasses, pumps or the like. Referring to
For the heat exchanger 218 shown in
In a preferred embodiment, during fluid flow, the receiver 120 can act as a separator, which separates any portion of the fluid in a liquid state from any portion of the fluid in a gas state. As shown in
In this manner, substantially all of the fluid that enters the second portion 228 of the second end tank 174 and then flows into the plurality of second tubes 180 is in a liquid state. As such, a relatively low amount of cooling is typically required of the plurality of second tubes 180 to maintain the fluid in the liquid state. Exemplary hydraulic diameters for the plurality of second tubes 180 of
Referring to
Referring to
Generally, it is contemplated that the various concepts components and heat exchangers disclosed for the present invention may be combined with each other as desired. Also various other concepts, components and heat exchangers may be combined with the concepts, components, and heat exchangers disclosed for the present invention. Examples of heat exchangers, compenents and concepts, which may be employed in combination with the heat exchangers, components and concepts of the present invention are disclosed in U.S. patent application Ser. No. 10/140,899, filed on May 7, 2002, titled “Improved Heat Exchanger” and expressly incorporated herein by reference for all purposes.
Unless stated otherwise, dimensions and geometries of the various structures depicted herein are not intended to be restrictive of the invention, and other dimensions or geometries are possible. Plural structural components can be provided by a single integrated structure. Alternatively, a single integrated structure might be divided into separate plural components. In addition, while a feature of the present invention may have been described in the context of only one of the illustrated embodiments, such feature may be combined with one or more other features of other embodiments, for any given application. It will also be appreciated from the above that the fabrication of the unique structures herein and the operation thereof also constitute methods in accordance with the present invention. For example, core depth can play a role in preferred embodiments of the present invention. In one of such preferred embodiments, the heat exchanger of the present invention has a core depth of between about 6.0 and 27.00 mm.
The preferred embodiment of the present invention has been disclosed. A person of ordinary skill in the art would realize however, that certain modifications would come within the teachings of this invention. Therefore, the following claims should be studied to determine the true scope and content of the invention.
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