US20060144051A1

US20060144051A1 - Evaporator designs for achieving high cooling performance at high superheats

Info

Publication number: US20060144051A1
Application number: US11/030,431
Authority: US
Inventors: Sunil Mehendale; Steven Papapanu
Original assignee: Delphi Technologies Inc
Current assignee: Delphi Technologies Inc
Priority date: 2005-01-06
Filing date: 2005-01-06
Publication date: 2006-07-06

Abstract

An evaporator includes plates disposed in pairs in first and second groups, along spaced tanks. Dimples extend from the interior portions in the first group, and interior fins are disposed against the interior portions of the second group. The dimples enhance the distribution of liquid refrigerant in the passageways and the thermal energy exchange between ambient air and an upstream, low vapor quality flow of fluid passing between upstream and downstream side edges, of the first group of plates. The evaporator also eliminates the tonal noise or whistle under certain transient operating conditions.

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention
This invention relates to a heat exchanger for use in a vehicle climate control system. More specifically, the invention relates to an evaporator for transferring heat between a cross-flow of air through the evaporator and a refrigerant circulating within the evaporator.
2. Description of the Related Art
Various evaporator designs exist in the art that incorporate components for promoting heat exchange between a refrigerant fluid flowing within tubes and air flowing through fins that are disposed on the exterior surfaces of the tubes. The tubes typically incorporate features that force the refrigerant entering the evaporator to flow in a number of passes before it exits the evaporator. The evaporators often also include specific modifications to the interior surfaces of the tubes, which increase the surface area available for heat exchange between the ambient air and the fluid. For example, some evaporators are formed entirely of tubes having interior surfaces upon which interior fins are disposed. Other evaporators utilize tubes having interior surfaces from which “dimpled”, or “bumped”, protrusions extend into the interior (refrigerant side) of the evaporator.
While interior fins and “bumped” or “dimpled” surfaces increase heat exchange within the evaporator, limiting use of one or the other of the fins or dimples throughout all of the tubes in an evaporator is not necessarily the optimum way to maximize heat exchange. This is especially the case in climate control systems utilizing thermostatic expansion valves (“TXVs”). In a TXV system, the evaporator outlet superheat is normally set at about 15° F.; however, when a TXV system is under transient operation, the superheat can increase to 30° F. or more. This reduces cooling capacity and causes the temperature distribution of the discharge air to become more non-uniform.
Another problem with dimpled evaporators is that under certain transient vehicle operating conditions, vapor flowing over the dimples gives rise to a pure tone noise or “whistle” emanating from the evaporator. By providing fins inside the refrigerant tube plates in appropriate locations, as described in this invention, it is possible to eliminate this whistling transient noise.

BRIEF SUMMARY OF THE INVENTION AND ADVANTAGES

The invention provides a laminate-type evaporator having first and second tanks and fabricated from a plurality of plates. Each plate has upstream and downstream side edges with an interior portion recessed relative thereto. The plates are disposed in pairs with the side edges of each pair in abutting engagement with one another and the interior portions defining a passageway between each pair. The pairs are spaced along the tanks in first and second groups, and the passageways are in fluid communication with the tanks for permitting a fluid to flow between the tanks through the passageways. A thermal energy exchange occurs between the fluid and a cross-flow of air through the first and second groups from the upstream to downstream side edges. Dimples extend from the interior portions into the passageways of the first group. Interior fins are disposed against the interior portions and extend to the upstream and downstream side edges, which enhances the thermal energy exchange between the fluid and the cross-flow of air between the upstream and downstream side edges of the second group of plates.
Disposing dimples on the first group of plates enhances the thermal energy exchange between the air and a first flow of the fluid passing from the upstream to downstream side edges of the first group of plates. The fins on the second group of plates enhance thermal energy exchange between the air and a second flow of fluid passing from the upstream to downstream side edges of the second group of plates independently and separately from the first flow of fluid.
The subject invention overcomes the limitations of the art by providing an evaporator which utilizes tubes having interior fins in combination with a separate, distinct group of tubes having interior surfaces upon which dimples are formed. The interior fins are utilized in those tubes which define the final refrigerant passes of the evaporator. Doing so reduces refrigerant side thermal resistance by providing increased refrigerant side surface area to compensate for the decrease in the refrigerant side heat transfer coefficient that often occurs in the last passes of evaporators, especially in those operating at high outlet superheats. Additionally, providing interior fins in the final refrigerant passes also improves the thermal contact between the air fins and the tubes, because the tubes in this region of the evaporator have no dimples. Thus, in the final evaporator passes, a higher overall heat transfer coefficient is achieved resulting from reduced thermal resistance on the refrigerant side and in the conduction path from the air fins to the tube. Tubes having dimples formed on the interior surfaces are utilized in the initial refrigerant passes on the upstream airside of the evaporator where high refrigerant side surface area is not critical to initiate heat exchange, because of the prevailing high refrigerant side heat transfer coefficients associated with low to medium vapor quality two-phase flow. Providing interior fins in the final refrigerant passes also eliminates the tonal noise or whistle originating in the evaporator under certain transient operating conditions. This is because high velocity refrigerant vapor flow over the dimples in the last passes is the cause of a phenomenon called acoustic resonance, which is perceptible as whistling. Combining different surface enhancements by providing them only where they are truly necessary reduces total evaporator mass, decreases manufacturing costs, eliminates transient whistling noise, and improves heat exchange efficiency and temperature uniformity and stability.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

Other advantages of the present invention will be readily appreciated as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
FIG. 1 is an exploded perspective view of an evaporator according to one embodiment of the present invention;
FIG. 2 is a cross-sectional view taken along line 2-2 of the second group of plates in the evaporator shown in FIG. 1;
FIG. 3 is a cross-sectional perspective view of a selected plurality of the second group of plates in the evaporator shown in FIG. 1;
FIG. 4 is an exploded perspective view of an evaporator according to an alternative embodiment of the invention;
FIG. 5 is a fragmentary perspective view of the second group of plates in the evaporator shown in FIG. 4;
FIG. 6 is a cross-sectional view taken along line 6-6 of FIG. 4 of plate pairs and exterior fins in the second group of the evaporator, and
FIG. 7 is a cross sectional view across the bottom of the left most group shown in FIG. 4.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the Figures, wherein like numerals indicate like or corresponding parts throughout the several views, a laminate-type evaporator is generally shown at 10 in FIGS. 1 through 3. The evaporator 10 includes upper and lower or first and second tanks 12, 14 and is fabricated from a plurality of plates 16.
Each of the plates 16 has upstream and downstream side edges 18, 20 with an interior portion 22 recessed relative thereto. As shown in FIG. 2, the plates 16 are disposed in pairs 24, with the side edges 18 and 20 in overlapping and abutting engagement with one another such that the interior portions 22 define a passageway 26 between the plates 16 in each pair 24.
Referring now to FIG. 1, the pairs 24 are spaced along the tanks 12, 14 in first and second groups 28, 30 with the passageways 26 in fluid communication with the tanks 12, 14. The manner in which the passageways 26 are interconnected permits a fluid, or fluid stream of refrigerant, 32 to flow through the passageways 26 for allowing a thermal energy exchange to occur between the fluid 32 which flows through the passageways 26 in a specific number of passes or circuits and a cross-flow of air across the first and second groups 28, 30 from the upstream side edges 18 to the downstream side edges 20.
The evaporator 10 also includes a plurality of dimples 34 which extend from the interior portions 22 of the first group 28 of plates 16 into the passageways 26 for enhancing the thermal energy exchange between the fluid 32 and the cross-flow of air between the upstream and downstream side edges 18, 20. The thermal efficiency of the evaporator 10 is further improved by a plurality of interior fins 36. The fins 36 are disposed against the interior portions 22 of the second group of plates 30. As shown in FIG. 3, the fins 36 extend to the upstream and downstream side edges 18, 20 of the plates 16 in the second group 30.
Disposing the dimples 34 on the first group 28 of plates 16 enhances the thermal energy exchange of air with the flow of the fluid 32 passing between the upstream and downstream side edges 18, 20 of the first group 28 of plates 16, while the fins 36 on the second group 30 of plates 16 enhance the thermal energy exchange of air with the flow of the fluid 32 passing through the second group of plates 30.
As is best shown in FIG. 2, which shows a representative example of the plates 16 used in the second group 30, each plate 16 includes a pair of tubular projections 38 disposed within the periphery of the plates 16. The interior portion 22 interconnects and is in fluid communication with the projections 38. The tubular projections 38 on the plates 16 are in abutting engagement with one another, which in turn defines the upper and lower tanks 12, 14.
The plates 16 include upper and lower side edges 40, 42 that interconnect the upstream and downstream side edges 18, 20. The upper tank 12 is disposed adjacent the upper edges 40, and the lower tank 14 is disposed adjacent the lower side edges 42. The tanks 12, 14 are in fluid communication with the passageways 26, which permits the fluid 32 to flow between the first and second groups 28, 30 of plates 16.
The evaporator 10 also includes exterior fins 48 which are disposed against the exterior surfaces of the adjacent pairs 24 of plates 16. The fins 48 extend from the upper tank 12 to the lower tank 14. Each exterior fin 48 has a plurality of folds 50. The folds 50 extend perpendicularly to the longitudinal axes 51 of the plates 16 between the upstream and downstream side edges 18, 20. The orientation of the folds 50 relative to the longitudinal axis 51 of each plate 16 maximizes the total surface area available on the exterior fins 48 for transferring thermal energy between the cross-flow of air and the fluid 32 as the air passes across the exterior fins 48 from the upstream to downstream side edges 18, 20 of the plates 16.
The evaporator 10 also has upstream or right and downstream or left endplates 52, 54. The upstream endplate 52 is disposed against that plate 16 which is located rightmost from the remaining plates 16 forming the first group 28. The right endplate 52 includes an inlet aperture 56. As is shown in FIG. 1, the endplate 52 is positioned in longitudinal alignment with the plates 16 in the first group 28, with the inlet aperture 56 in axial alignment with the upper tank 12.
The left endplate 54 includes an outlet aperture 58, and is positioned against that plate 16 which is located leftmost from the rest of the plates 16 in the second group 30. Like the inlet aperture 56, the outlet aperture 58 is in axial alignment with the upper tank 12 for permitting the fluid 32 to exit the evaporator 10 after flowing through the plates 16 in the second group 30.
The evaporator 10 is configured in a manner that directs the fluid 32 through a plurality of passes through the passageways 26 and across the path of the cross-flow of air through the exterior fins 48. As is shown in FIG. 1, a downstream flow separator 60 directs the fluid 32 to flow from the first group 28 of plates 16 to the second group 30. The downstream flow separator 60 may be positioned in either the upper or lower tank 12, 14 and fabricated from any components suitable for diverting the flow of fluid 32 from one tank 12, 14 to the other. However, as is shown in FIG. 1, the downstream flow separator 60 consists of a planar surface, or blind 62 which is disposed across one of the tubular projections 38 that form the upper tank 12 to block and divert flow.
The blind 62 is disposed in the upper tank 12 within the tubular projection 38 of the first plate pair 24 positioned immediately downstream from the first group 28 of plates 16. Positioning the blind 62 in this location prevents the fluid 32 from flowing further to the left in the upper tank 12 past the blind 62, and instead diverts the fluid 32 to flow into the lower tank 14 through the plate pairs 24 of the third pass of the first group 28. From the lower tank 14, the fluid 32 then flows through the plate pairs 24 in the second group 30.
The evaporator 10 also utilizes upstream and intermediate flow separators 64, 66, which consist of blinds 68, 70 identical in shape and structure to the blind 62 described above with reference to the first flow separator 60. The blind 68 which forms the rightmost flow separator 64 is disposed within the upper tank 12 intermediate two of the plate pairs 24 that are located in the first group 28 a predetermined distance to the left of the inlet aperture 56.
The intermediate flow separator 66 is positioned within the first group 28 to the left of the rightmost flow separator 64. However, in contrast to the blind 68, the blind 70 forming the intermediate flow separator 66 is disposed within the lower tank 14 between a plate pair 24 located a predetermined distance to the right of the flow separator 60, and a plate pair 24 located a predetermined distance to the left of the upstream flow separator 64.
Although any number of flow separators may be utilized in the evaporator 10 to define flow path configurations with any number of passes, the rightmost, leftmost and intermediate flow separators 64, 60, 66 are utilized in combination with the upstream and downstream endplates 52, 54 to define four passes through the evaporator 10 in the particular case shown in FIG. 1. Specifically, upon entering the evaporator 10 by passing through the inlet aperture 56, the fluid 32 flows into the upper tank 12, encounters the blind 68 of the rightmost flow separator 64, and is diverted through the passageways 26 defined by the first group 28 of plates 16 into the lower tank 14 to complete a first pass through the evaporator 10.
The fluid 32 continues to flow to the left through the lower tank 14 and is diverted through the passageways 26 located immediately between the intermediate blind 70 and the rightmost blind 68. The fluid 32 flows back into the upper tank 12, thus completing a second pass through the evaporator 10.
The fluid 32 completes a third pass through the first group 28 by flowing to the left through the upper tank 12 to the flow separator 60. The blind 62 defining the flow separator 60 causes the fluid 32 to flow through the passageways 26 of the selected group of the plate pairs 24 in the first group 28 positioned immediately upstream from the second group 30. The fluid 32 is diverted back into the second tank 14 and into the second group 30 of plates 16. The fluid 32 then makes a fourth, or final, pass from the second tank 14, through the passageways 26 and across the interior fins 36 of the plates 16 in the second group 30 prior to re-entering the upper tank 12 and exiting the evaporator 10 through the outlet aperture 58 located in the left end plate 54.
Referring now to FIGS. 4 through 7, an evaporator according to an alternative embodiment of the invention is generally shown at 110. The evaporator 110 includes many of the same components and is formed from the same materials as the evaporator 10. Like elements are numbered the same as the first embodiment but differ by one hundred (100) The plates 116 of the evaporator 110 include upstream and downstream side edges 118, 120 that interconnect upper and lower edges 140, 142. Each plate 116 also includes a pair of tubular projections 138 interconnected by an interior portion 122. However, in contrast to each pair of tubular projections 38 of the evaporator 10, each projection 138 in the evaporator 110 is disposed adjacent the upper edge 140 of a selected one of the plates 116. The tubular projections 138 form first and second tanks 112, 114. Unlike the tanks 12, 14 of the evaporator 10, the first and second tanks 112, 114 in the evaporator 110 are disposed adjacent the upper edges 140 of the plates 116.
In contrast to the plates 16 utilized in the evaporator 10, the interior portions 122 of the plates 116 in both the first group 128 and the second group, generally shown at 130 in FIGS. 5, 6 and 7 each include a central rib defined by an elongate projection 172. The rib 172 extends from the interior portion 122 to abut a like rib 172 in the opposite plate 116 to define a first recess 174 adjacent the upstream side edges 118 and a second recess 176 adjacent the downstream side edge 120. A return recess interconnects the first and second recesses 174, 176. As is best shown in FIG. 5, the ribs 172 in each of the adjacent pairs 124 of plates 116 in the second group 130 are in abutting engagement with one another such that the passageways 126 define a plurality of U-shaped channels 180 interconnecting the first and second tanks 112, 114.
As is shown in FIG. 5, each of the plates 116 also includes first and second flanges 182, 184 that extend from each of the lower edges 142. The first flange 182 has a shape complementary to that of the second flange 184. As is shown in FIG. 4, this permits the first and second flanges 182, 184 to be placed in interlocking engagement with respective second and first flanges 184, 182 on an adjacent plate 116 to define an evaporator base 186.
While the exterior fins 148 are disposed against the exterior surfaces of the adjacent pairs 124 of plates 116, in contrast to the exterior fins 48 of the evaporator 10, the fins 148 extend from the first and second tanks 112, 114 to the lower edges 142 of the plates 116 adjacent the base 186.
The U-shaped channels 180 affect both the rate of heat exchange within the evaporator 110 and the location of the interior fins 136 and dimples 134 disposed within the passageways 126. As is shown in FIGS. 5 and 6, the interior fins 136 on each of the plates 116 in the second group 130 include a first fin group 188. The first fin group 188 is disposed against the first recess 174 adjacent the upstream side edge 118. A second fin group 190 is disposed against the second recess 176 adjacent the downstream side edge 120.
Referring again to FIG. 4, the dimples 134 on the interior portions 122 of the plates 116 in the first group 128 are randomly dispersed across the first recesses 174, second recesses 176 and return recesses 178. Although not required, the evaporator 110 also has a plurality of second dimples 192, as shown in both FIGS. 4 and 7. As is shown in FIGS. 5 and 7, the second dimples 192 extend from the interior portion 122 and into the passageway 126 of each of the plates 116 in the second group 128, which further enhances distribution of liquid refrigerant and the thermal energy exchange between the fluid 132 flowing therethrough and the cross-flow of air flowing through the evaporator 110 from the upstream to downstream side edges 118, 120. The second dimples 192 extend from the interior portions 122 intermediate the first and second fin groups 188, 190. Specifically, the second dimples 192 extend from one or more of the return recesses 178.
The evaporator 110 utilizes right or upstream and left or downstream endplates 152, 154 which have respective inlet and outlet apertures 156, 158. The endplates 152, 154 are identically shaped. The right endplate 152 is disposed against that plate 116 which is located to the right of the remaining plates 116 that constitute the first plate group 128. The endplate 152 is disposed in abutting engagement with the aforementioned plate 116 with the inlet aperture 156 in axial alignment with the first tank 112. The left endplate 154 is similarly disposed against the plate 116 in the second group 130 which is located furthest to the left of the other plates 116 of the evaporator 110. The left endplate 154 is oriented in axial alignment with the first tank 112 with the outlet aperture 158 adjacent the side edge 118. As described in greater detail below, this allows the fluid 132 to exit the evaporator 110 after flowing through the passageways 126 in the second group 130.
The evaporator 110 utilizes right and left flow separators 164, 160 to direct the fluid 132 through a predetermined flow configuration within the evaporator 110. In order to accommodate the U-shaped configuration of the plates 116, the shape and components of the flow separators 160, 164 differ from those utilized in the evaporator 10. In particular, the left flow separator 160 includes a planar surface, or blind 194. The blind 194 covers a selected one of the tubular projections 138 in a single plate pair 124 positioned intermediate the first and second plate groups 128, 130. As is shown in FIG. 4, the blind 194 covers the tubular projection 138 on the first plate 116 immediately to the right of the second group 130, which in turn blocks the leftmost portion of the second tank 114. The blind 194 effectively blocks the fluid 132 from flowing further to the left through the second tank 114 and from the second tank 114, through the U-shaped channels 180 within the second group 130. After the fluid 132 exits the first plate group 128, it first flows through the leftmost portion of tank 112, then through the U-shaped channels 180 within the second group 130, and finally the fluid 132 flows through the leftmost portion of the second tank 114 prior to exiting the evaporator 110 through the outlet aperture 158.
The upstream flow separator 164 includes a single blind 198, which covers a tubular projection 138 in a selected plate 116 in the first group 128. In particular, the blind 198 covers the projection 138 located adjacent the downstream side edge 120, which effectively blocks the portion of first tank 112 to the left of blind 198. The blind 198 diverts the fluid 132 to flow in a first pass through the U-shaped channels 180, over the dimples 134 and into the second tank 114. The fluid 132 continues flowing through the second tank 114 and encounters the other blind 194 in the second tank 114 and is then diverted to flow in a second pass through the U-shaped channels 180 of a selected plurality of plates 116 in the first group 128. These plates 116 are located immediately to the right of the second group 130. The fluid 132 then flows back into the first tank 112 and flows in a third, or final, pass through the second plate group 130 in the manner described above.
While the invention has been described with reference to an exemplary embodiment, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed as the best mode contemplated for carrying out this invention, but that the invention will include all embodiments falling within the scope of the appended claims.

Claims

1. A laminate-type evaporator comprising:

a first tank;

a second tank;

a plurality of plates each having upstream and downstream side edges in spaced relation to one another and an interior portion recessed relative to said side edges;

said plates disposed in pairs with said side edges, of each pair in abutting engagement with one another and said interior portions defining a passageway between each pair of plates;

said pairs spaced along said tanks, in first and second groups, with said passageways in fluid communication with said first and second tanks, for permitting a fluid to flow between said tanks through said passageways for allowing a thermal energy exchange between the fluid and a cross-flow of air through said first and second groups from said upstream side edge to said downstream side edge;

a plurality of dimples extending from said interior portions of said first group of plates into said passageways for enhancing the distribution of liquid refrigerant in said passageways and the thermal energy exchange between the fluid and the cross-flow of air between said upstream and downstream side edges and

a plurality of interior fins disposed against said interior portions and extending to said upstream and downstream side edges of said second group of plates for enhancing the thermal energy exchange between the fluid and the cross-flow of air between said upstream and downstream side edges of said second group whereby said dimples of said first group of plates enhance the distribution of liquid refrigerant and the thermal energy exchange with an upstream flow of the low vapor quality fluid passing between said upstream and said downstream side edges of said first group of plates while said fins of said second group of plates enhance the thermal energy exchange with a downstream flow of the high vapor quality fluid passing between said upstream and said downstream side edges, of said second group of plates.

2. An evaporator as recited in claim 1 wherein each of said plates includes a pair of tubular projections with said interior portion interconnecting said pair of tubular projections in fluid communication therewith and said pairs of tubular projections on said plates in abutting engagement with one another to define said first and second tanks.

3. An evaporator as recited in claim 2 wherein said plates include upper and lower edges interconnecting said upstream and downstream side edges with said first tank disposed adjacent said upper edges and said second tank disposed adjacent said lower edges.

4. An evaporator as recited in claim 2 wherein said plates include upper and lower edges interconnecting said upstream and downstream side edges with said first and second tanks disposed adjacent said upper edges.

5. An evaporator as recited in claim 4 wherein each of said interior portions of said second group of plates include a central rib extending from said interior portion to define a first recess adjacent said upstream said edge, a second recess adjacent said downstream side edge and a return recess interconnecting said first and second recesses, said central ribs in each of said adjacent pairs of said plates in said second group in abutting engagement with one another wherein said recesses define a plurality of U-shaped channels interconnecting said first and second tanks.

6. An evaporator as recited in claim 5 wherein said interior fins on each of said plates in said second group include a first fin group disposed against said first recess.

7. An evaporator as recited in claim 5 wherein said interior fins on each of said plates in said second group include a second fin group disposed against said second recess.

8. An evaporator as recited in claim 7 and including a plurality of second dimples extending from said interior portions of said second group of plates into said passageways for enhancing the distribution of liquid refrigerant and the thermal energy exchange between the fluid flowing therethrough and the cross-flow of air.

9. An evaporator as recited in claim 8 wherein said second dimples extend from said interior portions intermediate said first and second fin groups.

10. An evaporator as recited in claim 9 wherein said second dimples extend from said return recesses.

11. An evaporator as recited in claim 1 including at least two groups of said second group of plates including said fins with four or more groups of said first group of plates.

12. An evaporator as recited in claim 1 including one or two groups of said second group of plates including said fins with four or more groups of said first group of plates.