Temperature control heat exchanger for battery

Abstract

In a heat exchanger 10, a supply pipe part 15 and a discharge pipe part 16 are provided at asymmetric positions with respect to a central axis in the width direction. The heat exchanger 10 has two or more upstream-side flow paths R1a, R1b, R1c, R1d, R1e extending along the central axis, two or more downstream-side flow paths R1f, R1g, R1h, R1i, R1j extending along the central axis, and a first aggregation flow path R1k.

Description

Battery temperature control heat exchanger

[0001] The present disclosure relates to a temperature control heat exchanger for a battery for controlling the temperature of the battery.

[0002] For example, vehicles equipped with a traction motor, such as hybrid vehicles and electric vehicles, may be equipped with a drive battery. In the vehicles disclosed in Patent Documents 1 to 4, a cooling member having a refrigerant passage therein is disposed below the battery module of the drive battery. The cooling member is connected to a refrigerant supply pipe that supplies refrigerant to the refrigerant passage and a refrigerant discharge pipe that discharges refrigerant from the refrigerant passage. The refrigerant supply pipe and the refrigerant discharge pipe are disposed in the center of the vehicle body in the vehicle width direction, and multiple cooling members extend from the refrigerant supply pipe and the refrigerant discharge pipe toward both sides in the vehicle width direction.

[0003] JP 2019-186149 A JP 2020-187966 A JP 2020-187967 A JP 2020-187968 A

[0004] In order to suppress temperature variations between cells, the flow pattern of the heat-carrying fluid inside a temperature-control heat exchanger for a battery may be set so that the fluid flows from one side of the stacking direction of the cells to the other side, then makes a U-turn and returns. In this case, the different flow path lengths of the multiple flow paths tend to cause a flow rate bias toward the inside of the central axis extending in the flow direction of the flow path. One method to reduce this bias is to partially change the cross-sectional area of ​​the flow path by providing a restriction, but this method has the problems of being difficult to adjust and increasing pressure loss due to the restriction.

[0005] The present disclosure has been made in consideration of the above points, and an object thereof is to make it difficult for temperature variations to occur between cells while suppressing an increase in pressure loss.

[0006] In order to achieve the above object, one aspect of the present disclosure can be a temperature control heat exchanger for a battery configured to allow a heat carrier fluid to flow therethrough and to regulate the temperature of a battery module, wherein a supply pipe section to which the heat carrier fluid is supplied and a discharge pipe section to which the heat carrier fluid is discharged are provided at asymmetric positions with respect to a central axis passing through the center in the width direction. The temperature control heat exchanger for a battery has three or more upstream flow paths connected to the supply pipe section and extending from one side to the other along the central axis on the side where the supply pipe section is located, closer to the central axis; three or more downstream flow paths connected to the discharge pipe section and extending from one side to the other along the central axis on the side where the discharge pipe section is located, closer to the central axis; and a first consolidation flow path that consolidates the downstream sides of at least two of the upstream flow paths and extends in a direction intersecting the central axis, and is connected to the upstream sides of at least two of the downstream flow paths, and a flow path among the upstream flow paths other than the flow path that is connected to the first consolidation flow path is connected to the discharge pipe section without being consolidated.

[0007] According to this configuration, the heat-carrying fluid supplied from the supply pipe flows into three or more upstream flow paths and circulates from one side to the other along the central axis. Because the downstream sides of the upstream flow paths are connected to the first converging flow path, the heat-carrying fluid that has flowed through two or more upstream flow paths is converged in the first converging flow path and then flows in a direction intersecting the central axis. The heat-carrying fluid that has flowed through the first converging flow path flows into two or more downstream flow paths and then circulates toward one side. The flow of the heat-carrying fluid bends at least two times: once when flowing from the upstream flow path into the first converging flow path and once when flowing from the first converging flow path into the downstream flow path. By converging multiple flows in the first converging flow path and bending the flow path at least two times, the flow rates of the heat-carrying fluid flowing through each upstream flow path and each downstream flow path can be made nearly uniform even when the supply pipe and the discharge pipe are positioned asymmetrically with respect to the widthwise central axis. This reduces temperature variations between cells without the need for a throttle.

[0008] Furthermore, the configuration can include a second collecting flow path that collects the downstream sides of at least two of the upstream flow paths that are not connected to the first collecting flow path and extends in a direction intersecting the central axis, and that is connected to the upstream sides of at least two of the downstream flow paths that are not connected to the first collecting flow path.

[0009] The total cross-sectional area of ​​the upstream flow paths may be different from the cross-sectional area of ​​the intermediate portion of the first collecting flow path. The total cross-sectional area of ​​the upstream flow paths may be set to be larger than the cross-sectional area of ​​the intermediate portion of the first collecting flow path.

[0010] The upstream flow path communicating with the first collecting path may include a flow path having the shortest flow length from the supply pipe to the discharge pipe. In this case, when a total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths communicating with the first collecting path among the plurality of upstream flow paths is defined as A, a total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths communicating with the second collecting path among the plurality of upstream flow paths is defined as B, a cross-sectional area of ​​an intermediate portion of the first collecting path is defined as a, and a cross-sectional area of ​​the intermediate portion of the second collecting path is defined as b, the cross-sectional areas of the intermediate portions of the first collecting path and the second collecting path can be set so that a / b is a value obtained by multiplying A / B by a coefficient equal to or greater than 0.36 and equal to or less than 0.93.

[0011] The extending direction of the upstream flow path and the extending direction of the downstream flow path may be set to be parallel to the stacking direction of the cells of the battery module.

[0012] A total cross-sectional area obtained by summing the cross-sectional areas of the upstream flow paths communicating with the first collecting flow path may be set to be equal to a total cross-sectional area obtained by summing the cross-sectional areas of the downstream flow paths communicating with the first collecting flow path. Also, a total cross-sectional area obtained by summing the cross-sectional areas of the upstream flow paths communicating with the second collecting flow path may be set to be equal to a total cross-sectional area obtained by summing the cross-sectional areas of the downstream flow paths communicating with the second collecting flow path.

[0013] As described above, since the multiple flows of the heat carrier fluid are collected in the collecting flow path and bent at least twice, the flow rate of the heat carrier fluid flowing through each upstream flow path and each downstream flow path can be made nearly uniform without providing a restriction, which makes it possible to suppress temperature variations between cells while suppressing an increase in pressure loss.

[0014] FIG. 1 is a plan view showing a state in which a temperature control heat exchanger for a battery according to an embodiment of the present invention is in use. FIG. 2 is a rear view showing a state in which the temperature control heat exchanger for a battery is in use. FIG. 3 is a plan view showing the positional relationship between a first heat exchanger and a second heat exchanger. FIG. 4 is a perspective view of the first heat exchanger. FIG. 5 is a view equivalent to FIG. 4 showing a first flow path. FIG. 6 is a perspective view of the first heat exchanger as seen from below. FIG. 7 is a right side view of the first heat exchanger. FIG. 8 is a view showing the relationship between the stacking direction of cells in a battery module and the first flow path. FIG. 9 is a view illustrating the relationship between the heights of the supply pipe section and the discharge pipe section. FIG. 10 is a view equivalent to FIG. 9 when the number of heat exchangers is increased. FIG. 11 is a view illustrating details of the first flow path. FIG. 12 is a graph showing the relationship between a coefficient related to the cross-sectional area of ​​the flow path and flow rate variation.

[0015] Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Note that the following description of the preferred embodiments is merely exemplary in nature and is not intended to limit the present invention, its applications, or its uses.

[0016] 1 and 2 show a state in which a battery temperature control heat exchanger 1 according to an embodiment of the present invention is used. The battery temperature control heat exchanger 1 is used to regulate the temperature of battery modules B1 and B2. The battery modules B1 and B2 are drive batteries mounted in a vehicle equipped with a traction motor, such as a hybrid vehicle (including a plug-in hybrid) or an electric vehicle. The locations where the battery modules B1 and B2 are mounted are not particularly limited, but examples include below a floor panel (not shown), below a seat (not shown), or inside a trunk (not shown).

[0017] The temperatures of the battery modules B1 and B2 must be kept within a predetermined temperature range during charging and discharging, so the temperatures of the battery modules B1 and B2 are adjusted by the battery temperature control heat exchanger 1. For example, if the temperatures of the battery modules B1 and B2 are low and unsuitable for charging and discharging, the temperatures of the battery modules B1 and B2 are increased by the battery temperature control heat exchanger 1. Conversely, if the temperatures of the battery modules B1 and B2 are high and unsuitable for charging and discharging, the temperatures of the battery modules B1 and B2 are decreased by the battery temperature control heat exchanger 1.

[0018] In the description of this embodiment, for convenience of explanation, the right side, left side, front side, and rear side are defined as shown in each drawing. The right side is the right side of the vehicle, the left side is the left side of the vehicle, the front side is the front side of the vehicle, and the rear side is the rear side of the vehicle. In each drawing, the left-right direction is the vehicle width direction. The definitions of these directions may be reversed.

[0019] The battery modules constituting the drive battery of this embodiment include a left battery module B1 mounted on the left side of the vehicle and a right battery module B2 mounted on the right side. The left battery module B1 and the right battery module B2 are arranged with a gap between them in the left-right direction.

[0020] The left battery module B1 and the right battery module B2 have the same size and capacity. Therefore, in principle, the left battery module B1 and the right battery module B2 need to be heated and cooled in the same way. However, the left battery module B1 and the right battery module B2 may have different sizes and capacities. Furthermore, the number of battery modules is not particularly limited, and multiple battery modules may be arranged in the front-to-rear direction.

[0021] The battery temperature control heat exchanger 1 includes a first heat exchanger 10 and a second heat exchanger 20 configured to allow a heat carrier fluid to flow therethrough. The battery temperature control heat exchanger 1 may be configured only with the first heat exchanger 10. The first heat exchanger 10 has a shape as shown in FIGS. 4 to 7 and is disposed below the left battery module B1 as shown in FIG. 2. The second heat exchanger 20 is disposed below the right battery module B2 so as to be aligned with the first heat exchanger 10 in the left-right direction. In this embodiment, the battery temperature control heat exchanger 1 is configured such that the first heat exchanger 10 regulates the temperature of the left battery module B1, and the second heat exchanger 20 regulates the temperature of the right battery module B2. In other words, the first heat exchanger 10 and the second heat exchanger 20 are aligned in the same direction as the left battery module B1 and the right battery module B2. A gap is provided between the first heat exchanger 10 and the second heat exchanger 20 so that the first heat exchanger 10 and the second heat exchanger 20 do not come into contact with each other.

[0022] Although not shown, when the battery modules are arranged in a line in the front-to-back direction, the first heat exchanger 10 and the second heat exchanger 20 can be arranged in a line in the front-to-back direction in accordance with the arrangement direction of the battery modules.

[0023] The first heat exchanger 10 has a first flow path R1 through which a heat-carrying fluid can flow. The detailed shape of the first flow path R1 is shown in FIG. 5 . As shown in FIG. 8 , the arrangement direction (left-right direction) of the multiple cells constituting the left battery module B1 coincides with the extension direction of the first flow path R1. The upstream end R1A of the first flow path R1 is located at the right end and front portion of the first heat exchanger 10. The downstream end R1B of the first flow path R1 is located at the right end and rear portion of the first heat exchanger 10. Therefore, the upstream end R1A of the first flow path R1 and the downstream end R1B of the first flow path R1 are spaced apart from each other in the front-rear direction.

[0024] If the temperature of the heat-carrying fluid flowing into the upstream end R1A of the first flow path R1 is higher than the temperature of the left battery module B1, the left battery module B1 can be heated. Conversely, if the temperature of the heat-carrying fluid flowing into the upstream end R1A of the first flow path R1 is lower than the temperature of the left battery module B1, the left battery module B1 can be cooled.

[0025] The first heat exchanger 10 is formed by joining an upper plate 11 and a lower plate 12. The upper plate 11 is a member that forms the upper portion of the first heat exchanger 10. The lower plate 12 is a member that forms the lower portion of the first heat exchanger 10. The upper plate 11 and the lower plate 12 are made of a metal material with high thermal conductivity, such as an aluminum alloy. The upper plate 11 is flat. The upper surface of the upper plate 11 is positioned so as to contact the lower surface of the left battery module B1. By making the upper plate 11 flat, the upper surface of the upper plate 11 becomes flat, ensuring a large contact area with the lower surface of the left battery module B1.

[0026] As shown in Figure 6, the lower plate 12 has a bulge 12a that bulges downward to correspond to the shape of the first flow path R1. Because the bulge 12a for forming the first flow path R1 is provided only on the lower plate 12, the upper surface of the upper plate 11 can be made flat. By joining the upper surface of the lower plate 12 and the lower surface of the upper plate 11, the first heat exchanger 10 having the first flow path R1 formed therein is obtained. The manufacturing method for the first heat exchanger 10 is not limited to the above-described manufacturing method, and any manufacturing method may be used.

[0027] 3, a first front extension 13 extending to the right is integrally formed with the right end and front portion of the first heat exchanger 10. The upstream end R1A of the first flow path R1 extends until it reaches the inside of the first front extension 13. A first rear extension 14 extending to the right is integrally formed with the right end and rear portion of the first heat exchanger 10. The downstream end R1B of the first flow path R1 extends until it reaches the inside of the first rear extension 14.

[0028] The first heat exchanger 10 is provided on the second heat exchanger 20 side with a first supply pipe 15 that supplies the heat carrier fluid to the first flow path R1 and a first discharge pipe 16 that discharges the heat carrier fluid from the first flow path R1. The first supply pipe 15 is provided in the first front extension 13, which extends to the right, i.e., protrudes to the right, so that the first supply pipe 15 protrudes from the end of the first heat exchanger 10 toward the second heat exchanger 20. The first discharge pipe 16 is provided in the first rear extension 14, which extends to the right, i.e., protrudes to the right, so that the first discharge pipe 16 protrudes from the end of the first heat exchanger 10 toward the second heat exchanger 20. The first supply pipe 15 and the first discharge pipe 16 are positioned in the center in the vehicle width direction.

[0029] The first supply pipe 15 protrudes upward from the first front extension 13. The lower end of the first supply pipe 15 is the downstream end of the first supply pipe 15 and is connected to the upstream end R1A of the first flow path R1 located inside the first front extension 13.

[0030] The first discharge pipe 16 protrudes upward from the first rear extension 14. The lower end of the first discharge pipe 16 is the upstream end of the second supply pipe 16 and is connected to the downstream end R1B of the first flow path R1 located inside the first rear extension 14.

[0031] The second heat exchanger 20 is configured with the same heat exchanger as the first heat exchanger 10, and can be used as the second heat exchanger 20 by rotating the first heat exchanger 10 180 degrees around the vertical axis. In other words, the first heat exchanger 10 and the second heat exchanger 20 are configured with common parts, and the first heat exchanger 10 can be used as the second heat exchanger 20, and the second heat exchanger 20 can be used as the first heat exchanger 10.

[0032] That is, the second heat exchanger 20, like the first heat exchanger 10, has a second flow path R2 (shown by a dashed line in FIG. 3 ) therein through which a heat-carrying fluid can flow. The upstream end R2A of the second flow path R2 is located at the left end and in the front portion of the second heat exchanger 20. The downstream end R2B of the second flow path R2 is located at the left end and in the rear portion of the second heat exchanger 20. Therefore, the upstream end R2A of the second flow path R2 and the downstream end R2B of the second flow path R2 are spaced apart from each other in the front-to-rear direction.

[0033] 2, the second heat exchanger 20 is configured by joining an upper plate 21 and a lower plate 22, similar to the first heat exchanger 10. The lower plate 22 has a bulging portion 22a that bulges downward in accordance with the shape of the second flow path R2.

[0034] 3, a second front extension 23 extending to the left is integrally formed with the left end and front portion of the second heat exchanger 20. The upstream end R2A of the second flow path R2 extends until it reaches the inside of the second front extension 23. A second rear extension 24 extending to the left is integrally formed with the left end and rear portion of the second heat exchanger 20. The downstream end R2B of the second flow path R2 extends until it reaches the inside of the second rear extension 24.

[0035] The second heat exchanger 20 is provided on the first heat exchanger 10 side with a second supply pipe 25 that supplies the heat carrier fluid to the second flow path R2 and a second discharge pipe 26 that discharges the heat carrier fluid from the second flow path R2. The second supply pipe 25 is provided in the second front extension 23, which extends to the left, i.e., protrudes to the left, so that the second supply pipe 25 protrudes from the end of the second heat exchanger 20 toward the first heat exchanger 10. The second discharge pipe 26 is provided in the second rear extension 24, which extends to the left, i.e., protrudes to the left, so that the second discharge pipe 26 protrudes from the end of the second heat exchanger 20 toward the first heat exchanger 10. The second supply pipe 25 and the second discharge pipe 26 are positioned in the center in the vehicle width direction.

[0036] The second supply pipe 25 protrudes upward from the second front extension 23. The lower end of the second supply pipe 25 is the downstream end of the second supply pipe 25 and is connected to the upstream end R2A of the second flow path R2 located inside the second front extension 23.

[0037] The second discharge pipe 26 protrudes upward from the second rear extension 24. The lower end of the second discharge pipe 26 is the upstream end of the second discharge pipe 26 and is connected to the downstream end R2B of the second flow path R2 located inside the second rear extension 24.

[0038] The first supply pipe 15, the first discharge pipe 16, the second supply pipe 25, and the second discharge pipe 26 are positioned in the left-right center of the battery temperature control heat exchanger 1 and are aligned in a straight line in the front-to-rear direction. When the battery temperature control heat exchanger 1 is viewed from the front-to-rear direction, the first supply pipe 15, the first discharge pipe 16, the second supply pipe 25, and the second discharge pipe 26 are arranged so as to overlap one another.

[0039] The second supply pipe section 25 is located at the front end, and the first discharge pipe section 16 is located at the rear end. The first supply pipe section 15 is located behind the second supply pipe section 25, and the second discharge pipe section 26 is located in front of the first discharge pipe section 16. In other words, the first supply pipe section 15 and the second supply pipe section 25 are arranged adjacent to each other in the front-to-rear direction, and the first discharge pipe section 16 and the second discharge pipe section 26 are arranged adjacent to each other in the front-to-rear direction.

[0040] A common supply pipe P1 (shown in FIG. 1) is connected to the first supply pipe section 15 and the second supply pipe section 25. A common discharge pipe P2 (shown in FIG. 1) is connected to the first discharge pipe section 16 and the second discharge pipe section 26. The height of the upper ends of the first supply pipe section 15 and the second supply pipe section 25 may be the same as the height of the upper ends of the first discharge pipe section 16 and the second discharge pipe section 26, or, as shown in FIG. 9, the height of the upper ends of the first supply pipe section 15 and the second supply pipe section 25 may be lower than the height of the upper ends of the first discharge pipe section 16 and the second discharge pipe section 26. In the case shown in FIG. 9, the supply pipe P1 can be disposed directly below the discharge pipe P2, thereby reducing the horizontal dimension of the space required to install the supply pipe P1 and the discharge pipe P2.

[0041] The number of heat exchangers constituting the battery temperature control heat exchanger 1 is not limited to two. Fig. 10 shows a case where the number of heat exchangers constituting the battery temperature control heat exchanger 1 is increased, and even when the battery temperature control heat exchanger 1 further includes supply pipes 33 and 34, a common supply pipe P1 can be used to connect to the first supply pipe 15 and the second supply pipe 25. In this case, the supply pipe P1 can be diverted so as not to interfere with the discharge pipe P2.

[0042] A pump (not shown) for feeding the heat-carrying fluid is provided upstream of the supply pipe P1, and operating the pump causes the heat-carrying fluid to flow into the supply pipe P1. A heating device and a cooling device (neither of which are shown) are also provided upstream of the supply pipe P1. The heating device and the cooling device detect the temperature state of the battery modules B1 and B2, and operate to lower the temperature of the heat-carrying fluid when the temperature state of the battery modules B1 and B2 is such that cooling is required, while they operate to raise the temperature of the heat-carrying fluid when the temperature state of the battery modules B1 and B2 is such that heating is required. This circuit configuration allows the heat-carrying fluid at a desired temperature state to circulate within the battery temperature control heat exchanger 1.

[0043] (Details of the Flow Paths of the Heat Exchanger) FIG. 11 is a diagram illustrating the details of the first flow path R1 formed inside the first heat exchanger 10. In FIG. 11, the width direction and the longitudinal direction of the first heat exchanger 10 are defined. The width direction of the first heat exchanger 10 is the front-rear direction in FIG. 1. The longitudinal direction of the first heat exchanger 10 is the left-right direction in FIG. 1. The dashed dotted line indicated by the symbol L in FIG. 11 passes through the center of the first heat exchanger 10 in the width direction, extends in the longitudinal direction, and indicates the central axis of the first heat exchanger 10. The central axis of the first heat exchanger 10 is defined imaginarily.

[0044] The first flow path R1 has a flat shape. The first supply pipe 15, which supplies the heat carrier fluid to the first flow path R1, and the first discharge pipe 16, which discharges the heat carrier fluid from the first flow path R1, are located asymmetrically with respect to the central axis L of the first heat exchanger 10 in the width direction. Specifically, the first supply pipe 15 is located away from one end (the left end in FIG. 11 ) of the first heat exchanger 10 in the width direction toward the other end (the right end in FIG. 11 ), while the first discharge pipe 16 is located at the other end (the right end in FIG. 11 ) of the first heat exchanger 10 in the width direction. Therefore, the distance between the first supply pipe 15 and the central axis L is shorter than the distance between the first discharge pipe 16 and the central axis L. Note that the first supply pipe 15 and the first discharge pipe 16 may be located in opposite positions relative to the central axis L.

[0045] The first flow path R1 includes five upstream flow paths R1a, R1b, R1c, R1d, and R1e, five downstream flow paths R1f, R1g, R1h, R1i, and R1j, a first consolidation flow path R1k, and a second consolidation flow path R1l. That is, the first heat exchanger 10 has four or more upstream flow paths R1a, R1b, R1c, R1d, and R1e, four or more downstream flow paths R1f, R1g, R1h, R1i, and R1j, the first consolidation flow path R1k, and the second consolidation flow path R1l. The extension directions of the upstream flow paths R1a, R1b, R1c, R1d, and R1e and the extension directions of the downstream flow paths R1f, R1g, R1h, R1i, and R1j are set to be parallel to the stacking direction of the cells of the battery module B1 (the left-right direction in FIG. 8 ).

[0046] The number of upstream flow paths is not limited to five, and may be any number as long as the first collecting flow path R1k and the second collecting flow path R1l can be provided. The number of downstream flow paths is also not limited to five, and may be any number as long as the first collecting flow path R1k and the second collecting flow path R1l can be provided. The length and width of each flow path can be set as desired.

[0047] The upstream ends of the upstream flow paths R1a, R1b, R1c, R1d, and R1e are each connected to the first supply pipe 15. The upstream flow paths R1a, R1b, R1c, R1d, and R1e extend linearly from one longitudinal side to the other along the central axis L on the side where the first supply pipe 15 is provided relative to the central axis L of the first heat exchanger 10, i.e., on the left side of the central axis L of the first heat exchanger 10 in FIG. 11 . The upstream flow paths R1a, R1b, R1c, R1d, and R1e are parallel to each other. The cross-sectional areas of the upstream flow paths R1a, R1b, R1c, R1d, and R1e are set to be the same. The cross-sectional areas are the cross-sectional areas when the flow paths are cut in a direction perpendicular to the flow paths. The same applies hereinafter.

[0048] The downstream ends of the downstream flow paths R1f, R1g, R1h, R1i, and R1j are each connected to the first discharge pipe section 16. The downstream flow paths R1f, R1g, R1h, R1i, and R1j extend linearly from one longitudinal side to the other along the central axis L on the side where the first discharge pipe section 16 is provided relative to the central axis L of the first heat exchanger 10, i.e., on the right side of the central axis L of the first heat exchanger 10 in FIG. 11 . The downstream flow paths R1f, R1g, R1h, R1i, and R1j are parallel to one another. The cross-sectional areas of the downstream flow paths R1f, R1g, R1h, R1i, and R1j are set to be the same.

[0049] The first consolidation flow path R1k is connected to the downstream sides of the upstream flow paths R1c, R1d, and R1e, which are located on the inner side in the width direction of the first heat exchanger 10, among the upstream flow paths R1a, R1b, R1c, R1d, and R1e, and extends in a direction intersecting the central axis L. The downstream side of the first consolidation flow path R1k is connected to the upstream sides of the downstream flow paths R1f, R1g, and R1h, which are located on the inner side in the width direction of the first heat exchanger 10, among the downstream flow paths R1f, R1g, R1h, R1i, and R1j. Because the first consolidation flow path R1k is connected to the downstream sides of the three upstream flow paths R1c, R1d, and R1e, the downstream sides of the three upstream flow paths R1c, R1d, and R1e are consolidated by the single first consolidation flow path R1k.

[0050] The second collecting flow path R1l extends in a direction intersecting the central axis L at a location farther from the first supply pipe portion 15 and the first discharge pipe portion 16 than the first collecting flow path R1k. The upstream side of the second collecting flow path R1l is connected to the downstream side of the upstream flow paths R1a, R1b, which are not connected to the first collecting flow path R1k. The downstream side of the second collecting flow path R1l is connected to the upstream side of the downstream flow paths R1i, R1j, which are not connected to the first collecting flow path R1k. Since the second collecting flow path R1l is connected to the downstream side of the two upstream flow paths R1a, R1b, the downstream sides of at least two of the upstream flow paths R1a, R1b, which are not connected to the first collecting flow path R1k, are collected by the second collecting flow path R1l.

[0051] The total cross-sectional area of ​​the upstream flow paths R1c, R1d, and R1e communicating with the first collecting flow path R1k is different from the cross-sectional area of ​​a middle portion of the first collecting flow path R1k. Specifically, the total cross-sectional area of ​​the upstream flow paths R1c, R1d, and R1e communicating with the first collecting flow path R1k is set to be larger than the cross-sectional area of ​​the middle portion of the first collecting flow path R1k. The middle portion of the first collecting flow path R1k is the portion between the portion of the upstream flow paths R1c, R1d, and R1e that is closest to the central axis L and the portion of the downstream flow paths R1f, R1g, and R1h that is closest to the central axis L and is connected to the downstream flow path R1f.

[0052] Furthermore, the total cross-sectional area of ​​the upstream flow paths R1a and R1b communicating with the second converging flow path R1l is different from the cross-sectional area of ​​a middle portion of the second converging flow path R1l. Specifically, the total cross-sectional area of ​​the upstream flow paths R1a and R1b communicating with the second converging flow path R1l is set to be larger than the cross-sectional area of ​​the middle portion of the second converging flow path R1l. The middle portion of the second converging flow path R1l is the portion between the portion of the upstream flow paths R1a and R1b that is closest to the central axis L and the portion of the downstream flow paths R1i and R1j that is closest to the central axis L and communicates with the downstream flow path R1i.

[0053] The total cross-sectional area of ​​the upstream flow paths R1c, R1d, and R1e communicating with the first collecting flow path R1k is set to be the same as the total cross-sectional area of ​​the downstream flow paths R1f, R1g, and R1h communicating with the first collecting flow path R1k. Also, the total cross-sectional area of ​​the upstream flow paths R1a and R1b communicating with the second collecting flow path R1l is set to be the same as the total cross-sectional area of ​​the downstream flow paths R1i and R1j communicating with the second collecting flow path R1l.

[0054] As described above, the number of upstream flow paths R1c, R1d, and R1e communicating with the first collecting flow path R1k is three, while the number of upstream flow paths R1a and R1b communicating with the second collecting flow path R1l is two. In this manner, in this embodiment, the number of upstream flow paths R1c, R1d, and R1e communicating with the first collecting flow path R1k is set to be greater than the number of upstream flow paths R1a and R1b communicating with the second collecting flow path R1l.

[0055] Here, the total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths R1c, R1d, and R1e that communicate with the first collecting flow path R1k among the multiple upstream flow paths R1a, R1b, R1c, R1d, and R1e is defined as A. Furthermore, the total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths R1a and R1b that communicate with the second collecting flow path R1l among the multiple upstream flow paths R1a, R1b, R1c, R1d, and R1e is defined as B. Furthermore, the cross-sectional area of ​​the intermediate portion of the first collecting flow path R1k is defined as a, and the cross-sectional area of ​​the intermediate portion of the second collecting flow path R1l is defined as b. The cross-sectional areas of the intermediate portions of the first collecting flow path R1k and the second collecting flow path R1l are set so that a / b is a value obtained by multiplying A / B by a coefficient of 0.36 or more and 0.93 or less.

[0056] 12 is a graph showing the relationship between the coefficient and the flow rate variation in the upstream flow paths R1c, R1d, and R1e that communicate with the first collecting flow path R1k and the upstream flow paths R1a and R1b that communicate with the second collecting flow path R1l. The flow rate variation (%) can be calculated using the following formula.

[0057] Equal flow rate ratio (%) in the middle section of the first collecting flow path R1k = (number of upstream flow paths connected to the first collecting flow path R1k / total number of upstream flow paths) × 100 In this example, the number of upstream flow paths connected to the first collecting flow path R1k is 3, and the total number of upstream flow paths is 5.

[0058] Flow rate variation (%) = Actual flow rate ratio (%) of the middle portion of the first converging flow path R1k - Equal flow rate ratio (%) As shown in Figure 12, by setting the coefficient between 0.36 and 0.93, the flow rate variation is within a range of plus or minus 5%. In other words, when the flow rate variation exceeds 5%, the temperature variation on the top surface of the heat-carrying fluid inlet side of the first heat exchanger 10 increases. At even lower flow rates, this temperature variation increases. However, by keeping the flow rate variation within 5%, the temperature variation on the top surface of the heat-carrying fluid inlet side of the first heat exchanger 10 is reduced to a practically acceptable range. Therefore, the coefficient is set to a range between 0.36 and 0.93. The flow rate variation analysis was performed using GT-SUITE analysis software. The heat-carrying fluid was 50% LLC, the heat-carrying fluid flow rate was 2 liters / minute, and the battery module temperature was fixed at 40°C. Heat transfer to the surroundings was adiabatic.

[0059] (Effects of the embodiment) As described above, according to the present embodiment, the temperature of the battery modules B1, B2 can be regulated by supplying a heat carrier fluid to the first flow paths R1 and second flow paths R2 of the first heat exchanger 10 and the second heat exchanger 20 disposed below the battery modules B1, B2. Because the battery temperature control heat exchanger 1 is divided into the first heat exchanger 10 and the second heat exchanger 20, even if the driving battery is enlarged, the first heat exchanger 10 and the second heat exchanger 20 do not need to be as long as conventional cooling members. This reduces the costs of manufacturing and transporting the first heat exchanger 10 and the second heat exchanger 20, and makes the first heat exchanger 10 and the second heat exchanger 20 less likely to deform during transport.

[0060] Furthermore, since the first supply pipe 15 and the first discharge pipe 16 and the second supply pipe 25 and the second discharge pipe 26 can be concentrated between the first heat exchanger 10 and the second heat exchanger 20, the space occupied by the supply pipe P1 connected to the supply pipes 15 and 25 and the discharge pipe P2 connected to the discharge pipes 16 and 26 can be reduced. As a result, the space available for mounting the battery modules B1 and B2 can be expanded, and the energy density can be improved. Furthermore, the supply pipe P1 connected to the supply pipes 15 and 25 and the discharge pipe P2 connected to the discharge pipes 16 and 26 can be shortened, thereby improving the cooling and heating capabilities of the battery modules B1 and B2.

[0061] 11 , the heat-carrying fluid supplied from the supply pipe 15 of the first heat exchanger 10 flows into the upstream flow paths R1a, R1b, R1c, R1d, and R1e and circulates from one side to the other in the longitudinal direction along the central axis L. Since the downstream sides of the upstream flow paths R1c, R1d, and R1e are connected to the first converging flow path R1k, the heat-carrying fluid flowing through the upstream flow paths R1c, R1d, and R1e is converged in the first converging flow path R1k and then flows in a direction intersecting the central axis L. The heat-carrying fluid flowing through the first converging flow path R1k flows into the downstream flow paths R1f, R1g, and R1h and then circulates toward one side in the longitudinal direction. The flow of the heat transfer fluid bends at least twice: once when flowing from the upstream flow paths R1c, R1d, and R1e into the first converging flow path R1k, and once when flowing from the first converging flow path R1k into the downstream flow paths R1f, R1g, and R1h. By converging multiple flows in the first converging flow path R1k and bending the flow path at least twice, the flow rates of the heat transfer fluid flowing through the upstream flow paths R1c, R1d, and R1e and the downstream flow paths R1f, R1g, and R1h can be made nearly uniform even when the supply pipe 15 and the discharge pipe 16 are positioned asymmetrically with respect to the central axis L. This reduces temperature variations between cells without the need for a throttle. The same applies to the second converging flow path R1l.

[0062] The above-described embodiments are merely examples in all respects and should not be construed as limiting. Furthermore, all modifications and variations within the scope of the claims are within the scope of the present invention.

[0063] As described above, the temperature control heat exchanger for a battery according to the present invention can be used to control the temperature of a drive battery in, for example, a hybrid vehicle, an electric vehicle, or the like.

[0064] REFERENCE SIGNS LIST 1 Battery temperature control heat exchanger 10 First heat exchanger 15 First supply pipe section 16 First discharge pipe section B1, B2 Battery module R1a, R1b, R1c, R1d, R1e Upstream flow path R1f, R1g, R1h, R1i, R1j Downstream flow path R1k First collecting flow path R1l Second collecting flow path

Claims

1. A temperature control heat exchanger for a battery configured to allow a heat carrier fluid to flow therethrough and for controlling the temperature of a battery module, wherein a supply pipe section to which a heat carrier fluid is supplied and a discharge pipe section to which the heat carrier fluid is discharged are arranged at asymmetric positions with respect to a central axis passing through the center in the width direction, and the temperature control heat exchanger for a battery has three or more upstream flow paths connected to the supply pipe section and extending from one side to the other along the central axis on a side of the central axis where the supply pipe section is located, and three or more downstream flow paths connected to the discharge pipe section and extending from one side to the other along the central axis on a side of the central axis where the discharge pipe section is located, and a first consolidation flow path that consolidates the downstream sides of at least two of the upstream flow paths and extends in a direction intersecting the central axis, and is connected to the upstream sides of at least two of the downstream flow paths, and among the upstream flow paths, a flow path different from a flow path connected to the first consolidation flow path is connected to the discharge pipe section.

2. A temperature control heat exchanger for a battery as described in claim 1, further comprising a second collecting flow path that collects the downstream sides of at least two of the upstream flow paths that are not connected to the first collecting flow path and extends in a direction intersecting the central axis, and that is connected to the upstream sides of at least two of the downstream flow paths that are not connected to the first collecting flow path.

3. The temperature control heat exchanger for a battery according to claim 1, which has only one first collecting flow path.

4. A temperature control heat exchanger for a battery as described in claim 1, wherein the total cross-sectional area of ​​the multiple upstream flow paths connected to the first collecting flow path is different from the cross-sectional area of ​​the middle part of the first collecting flow path.

5. A temperature control heat exchanger for a battery as described in claim 4, wherein the total cross-sectional area of ​​the plurality of upstream flow paths is set to be larger than the cross-sectional area of ​​the middle part of the first collecting flow path.

6. A temperature regulating heat exchanger for a battery as described in claim 2, wherein the upstream flow path communicating with the first collecting path includes a flow path with the shortest flow length from the supply pipe section to the discharge pipe section, and wherein the total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths communicating with the first collecting path among the plurality of upstream flow paths is A, and the total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths communicating with the second collecting path among the plurality of upstream flow paths is B, and the cross-sectional area of ​​the intermediate part of the first collecting path and the cross-sectional area of ​​the intermediate part of the second collecting path are set so that a / b is a value obtained by multiplying A / B by a coefficient of 0.36 or more and 0.93 or less.

7. A temperature control heat exchanger for a battery as described in claim 1, wherein the direction in which the upstream flow path extends and the direction in which the downstream flow path extends are set to be parallel to the stacking direction of the cells of the battery module.

8. A temperature control heat exchanger for a battery as described in claim 1, wherein the total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths communicating with the first collecting flow path is set to be the same as the total cross-sectional area obtained by adding up the cross-sectional areas of the downstream flow paths communicating with the first collecting flow path.

9. A temperature control heat exchanger for a battery as described in claim 2, wherein the total cross-sectional area obtained by adding up the cross-sectional areas of the upstream flow paths communicating with the second collecting flow path is set to be the same as the total cross-sectional area obtained by adding up the cross-sectional areas of the downstream flow paths communicating with the second collecting flow path.

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