WO2003048670A1

WO2003048670A1 - Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle

Info

Publication number: WO2003048670A1
Application number: PCT/US2002/034606
Authority: WO
Inventors: Stephen Memory; C. James Rogers; Gregory G. Hughes; Frank M. Grippe; Rifiquat Cheema; William Markusen; Kenneth Ritt; Frank Vetter
Original assignee: Modine Manufacturing Company
Priority date: 2001-11-30
Filing date: 2002-10-30
Publication date: 2003-06-12
Also published as: CN101089533A; EP1448945A1; RU2319094C2; CA2467137A1; AU2002365762A1; MXPA04004660A; TW200301815A; AU2002365762B2; CN100380081C; US20030102113A1; BR0214479A; RU2004117856A; JP2005512009A; AR037428A1; KR20050058253A; CN1596360A

Abstract

Heat exchanger (10) for providing supercritical cooling to the refrigerant of a transcritical cooling system (12) including a pair of elongated headers (20, 22) plurality of elongated tubes (28) spaced in side-by-side relation along the longitudinal axes (24, 26) of the headers (20, 22), and serpentine fins (30) extending between adjacent pairs of the tubes. Each of the tubes (28) is folded upon itself to define at least two parallel legs (36) of the tubes (28) and has a flattened cross-section. The parallel legs (36) of the tubes (28) are preferably spaced from each other, with the major dimension D of each of the parallel legs lying in a common plane. Each of the fins (30) includes alternating tabs (40) and elongated separations (42) extending parallel to the parallel legs (36) and located between the parallel legs (36) of the adjacent tubes (28) to divide the width (W) of each fin (30) into discrete fin elements (44) that are connected to each other by the tabs (40). Each of the fin elements (44) extends along one of the parallel legs (36) of the adjacent tubes (28).

Description

HEAT EXCHANGER FOR PROVIDING SUPERCRITICAL COOLING OF A WORKING FLUID IN A TRANSCRITICAL COOLING CYCLE

FIELD OF THE INVENTION

This invention relates to heat exchangers, and more particularly, to heat exchangers that provide supercritical cooling of a working fluid in a transcritical cooling cycle.

BACKGROUND OF THE INVENTION

One common form of a heat exchanger includes a so called "core" made up of tubes and interconnecting fins. One fluid is passed through the tubes of the core while a second fluid is passed through the core itself in the spaces between the fins and tubes. Typically, the opposite ends of the tubes are connected to a pair of parallel manifolds or "tanks", with one of the manifolds being an inlet manifold and the other manifold being an outlet manifold which direct one of the fluids into and out of the tubes, respectively. Heat exchangers of this general type are used for a large variety of purposes, such as radiators, condensers, evaporators, charge air coolers, oil coolers, etc., all of which may be utilized in a vehicle. One common form of this type of heat exchanger is known as a parallel flow heat exchanger wherein flat, multi-port tubes direct a refrigerant through the heat exchanger. Typically, the flat tubes are straight and the manifolds are spaced on opposite sides of the heat exchanger to receive the opposite ends of the tubes. However, it is known to bend the flat tubes so that each tube is shaped as a so called "hair pin" tube having two parallel legs, with the inlet and outlet manifold positioned next to each other to receive the ends of the tubes. One such construction is shown in U.S. Pat. No. 5,531 ,268 issued to

Hoshino et al. While the construction shown in the 5,531 ,268 patent may be sϋitable for its intended purpose, there is always room for improvement. Further, the construction may not be suitable or optimum for use in some air conditioning systems that rely on a higher operating pressure, such as a transcritical cooling cycle that requires a gas cooler for providing supercritical cooling of a refrigerant such as carbon dioxide, (C0₂).

Increasing environmental concerns over the use of many conventional refrigerants such as CFC12 and, to a lesser extent, HFC134a, has led to consideration of transcritical C0₂ systems, particularly for use in vehicular applications. For one, the C0₂ utilized as a refrigerant in such systems could be claimed from the atmosphere at the outset with the result that if it were to leak from the system back to the atmosphere, there would be no net increase in atmospheric C0₂ content. Moreover, while C0₂ is undesirable from the standpoint of a greenhouse effect, it does not affect the ozone layer and would not cause an increase in the greenhouse effect since there would be no net increase in the atmospheric C0₂ content as a result of leakage.

SUMMARY OF THE INVENTION

It is the principle object of the invention to provide a new and improved heat exchanger. It is another object of the invention to provide an improved heat exchanger that is suitable for supercritical cooling of a working fluid in a transcritical cooling cycle.

An exemplary embodiment of the invention achieves at least some of the foregoing objects in a heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle. The heat exchanger includes a pair of elongated headers having longitudinal axis disposed substantially parallel to each other, a plurality of elongated tubes spaced in side by side relation along the longitudinal axis of the headers, with each of the tubes being folded upon itself to define at least two parallel legs of the tube so that the working fluid flows serially through at least two parallel passes from one of the headers to the other, and serpentine fins extending between adjacent pairs of the tubes, with each of the fins having a length extending parallel to the parallel legs of the adjacent tubes. Each of the tubes has a flat cross-section with a major dimension and a minor dimension. The major dimensions of the parallel legs of each of the tubes lie in a common plane that is substantially transverse to the longitudinal axes of the headers. Each of the tubes has a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers.

In one form, each of the serpentine fins has a transverse width extending across the parallel legs of the adjacent tubes. Each of the fins includes a plurality of alternating tabs and elongated separations extending parallel to the parallel legs, with the tabs and separations located between the parallel legs of the adjacent tubes to divide the width of each fin into a plurality of discrete fin elements that are connected to each other by the tabs. Each of the fin elements corresponds to and extends along one of the parallel legs of each of the adjacent tubes.

In one form, the parallel legs of each of the tubes are spaced from each other.

In one form, each of the tubes is folded upon itself at least twice to define at least three parallel legs of the tube so that the working fluid flows serially through at least three parallel fluid passes from one of the headers to the other.

In one form, each of the tubes is a multi-port tube with a hydraulic diameter in the range of .015 inch to .040 inch. In one forjn, the major dimension of each of the tubes is no greater than .500 inch and the minor dimension is no greater than .100 inch.

In one form, each of the fins has a fin height extending from one of the tubes to an adjacent one of the tubes, parallel to the longitudinal axes of the headers, and the major dimension of the tubes is no greater than the fin height.

In one form, the major dimensions of the tubes extend parallel to the longitudinal axes of the headers at the location where the tube end is connected to the header. Other objects and advantages will become apparent from the following specification taken in connection with the accompanying drawings.

DESCRIPTION OF THE DRAWINGS

Fig.1 is a somewhat diagrammatic elevation view of a cooling system including a heat exchanger embodying the present invention; Fig. 2 is an elevation view of the heat exchanger shown in Fig. 1 ;

Fig. 3 is a side view of the heat exchanger shown in Fig. 2;

Fig.4 is a top view of the heat exchanger shown in Fig. 2;

Fig. 5 is an enlarged, partial section view taken along line 5-5 in Fig. 3; Fig. 6 is an enlarged, partial view of a tube employed in the heat exchanger shown in Figs. 1-5; and

Fig.7 is a perspective view showing a tube and a fin utilized in a heat exchanger embodying the invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to Fig. 1 , a heat exchanger 10 embodying the present invention is shown in connection with a basic cooling system 12 that operates a transcritical cooling cycle. The heat exchanger 10 is shown in the form of a gas cooler 13 that provides supercritical cooling to the working fluid or refrigerant, such as C0₂, of the cooling system 12 by rejecting heat to a medium, such as an air flow A, on the fin side of the heat exchanger.10. The cooling system 12 includes the heat exchanger 10, a compressor 14, that compresses gaseous phase refrigerants to a supercritical pressure for delivery to the heat exchanger 10, an expansion device 16, that reduces the pressure in the refrigerant received from the heat exchanger 10 so at least some of the refrigerant enters the liquid phase, an evaporator 17 that transfers heat from one medium into the refrigerant to change the refrigerant from the liquid phase to the gaseous phase, an accumulator 18 (optional), and a suction line heat exchanger 19 that transfers heat from the refrigerant exiting the heat exchanger 10 into the refrigerant exiting the evaporator 17, or accumulator 18 if used. It should be understood that the heat exchanger 10 may find use in other types of cooling systems, and in other configurations of cooling systems that perform a transcritical cooling cycle, and is not limited to use with the specific cooling system shown in Fig. 1 unless specifically recited in the claims. Further, while the disclosed heat exchanger 10 can provide distinct advantages when used as a gas cooler 13, it may also prove advantageous when used for other purposes, such as a condenser or an evaporator, regardless of whether it is used in connection with a transcritical cooling cycle.

With reference to Figs. 2-4, the heat exchanger 10 includes a pair of elongated tubular headers 20 and 22 having longitudinal axes 24 and 26, respectively, disposed substantially parallel to each other; a plurality of elongated tubes 28 spaced in side-by-side relations along the longitudinal axes 24, 26 of the headers 20, 22; and serpentine fins 30 extending between adjacent pairs of the tubes 28. It should be understood that in the illustrated embodiment, each fin 30 extends over a length L of the tubes 28, but the middle portions of the lengths are not shown in Fig. 2 for convenience of illustration. Preferably, the fins 30 are louvered. As seen in Fig. 3, each of the tubes 28 has a first end 31 connected to the header 20 and a second end 32 connected to the header 22 to transfer the refrigerant between the headers 20, 22.

Each of the tubes 28 has a flattened cross-section with a major dimension D and a minor dimension d, as best seen in Fig. 5. Each of the tubes 28 is preferably a multi-port tube and, in highly preferred embodiments, a multi-port tube having a hydraulic diameter in the range of

0.015 inch to 0.045 inch. In this regard, it should be understood that while Fig. 5 shows six ports 34, it may be beneficial in some applications to include more than, or less than, six ports 34 in each of the multi-port tubes 28. For example, in one preferred embodiment each of the tubes has four ports 34. In one preferred embodiment, the tubes are configured to withstand a burst pressure of at least 6500 PSI, at 70°F ambient, such as may be required for operation as a gas cooler in a transcritical C0₂ cooling system.

Preferably, the major dimension D of each of the tubes 28 is nominally no greater than 0.500 inch and the minor dimension d is nominally no greater than 0.100 inch, while in some highly preferred embodiments the minor dimension d is nominally no greater than 0.060 inch and the major dimension D is nominally no greater than 0.320 inch. In this regard, reducing the major dimension D can offer a number of advantages. For example, because each of the tubes 28 includes at least two parallel legs 36, the depth of the heat exchanger 10 becomes highly dependent upon the size of the major dimension D and will be reduced with the reduction in the major dimension D. Further, the diameter of the headers 20, 22 can be reduced in a construction where the major dimension D of the tube ends 31 , 32 extends transverse to the longitudinal axes 24, 26 of the headers 20, 22 at the locations where the ends 31, 32 are connected to the headers 20, 22, rather than the parallel construction shown in Figs. 1-4. Additionally, the length of the headers 20, 22, can be reduced in a construction wherein the major dimension D of the tube ends 31 , 32 extend parallel to the longitudinal axes 24, 26 of the headers 20, 22, such as shown in Figs. 1-4. Finally, a reduction in the major dimension D can allow for a reduction in the fin height in some preferred embodiments. However, it should be understood that larger fin heights may offer advantages with respect to air side efficiency.

As best seen in Figs. 3, 4 and 6, each of the tubes 28 is folded upon itself to define at least two parallel legs 36 of the tube 28 so that the refrigerant flows serially through at least two parallel fluid passes 38 from the header 20 to the header 22. In this regard, it is preferred that the inlet and outlet headers 20, 22 be selected so that the heat exchanger 10 operates in a cross-counterflow configuration relative to the fluid flow on the fin side of the heat exchanger 10 when operating as a gas cooler. Each pair of the parallel legs is joined by a fold 39 that is twisted 90° relative to the legs 36 at the location of the fold 39 so that the major dimension D extends parallel to the axes 26, 24 at the location of the fold 39, rather than transverse.

Preferably the fold 39 is formed by first twisting the legs 36 90° relative to the portion of the tube 28 at the location of the fold 39, and then bending the tube through approximately 180° at the location of the fold 39 to form the fold 39. In this regard, it should be understood that the 90° twist of each of the legs 36 relative to the fold 39 can be in the same direction as shown in

Figs.3 and 6, or in opposite, directions, depending upon which configuration offers the most advantage for a particular application of the heat exchanger 10. As best seen in Fig. 6, the parallel legs 36 of each of the tubes 28 are preferably spaced from each other by a distance X, With the major dimension D of each of the parallel legs 36 lying in a common plane, illustrated by dashed line P in Figs. 2 and 5, that is substantially transverse to the longitudinal axes 24, 26 of the headers 20, 22. This allows the major dimension D to extend parallel to the direction of the flow of the medium through the fins 30. The spacing X reduces heat conduction from one leg 36 to the other, which can be advantageous when the heat exchanger 10 is providing supercritical cooling because the temperature of the refrigerant can vary substantially as it flows through the tube 28 from one header 20 to the other header 22. Preferably, the distance X is sufficient to minimize or prevent the closing of the space between adjacent parallel legs 36 by braze material during brazing of the heat exchanger 10, but not so large so as to unduly increase the depth of the heat exchanger 10. While it is preferred that the adjacent parallel legs 36 of each tube 28 be spaced from each other, in some applications this spacing may not be required and/or desirable

As seen in Figs. 1 and 5, each of the fins 30 has a fin height H equal to the spacing between adjacent tubes 28, i.e. a fin height H extending from one of the tubes 28 to an adjacent tube 28 parallel to the longitudinal axes 24, 26 of the headers 20, 22. Preferably, the major dimension D of the tubes

28 is no greater than the fin height H. This allows a construction wherein each of the tube ends 31 , 32 can be twisted 90° relative to the parallel legs 36 from which they extend so that the major dimension D of the end 31 , 32 extends parallel to the longitudinal axes 24, 26 of the headers 20, 22 at the location where the tube ends 31 and 32 are connected to the headers 20 and 22, as seen in Fig. 2. This can be important in high pressure applications, such as gas coolers used in transcritical refrigeration systems, where it is desirable that the diameter of the headers 20, 22 be as small as possible. It is conceivable, even likely, in such constructions that the major dimension D will be greater than the inner diameter of either of the headers 20, 22. By allowing the major dimension D to extend parallel to the longitudinal axis 24, 26 of the headers 20, 22 where the tube ends 31 , 32 are connected to the headers 20, 22, the major dimension D of each of the tubes 28 can be greater than the inner diameter of either of the headers 20, 22. While it is preferred that the major dimension D of the tube ends 31 , 32 extend parallel to the longitudinal axes 24, 26 of the headers 20, 22 at the location where the tube ends 31 , 32 are connected to the headers 20, 22, other orientations of the major dimension D at these locations may be advantageous in some applications. For example, it may be advantageous in some applications for the major dimension D of the tube ends 31 , 32 to extend transverse to the longitudinal axes 24, 26 at the location where the tube ends 31, 32 are connected to the headers 20, 22. As previously discussed, each of the serpentine fins 30 has a length

L extending parallel to the parallel legs 36 of the adjacent tubes 28 and, as best seen in Fig. 4, a transverse width W extending across the parallel legs 36 of the adjacent tubes 28. For purposes of illustration, Fig. 5 shows three legs 36 of the tubes 28 and Fig. 7 shows a fin 30 for use with a heat exchanger construction 10 wherein each of the tubes 28 has only two parallel legs 36. With reference to Fig. 7, each of the fins 30 includes a plurality of alternating tabs 40 and elongated separations 42 extending parallel to the parallel legs 36 and located between the parallel legs 36 of the adjacent tubes 28 to divide the width W of each fin 30 into two or more discrete fin strips or elements 44 that are connected to each other by the tabs 40. Each of the fin elements 44 corresponds to and extends along one of the parallel legs 36 of each of the adjacent tubes 28. The separations 42 are generally straight line and have opposed edges 45 that face one another and are generally transverse to the direction of the medium flow through the fins 30. While Fig. 7 illustrates the fin 30 for tubes 28 having two parallel legs 36, it should be understood that the above construction including the tabs 40, separations 42 and fin elements 44 is utilized in constructions of the heat exchanger 10 having more than two parallel legs 36 in each of the tubes 28, such as the constructions shown in Figs. 2-5. In such constructions, each of the fins 30 preferably extends across all of the parallel legs 36 with a fin element 44 corresponding to and extending along each of the parallel legs 36 of each of the adjacent tubes 28, and the tabs 40 and separations 42 provided between each of the fin elements 44.

The alternating tabs 40 in each of the fins 30 serve to restrict movement of the fin elements 44 relative to each other so that each fin 30 remains a unitary component during the assembly of the heat exchanger 10 and, furthermore, to better maintain the fin elements 44 in alignment with each other to minimize the pressure drop on the fin side of the heat exchanger. The purpose of the elongated separations 42 is to minimize the heat conduction from each of the parallel legs 36 to any adjacent parallel leg 36 of each tube 28 by interrupting, and thus minimizing, the heat conduction between the fin elements 44 associated with each of the parallel legs 36. This is desirable in applications, such as the gas cooler 13 of Figs. 2-4, where the working fluid temperature entering the heat exchanger 10 is significantly different from the desired temperature for the working fluid leaving the heat exchanger 10. It has been calculated that for a fin 30 with only 10% of its height unlouvered (typical in a louveredfin), as much as 40% of the total heat transfer between the parallel legs 36 can be conducted through the fins, and hence not rejected into the air. In some situations, conduction of the heat received from the fin 30 on the hot side of the heat exchanger 10 can actually make the fin 30 on the cold side of the heat exchanger 10 hotter than the working fluid flowing through the tubes 28 on the cold side, which leads to the undesirable situation of transferring heat back into the working fluid prior to the working fluid leaving the heat exchanger 10. Thus, it is desirable for each of the elongated separations 42 to extend uninterrupted as far as possible along the length of the fin 30 and for the number and size of the tabs 40 to be minimized to that which is required to prevent each of the fin elements 44 from separating during assembly and to maintain an acceptable degree of alignment between the fin elements 44 of each of the fins 30 during assembly. From the foregoing, It should be understood that a number of configurations are possible for the tabs 40 and the elongated separations 42. For example, in one embodiment of a fin 30 made of aluminum, with the fin 30 in an unfolded state, each of the tabs 40 extends approximately 0.020 inch along the length of the fin 30 and each of the elongated separations 42 of a fin 30 made of aluminum extends approximately 8.0 inches along the length of the unfolded fin 30. In one preferred embodiment of the fin 30, the tabs 40 and the separations 44 have lengths extending parallel with the length of the fin 30 in the unfolded state and the ratio of the length of the separations 42 to the length of the tabs 40 is in the range of 200 to 600. In another example, such as shown in Fig. 7, each of the elongated separations 42 extends uninterrupted from one of the tabs 40 over 10 to 14 of the folds 46 to the next tab 40 with the fin 30 in the folded condition.

While the tabs 40 and the separations 42 can be formed in a number of ways, it is preferred that the separations 42 be formed as cuts or slits in the fin material that do not require removal of fin material during formation in the fin 30. One way of achieving such slits or cuts is to use a splitter disk in the fin roll die to create a simple cut in the fin 30 as the fin 30 is formed from a strip of sheet material. The split could be eliminated for a small portion of the disk in every revolution to form the tabs 40 to ensure that each fin element 44 stays attached to the adjoining fin element 44 of the fin 30. This provides a physical cut or slit in the fin 30, with no loss of fin surface. In one such construction the edges 45 are virtually, but not quite, in abutment with each other. One concern is that the fin elements 44 might braze together during the brazing process. One approach to minimize this concern is to locate the braze material on the side walls of the tube legs 36 that abut the fins 30, rather than cladding the braze material onto the fins 30. Another approach to minimize this concern is to offset adjacent fin elements 44 of the fin 30 at locations remote from the tab 40, which may allow for clad fins. Another approach would be to bend the edges 45 formed by the slits slightly apart, forming a very small louver, which may also allow for clad fins. Yet another approach is to coin each of the tab portions 40 to further separate the fin elements 44 from each other. Again, this last approach may allow for clad fins. While slits are preferred, in some applications it may be advantageous for the separations 42 to be formed as slots that do require removal of fin material when formed in the fins 30. In this regard, it would probably be sufficient for the slots to have a width of a few thousands of an inch parallel to the width W of the fin 30. While it is preferred that the fins 30 include the tabs 40 and separations 44, in some applications the tabs 40 and separations 42 may not be desirable and/or required.

It is preferred that the fins 30 be louvered, many forms of which are known. The exact configuration of the louvers will be highly dependent on the parameters of the particular application such as, for example, the fluid on the fin side of the heat exchanger 10, the available pressure drop on the fin side of the heat exchanger 10, the number of parallel iegs 36 in each of the tubes 28, and whether there is an odd or even number of parallel legs 36 in each of the tubes 28.

It should be understood that when operating as a gas cooler 13 in the system 12, the heat exchanger 10 will typically provide supercritical cooling of the refrigerant; however, there may be some conditions of operation wherein the ambient temperature is below the critical temperature, in which case the heat exchanger 10 will operate as a condenser that provides subcritical cooling for the refrigerant.

As best seen in Fig. 3, the illustrated heat exchanger 10 includes 12 parallel legs 36 for each of, the tubes 28. However, it should be understood that the optimum number of parallel legs for each application of the heat exchanger 10 will be highly dependent upon the specific parameters for the particular application such as, for example, the working fluid of the system 12, the envelope and environment into which the heat exchanger 10 must be packaged, and the function of the heat exchanger, i.e., as a gas cooler, condenser, or evaporator for use in either an AC or heat pump system. For example, in some applications it may be desirable to only have two or three parallel legs 36 for each of the tubes 28.

As another option, one or more baffles can be provided within either or both of the headers 20, 22 to direct the refrigerant from the header 20 through a subset of the tubes 28 to the header 22 and then back through a different subset of the tubes 28 to the header 20 and so on for as many passes from one header to the other as may be needed to provide the performance dictated by each particular application. In one preferred embodiment the headers 20, 22„ tubes 28, and fins

30 are all made of aluminum and brazed with an appropriate braze material. However, it should be understood that in some applications other suitable materials made be employed for these components as dictated by the parameters of the particular application.

It should also be understood that while the heat exchanger 10 illustrated in Figs. 1-3 is shown so that the longitudinal axes 24, 26 of the headers 20, 22 extend in a horizontal direction, and the parallel legs 36 of the tubes 28 extend in a vertical direction, it may be desirable in some applications for a heat exchanger 10 to have a different orientation, such as, for an example, an orientation wherein the axes 24, 26 extend in a vertical direction and the parallel legs 36 extend in a horizontal direction. Further, while the headers 20, 22 of the heat exchanger 10 illustrated in Figs. 1 -3 are located on the same side of the heat exchanger 10, it may be desirable in some applications for the headers 20, 22 to be located on opposite sides of the heat exchanger 10. A construction with the headers 20, 22 on the same side of the heat exchanger will typically result in an even number of parallel legs 36 for each of the tubes 28, while a construction with the headers 20,

22 on opposite sides of the heat exchanger 10 will typically result in a odd number of parallel legs 36 for each of the tubes 28. Of course, header plates fitted with tanks could be employed in lieu of the tubular headers 20, 22 if desired for a particular application.

Claims

I CLAIM:

1. A heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle, the heat exchanger comprising: a pair of elongated headers having longitudinal axes disposed substantially parallel to each other; a plurality of elongated tubes spaced in side by side relation along the longitudinal axes of the headers, each of the tubes having a flattened cross- section with a major dimension and a minor dimension, each of the tubes having a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers, each of the tubes being folded upon itself to define at least two parallel legs of the tube so that the working fluid flows serially through-at least two parallel fluid passes from one of the headers. to the other, the parallel legs of each of the tubes being spaced from each other with the major dimension of each of the parallel legs lying in a common plane that is substantially transverse to the longitudinal axes of the headers; and serpentine fins extending between adjacent pairs of said tubes, each of the fins having a length extending parallel to the parallel legs of the adjacent tubes and a transverse width extending across the at least two parallel legs of the adjacent tubes, each of the fins including a plurality of alternating tabs and elongated separations extending parallel to the parallel legs, the tabs and separations located between the parallel legs of the adjacent tubes to divide the width of each fin into a plurality of discrete fin elements that are connected to each other by the tabs, each of the fin elements corresponding to and extending along one of the parallel legs of each of the adjacent tubes.

2. The heat exchanger of claim 1 wherein the major dimension of each of the tubes is no greater than .500 inch and the minor dimension is no greater than .100 inch.

3. The heat exchanger of claim 1 wherein the major dimension of each of the tubes is no greater than .320 inch and the minor dimension

^' is no greater than .060 inch.

4. The heat exchanger of claim 1 wherein each of the tubes is folded at least twice to define at least three parallel legs of the tube so that the working fluid flows serially through at least three parallel fluid passes from one of the headers to the other.

5. The heat exchanger of claim 1 wherein each of the fins have a fin height extending from one the tubes to an adjacent one of the tubes, parallel to the longitudinal axes of the headers, and the major dimension of the tubes is no greater than the fin height.

6. The heat exchanger of claim 1 wherein the major dimension of each of the tube ends extends parallel to the longitudinal axes of the headers at the location where the tube end is connected to the header.

7. The heat exchanger of claim 1 wherein said separations in said fins are slits that do not require removal of fin material when formed in the fins.

8. The heat exchanger of claim 1 wherein said separations in said fins are slots that do require removal of fin material when formed in the fins.

9. The heat exchanger of claim 1 wherein, for at least one of the fins in an unfolded state of the fin, said separations and said tabs have lengths extending parallel with the length of the fin, and the ratio of the lengths of the separations to the lengths of the tabs is in the range of 200 to 600.

10. The heat exchanger of claim 1 wherein at least one of the tubes is a multi-port tube having a hydraulic diameter in the range of .015 inch to .040 inch.

11. A heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle, the heat exchanger comprising: a pair of elongated headers having longitudinal axes disposed substantially parallel to each other; a plurality of elongated tubes spaced in side by side relation along the longitudinal axes of the headers, each of the tubes having a flattened cross- section with a major dimension and a minor dimension, each of the tubes having a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers, each of the tubes being folded upon itself to define at least two parallel legs of the tube so that the working fluid flows serially through at least two parallel fluid passes from one of the headers to the other, the parallel iegs of each of the tubes having their major dimensions lying in a common plane that is substantially transverse to the longitudinal axes of the headers; and serpentine fins extending between adjacent pairs of said tubes, each of the fins having a length extending parallel to the parallel legs of the adjacent tubes and a transverse width extending across the. at least two parallel legs of the adjacent tubes, each of the fins including a plurality of alternating tabs and elongated separations extending parallel to the parallel legs, the tabs and separations located between the parallel legs of each of the adjacent tubes to divide the width of each fin into a plurality of discrete fin elements that are connected to each other by the tabs, each of the fin elements corresponding to and extending along one of the parallel legs of each of the adjacent tubes.

12. The heat exchanger of claim 11 wherein the major dimension of each of the tubes is no greater than .500 inch and the minor dimension is no greater than .100 inch.

13. The heat exchanger of claim 11 wherein the major dimension of each of the tubes is no greater than .320 inch and the minor dimension is no greater than .060 inch.

14. The heat exchanger of claim 11 wherein each of the tubes is folded at least twice to define at least three parallel legs of the tube so that the working fluid flows serially through at least three parallel fluid passes from one of the headers to the other.

15. The heat exchanger of claim 11 wherein the major dimension of each of the tube ends extends parallel to the longitudinal axes of the headers at the location where the tube end is connected to the header.

16. The heat exchanger of claim 11 wherein said separations in said fins are slits that do not require removal of fin material when formed in the fins.

17. The heat exchanger of claim 11 wherein, for at least one of the fins in an unfolded state of the fin, said separations and said tabs have lengths extending parallel with the length of the fin, and the ratio of the lengths of the separations to the lengths of the tabs is in the range of 200 to

600.

18. A heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle, the heat exchanger comprising: a pair of elongated headers having longitudinal axes disposed substantially parallel to each other; a plurality of elongated tubes spaced in side by side relation along the longitudinal axes of the headers, each of the tubes having a flattened cross- section with a major dimension and a minor dimension, the major dimension of each of the tubes being no greater than .500 inch and the minor dimension being no greater than .100 inch, each of the tubes having a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers, each of the tubes being folded upon itself to define at least two parallel legs of the tube so that the working fluid flows serially through at least two parallel fluid passes from one of the headers to the other, the parallel legs of each of the tubes having their major dimensions lying in a common plane that is substantially transverse to the longitudinal axes of the headers; and serpentine fins extending between adjacent pairs of said tubes, each of the fins having a length extending parallel to the parallel legs of the adjacent tubes.

19. A heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle, the heat exchanger comprising: a pair of elongated headers having longitudinal axes disposed substantially parallel to each other; a plurality of elongated tubes spaced in side by side relation along the longitudinal axes of the headers, each of the tubes having a flattened cross- section with a major dimension and a minor dimension, each of the tubes having a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers, each of the tubes being folded upon itself at least twice to define at least three parallel legs of the tube so that the working fluid flows serially through at least three parallel fluid passes from one of the headers to the other, the parallel legs of each of the tubes having their major dimensions lying in a common plane that is substantially transverse to the longitudinal axes of the headers; and serpentine fins extending between adjacent pairs of said tubes, each of the fins having a length extending parallel to the parallel legs of the adjacent tubes.

20. A heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle, the heat exchanger comprising: a pair of elongated headers having longitudinal axes disposed substantially parallel to each other; a plurality of elongated tubes spaced in side by side relation along the longitudinal axes of the headers, each of the tubes having.a flattened cross- section with a major dimension and a minor dimension, each of the tubes being a multi-port tube with a hydraulic diameter in the range of.015 inch to.040 inch, each of the tubes having a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers, each of the tubes being folded upon itself to define at least two parallel legs of the tube so that the working fluid flows serially through at least two parallel fluid passes from one of the headers to the other, the parallel legs of each of the tubes having their major dimensions lying in a common plane that is substantially transverse to the longitudinal axes of the headers; and serpentine fins extending between adjacent pairs of said tubes, each of the fins having a length extending parallel to the parallel legs of the adjacent tubes.