CN112640187A

CN112640187A - Cooling module of battery for vehicle

Info

Publication number: CN112640187A
Application number: CN202080004842.8A
Authority: CN
Inventors: 垣内修司; 仓桥和也; 李承知; 王鸣笛
Original assignee: Valeo Japan Co Ltd
Current assignee: Valeo Japan Co Ltd
Priority date: 2019-03-01
Filing date: 2020-02-28
Publication date: 2021-04-09
Also published as: WO2020179651A1; JPWO2020179651A1

Abstract

Even under the condition that the refrigerant in the pipeline at the downstream side of the refrigerant flow path of the cooling module has superheat degree, the battery degradation caused by heat generation can be restrained. A cooling module (20) for cooling a battery (10) is provided with a first header (22), a second header (24), and a plurality of pipelines (26), wherein the first header (22) is provided with a refrigerant inflow part (221) for inflow of a refrigerant for exchanging heat with the battery and a refrigerant outflow part (222) for outflow of the refrigerant for exchanging heat with the battery, and the plurality of pipelines (26) are arranged between the first header and the second header and are used for exchanging heat with the battery. The plurality of tube paths are composed of one or more first tube paths (26A) for flowing the refrigerant from the first header to the second header and one or more second tube paths (26B) for flowing the refrigerant from the second header to the first header, and the sum of the areas of the heat exchange surfaces of the first tube paths with the battery is larger than the sum of the areas of the heat exchange surfaces of the second tube paths with the battery.

Description

Cooling module of battery for vehicle

Technical Field

The present invention relates to a cooling module for a vehicle battery.

Background

Electric vehicles and hybrid vehicles travel using electric energy stored in a rechargeable battery. The battery is cooled in order to suppress deterioration of the battery due to heat generation during charging of the battery. Patent document 1 discloses a refrigerant cooling module for cooling a battery.

The cooling module of patent document 1 has a plurality of flat pipes (refrigerant pipes) provided between two header pipes (headers) and in contact with the batteries. When the battery is cooled, the refrigerant flowing through the pipe on the upstream side of the refrigerant flow path formed by the header pipe and the pipe is in a gas-liquid mixed state sufficiently containing liquid, and the battery has sufficient cooling capacity. The refrigerant is heated by the heat of the battery while flowing through the pipe, whereby the proportion of the refrigerant in a liquid state decreases and the proportion of the refrigerant in a gas state increases.

When the refrigerant flow rate is small or the heat generation amount of the battery is large, the refrigerant flowing through the pipe on the downstream side of the refrigerant flow path may be completely vaporized and may have a superheat (superheated) degree in the vicinity of the downstream end of the pipe. In such a situation, there is a problem that the cooling capacity is reduced and the temperature distribution of the battery becomes uneven.

Documents of the prior art

Patent document

Patent document 1: japanese unexamined patent application publication No. 2016-035378

Disclosure of Invention

Technical problem to be solved by the invention

The purpose of the present invention is to provide a technique that can suppress battery degradation due to heat generation even in a situation where the refrigerant in the pipe line on the downstream side of the refrigerant flow path of the cooling module has a degree of superheat.

Technical solution for solving technical problem

According to an embodiment of the present invention, there is provided a cooling module for cooling a vehicle battery, the cooling module including a first header, a second header, and a plurality of pipes, the first header has a refrigerant inflow portion into which a refrigerant having exchanged heat with the battery flows and a refrigerant outflow portion from which a refrigerant having exchanged heat with the battery flows, the plurality of tubes are arranged between the first header and the second header for exchanging heat with the battery, the plurality of tubes are composed of one or more first tubes for flowing the refrigerant from the first header to the second header and one or more second tubes for flowing the refrigerant from the second header to the first header, the sum of the areas of the heat exchange surfaces of the one or more first tubes with the battery is larger than the sum of the areas of the heat exchange surfaces of the one or more second tubes.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the above embodiment, even in a state where the refrigerant has a degree of superheat, deterioration of the battery due to heat generation can be suppressed.

Drawings

Fig. 1 is a schematic side view of a cooling module according to a first embodiment of the present invention.

Fig. 2 is a schematic side view of a cooling module according to a second embodiment of the present invention.

Fig. 3 is a schematic side view of a cooling module of a comparative example.

Fig. 4 is a schematic cross-sectional view showing a cross section of the pipe and the battery cut along a vertical plane perpendicular to the longitudinal direction of the pipe.

Fig. 5 is a schematic cross-sectional view showing a cross section obtained by cutting the pipe line, the battery, and the header with a vertical plane parallel to the longitudinal direction of the pipe line.

Fig. 6 is a circuit diagram showing an example of a refrigeration cycle apparatus incorporating a cooling module.

Fig. 7 is a schematic side view of a cooling module according to a third embodiment of the present invention.

Fig. 8 is a schematic side view of a cooling module according to a fourth embodiment of the present invention.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

A first embodiment will be described with reference to fig. 1.

The cooling module 20 has a first header (manifold) 22, a second header (manifold) 24, and a plurality of (four in the embodiment of fig. 1) tubes 26 arranged between the first header 22 and the second header 24.

The plurality of lines 26 preferably have the same dimensions for reasons of manufacturing technology (extrusion die outlay, uniformity of soldering, etc.). The surface of the battery 10 (battery module) for a vehicle is in thermal contact with the side surface of each pipe 26 directly or indirectly (preferably, directly as shown in fig. 4).

The first header 22 has a refrigerant inflow portion (inlet port) 221 into which a refrigerant having exchanged heat with the battery 10 flows, and a refrigerant outflow portion (outlet port) 222 from which a refrigerant having exchanged heat with the battery 10 flows. The interior of the first header 22 is divided by the partition wall 223 into an upper space on the refrigerant inflow portion 221 side and a lower space on the refrigerant outflow portion 222 side.

The refrigerant used in the embodiments described in the present specification is a heat medium used in a refrigeration cycle, and is a fluid that cools an object to be cooled by extracting heat equivalent to the heat of vaporization at the time of a phase change from a liquid phase to a gas phase from the object to be cooled. Specifically, as the refrigerant, a refrigerant for a vehicle air conditioner, for example, HFC-134a, HFO-1234yf that meets the recent EU regulation, and the like, which have been widely used conventionally, can be used.

The plurality of pipe lines 26 are classified into one or more first pipe lines 26A for flowing the refrigerant from the first header 22 to the second header 24 and one or more second pipe lines 26B for flowing the refrigerant from the second header 24 to the first header 22. The number of first conduits 26A is greater than the number of second conduits 26B. In the embodiment of fig. 1, three first lines 26A and one second line 26B are provided.

The plurality of pipes 26 are arranged in the vertical direction and extend in the horizontal direction. Preferably, the first conduit 26A is above the second conduit 26B. In this case, the refrigerant inflow portion 221 is located above the refrigerant outflow portion 222. The first header 22 and the second header 24 are arranged in parallel with each other and in the vertical direction.

As shown in fig. 4 and 5, each of the pipes 26 can be formed by an extruded profile having a plurality of channels (refrigerant flow paths) 261 extending in parallel with each other. As shown in fig. 5, the end portions of the pipes 26 are inserted into elongated slits formed in the first header 22, which is a hollow tubular member. A hollow tubular member constituting the refrigerant inflow portion 221 is inserted into a circular hole formed in the first header 22. The pipe line 26 and the refrigerant inflow portion (hollow tubular member) 221 are welded to the first header 22. In fig. 5, reference numeral 40 denotes solder.

The coupling structure of the first header 22 and the refrigerant outflow portion 222 and the coupling structure of the second header 24 and the respective tubes 26 are also the same as those shown in fig. 5. The tubes 26, the first header 22, and the second header 24 can be formed of a high thermal conductivity material, such as an aluminum alloy.

Fig. 6 shows an example of a refrigeration cycle apparatus 1 in which the cooling module 20 of the first embodiment is incorporated into a vehicle air conditioner. The refrigeration cycle apparatus 1 includes an outdoor heat exchanger 2, an indoor heat exchanger 3, a compressor 4, and an expansion valve 5, which are provided in a refrigerant circulation passage 7. The outdoor heat exchanger 2 is disposed, for example, behind a front grille of the vehicle. The indoor heat exchanger 3 is provided in a blower passage of an air conditioner, for example. With the air conditioning apparatus for a vehicle, a person skilled in the art performs air conditioning of the interior of the vehicle by a known method.

A pipe line 9 (refrigerant circuit) for the cooling module is connected to

branch points

8a and 8b provided in the refrigerant circulation path 7. The expansion valve 6 and the cooling module 20 of the first embodiment are provided in the pipe line 9. The

expansion valves

5,6 preferably have a function as a shut-off valve.

The quick charge of the battery 10 is generally performed at the stop (parking) of the vehicle. When the refrigerant does not need to flow into the indoor heat exchanger 3 during rapid charging of the battery 10, the expansion valve 5 functions as a shutoff valve. Therefore, at this time, the outdoor heat exchanger 2, the expansion valve 6, the cooling module 20, and the compressor 4 constitute a refrigeration cycle apparatus for cooling the battery 10. When it is necessary to flow the refrigerant to the indoor heat exchanger 3 during rapid charging of the battery 10, the

expansion valves

5 and 6 function as expansion valves. Therefore, at this time, the refrigerant discharged from the compressor 4 passes through the exterior heat exchanger 2 and is branched at the branch point 8a, and a part of the refrigerant flows through the expansion valve 5 and the interior heat exchanger 3, and another part of the refrigerant flows through the expansion valve 6 and the cooling module 20. Then, the flows of the two refrigerants merge at the branch point 8b and are sucked into the compressor 4. Therefore, a refrigeration cycle device for cooling the battery 10 is also configured at this time.

The cooling module of the first embodiment (and the cooling modules of the second to fourth embodiments described later) functions as an evaporator in the refrigeration cycle device for cooling a battery shown in fig. 6. In the refrigeration cycle apparatus shown in fig. 6, a refrigerant in a low-temperature low-pressure gas state flows into (is sucked into) the compressor 4, and is compressed in the compressor 4, thereby being in a high-temperature high-pressure gas state. Next, the refrigerant is cooled by heat exchange with ambient air (outside air) in the exterior heat exchanger 2 functioning as a condenser, and turns into a medium-temperature high-pressure liquid. The refrigerant is expanded while passing through the expansion valve 6, and becomes a low-temperature and low-pressure liquid or a gas-liquid mixed fluid. Then, the refrigerant is vaporized by heat exchange with the battery 10 when passing through the cooling module 20 functioning as an evaporator, and takes heat from the battery 10 by the heat of vaporization, and turns into a low-temperature low-pressure gas. Then, the refrigerant returns (is sucked into) the compressor 4 again and is compressed.

From the viewpoint of product cost, the refrigeration cycle device for cooling the battery is advantageously integrated with the refrigeration cycle for air conditioning as shown in fig. 6, but may be an independent refrigeration cycle device separate from the refrigeration cycle for air conditioning.

The operation of the cooling module 20 will be described in detail below. The arrows shown in fig. 1 to 3 indicate the flow direction and the state of the refrigerant, and the ratio of the refrigerant in a gaseous state contained in the refrigerant increases in the order of the thick solid line arrow, the thin solid line arrow, and the broken line arrow.

In the embodiment shown in fig. 1, the low-temperature and low-pressure refrigerant (a relatively low-temperature refrigerant in a liquid state or a gas-liquid mixed state containing a sufficient amount of liquid) flowing out of the expansion valve (for example, the expansion valve 6 in fig. 6) and flowing into the upper space of the first header 22 from the refrigerant inflow portion 221 flows out into the first pipe line 26A and flows in parallel through the three first pipe lines 26A. While passing through the first pipe 26A, the refrigerant exchanges heat with the battery 10, thereby cooling the battery 10. In the process of passing through the first pipe 26A, the refrigerant in a liquid state evaporates, and the proportion of gas increases. In the process of changing phase from liquid to gas, there is almost no change in temperature. The refrigerant flowing out of the first pipe line 26A to the second header 24 flows into one second pipe line 26B. The refrigerant also exchanges heat with the battery 10 while passing through the second duct 26B, thereby cooling the battery 10. The refrigerant in the liquid state is almost entirely vaporized while passing through the second pipe 26B. The refrigerant having passed through the second pipe line 26B flows into the lower space of the first header 22, passes through the refrigerant outflow portion 222, and flows out of the first header 22.

Fig. 2 shows a second embodiment. In fig. 2, the same or similar components as those in fig. 1 are denoted by the same reference numerals and redundant description is omitted.

The cooling module 20 shown in fig. 2 includes, in addition to the components of the cooling module 20 shown in fig. 1, a third header 28, a fourth header 30, one or more (two in the illustrated example) third tube paths 32A and one or more (one in the illustrated example) fourth tube paths 32B arranged between the third header 28 and the fourth header 30. In the embodiment of fig. 2, the number of first lines 26A is two, as is the number of third lines 32A. The interior of the second header 24 is divided into an upper side space and a lower side space by the partition wall 243. The interior of the third header 28 is divided into an upper side space and a lower side space by the partition wall 283.

The upper side space of the second header 24 and the upper side space of the third header 28 are connected by an upper side communication pipe 281.

The lower side space of the second header 24 and the lower side space of the third header 28 are connected by a lower communication pipe 282. The third and

fourth pipes

32A and 32B are in contact with another battery 10 (battery module) different from the battery 10 (battery module) with which the first and

second pipes

26A and 26B are in contact.

In the second embodiment, the refrigerant flowing into the upper space of the first header 22 from the refrigerant inflow portion 221 flows out to the two first tubes 26A. The refrigerant flows in parallel through the two first pipes 26A. While passing through the first pipe 26A, the refrigerant exchanges heat with the battery 10, thereby cooling the battery 10. The refrigerant flowing out of the first pipe 26A into the space above the second header 24 flows into the space above the third header 28 through the upper communication pipe 281. The refrigerant flowing out of the upper space of the third header 28 flows in parallel through the upper two third tubes 32A. The refrigerant exchanges heat with the battery 10 while passing through the third duct 32A, and cools the battery 10. The refrigerant flowing into the fourth header 30 from the third pipe line 32A flows into the lower one of the fourth pipe lines 32B. While passing through the fourth duct 32B, the refrigerant exchanges heat with the battery 10, thereby cooling the battery 10. The refrigerant flowing out of the fourth tube 32B into the space below the third header 28 flows into the space below the second header 24 through the lower communication tube 282. The refrigerant flowing out of the lower space of the second header 24 flows into one second pipe line 26B. The refrigerant exchanges heat with the battery 10 while passing through the second duct 26B, thereby cooling the battery 10.

In the second embodiment, as in the first embodiment, the refrigerant flowing through the first pipe line 26A is also in a low-temperature low-pressure liquid state or a gas-liquid mixed state containing a sufficient amount of liquid. Further, substantially all of the refrigerant flowing through the second pipe 26B may be in a gaseous state before flowing out of the second pipe 26B.

Advantages of the first and second embodiments will be described in comparison with a comparative example shown in fig. 3 configured based on conventional design ideas. Hereinafter, the second embodiment shown in fig. 2 is compared with the comparative example shown in fig. 3, but the advantages of the first embodiment shown in fig. 1 are also the same as those of the embodiment shown in fig. 2.

In fig. 2 and 3, the area of the portion where each duct 26(26A,26B) overlaps the battery 10 (the portion of the battery 10 that is located behind the duct 26) is the area of the heat exchange surface between one duct 26 and the battery 10 (hereinafter also referred to as "heat exchange area"). In fig. 2 and 3, the tubes 26 have the same shape and size, and therefore the heat exchange areas of the tubes are equal to each other by a value a ("a" is an appropriate positive number).

In the second embodiment, the number of the first pipe lines 26A overlapping the battery 10 in fig. 2 is 2, and therefore the total of the heat exchange areas of the two first pipe lines 26A is 2A. In fig. 2, the number of the second pipe lines 26B overlapping the battery 10 is 1, and therefore the total of the heat exchange areas of one second pipe line 26B is a.

According to the same concept as described above, in the comparative example shown in fig. 3, the sum total of the heat exchange areas of one first tube 26A is a, and the sum total of the heat exchange areas of two second tubes 26B is 2A.

When the mass flow rate of the refrigerant is constant, the volume flow rate of the refrigerant greatly increases when the ratio of the refrigerant in a gas state is increased by vaporization of the refrigerant by heat. As the volume flow rate of the refrigerant increases, the ventilation resistance when passing through the refrigerant passage increases. In consideration of this, according to the conventional design concept, as shown in fig. 3, the number of second lines 26B (the refrigerant flow in the gas supply state) which become bottlenecks in the refrigerant flow is increased (with respect to the mass flow rate) to ensure a sufficient mass flow rate of the refrigerant from the refrigerant inflow portion 221 to the refrigerant outflow portion 222.

On the other hand, in the first embodiment, the number of the second pipes 26B is reduced, and the number of the first pipes 26A through which the liquid-state refrigerant flows is substantially increased (it is to be noted that the total number of the pipes 26 is fixed for the reason of installation space). In this case, since the number of the second pipes 26B through which the refrigerant in a gaseous state substantially flows is reduced, the ventilation resistance when the refrigerant in a gaseous state passes through the refrigerant passage is increased, and as a result, the mass flow rate of the refrigerant from the refrigerant inflow portion 221 to the refrigerant outflow portion 222 is reduced to some extent.

However, since the ratio of the liquid in the refrigerant flowing through the first pipe passage 26A is sufficiently high, even if the flow rate of the refrigerant in the first pipe passage 26A is slightly reduced, the contact portion of the battery 10 with the first pipe passage 26A and the vicinity of the contact portion can be sufficiently cooled. Further, since the number of the first ducts 26A is larger than that of the comparative example, a larger range of one battery 10 (battery module) can be cooled.

After the refrigerant flowing through the second pipe 26B is completely vaporized (or after the refrigerant becomes an overheated state), the temperature of the refrigerant rises due to heat exchange with the battery 10, and the cooling effect of the battery 10 is reduced. That is, the region of the battery 10 in thermal contact with the second conduit 26B may not be cooled to the intended temperature.

Therefore, when the heat generation of the battery 10 is excessive or the cooling medium is not supplied to the cooling module 20 at a flow rate according to the heat generation of the battery 10, the cooling medium is completely vaporized at the time of flowing into the second pipe 26A or in the middle of passing through the second pipe 26, and becomes in a superheated (super) state until flowing out from the second pipe 26.

In such a situation, the cooling effect of the second duct 26B on the battery 10 is very low, and even if the number of second ducts 26B is increased, the cooling effect of the battery 10 cannot be improved. That is, increasing the number of the first ducts 26A to increase the total of the heat exchange areas of the first ducts 26A and the battery 10 is more advantageous for cooling the entire battery 10. The cooling of the region of battery 10 near second conduit 26B can also be performed by the movement of heat to the region of battery 10 cooled by first conduit 26A. All embodiments of the present invention (not only the first and second embodiments, but also the third and fourth embodiments) are based on the technical idea described above.

The mass flow rate of the refrigerant from the refrigerant inflow portion 221 to the refrigerant outflow portion 222 is secured in a trade-off relationship with the number of pipes through which the refrigerant sufficiently containing liquid flows. As a result of the studies by the inventors, it was found that increasing the number of first pipes 26A through which a refrigerant sufficiently containing a liquid flows is more advantageous for cooling the entire single battery 10, and the configuration of the above embodiment was obtained. That is, according to the above embodiment, even in the above situation, the cooling level required for the battery 10 can be maintained, and the life of the battery 10 can be prevented from being reduced.

The embodiment of the present invention is not limited to the first and second embodiments described above, and may be a third and fourth embodiment described below.

Fig. 7 shows a cooling module 20 according to a third embodiment. In fig. 7, the same or similar components as those in fig. 1 and 2 are denoted by the same reference numerals, and redundant description is omitted.

The cooling module 20 of the third embodiment has a plurality of pipes 26 for exchanging heat with the cells 10 between the first header 22 and the second header 24, as in the first and second embodiments described above. The cooling module 20 of the third embodiment has one or more (three in the illustrated example) first pipe lines 26A for flowing the refrigerant from the first header 22 to the second header 24 and one or more (three in the illustrated example) second pipe lines 26B for flowing the refrigerant from the second header 24 to the first header 22, as in the first and second embodiments.

In the cooling module 20 of the third embodiment, the second header pipe 24 is provided with the refrigerant outflow portion 242, unlike the first and second embodiments. Accordingly, the refrigerant flows from the first header 22 to the second header 24, then flows from the second header 24 to the first header 22, and then flows from the first header 22 to the second header 24 again. To realize this flow, the interior of the first header 22 is divided by the partition wall 224 into an upper space and a lower space on the refrigerant inflow portion 221 side, and the interior of the second header 22 is divided by the partition wall 244 into a lower space and an upper space on the refrigerant outflow portion 242 side.

The three first pipe lines 26A are grouped into one or more (one in the example of the figure) upstream side first pipe lines 26A1 arranged on the upstream side of the second pipe line 26B in the flow of the refrigerant and one or more (two in the example of the figure) downstream side first pipe lines 26A2 arranged on the downstream side of the second pipe line 26B in the flow of the refrigerant.

In the third embodiment, the pipes 26 also have the same shape as each other. Therefore, the sum of the areas of the heat exchange surfaces of the three second pipelines 26B with the battery 10 is larger than the sum of the areas of the heat exchange surfaces of the two downstream side first pipelines 26a2 with the battery 10.

In the third embodiment, at least three (i.e., a larger number than the downstream-side first pipe lines 26a2) second pipe lines 26B are provided adjacent to the two downstream-side first pipe lines 26a2 located on the most downstream side of the refrigerant flow path, and the second pipe lines 26B flow in parallel with the refrigerant having a higher liquid phase content than the refrigerant flowing through the downstream-side first pipe lines 26a 2. Therefore, also in the third embodiment, the same effects as those of the first and second embodiments can be obtained.

Fig. 8 shows a cooling module 20 according to a fourth embodiment. In fig. 8, the same or similar components as those in fig. 1 and 2 are denoted by the same reference numerals, and redundant description is omitted.

The cooling module 20 of the fourth embodiment has a plurality of pipes 26 for exchanging heat with the cells 10 between the first header 22 and the second header 24, as in the first and second embodiments described above. The first header 22 is provided with both the refrigerant inflow portion 221 and the refrigerant outflow portion 222. The cooling module 20 of the fourth embodiment has one or more (four in the illustrated example) first pipe lines 26A for flowing the refrigerant from the first header 22 to the second header 24 and one or more (three in the illustrated example) second pipe lines 26B for flowing the refrigerant from the second header 24 to the first header 22, as in the first and second embodiments.

In the cooling module 20 of the fourth embodiment, unlike the first and second embodiments described above, the refrigerant first flows from the first header 22 to the second header 24, then flows from the second header 24 to the first header 22, then flows again from the first header 22 to the second header 24, and then flows again from the second header 24 to the first header 22. To realize this flow, the interior of the first header 22 is divided by the partition walls 225,226 into an upper space on the refrigerant inflow portion 221 side, a lower space on the refrigerant outflow portion 222 side, and a central space. The interior of the second header 22 is divided into an upper space and a lower space by the partition wall 245.

The four first lines 26A are grouped into one or more (one in the illustrated example) upstream side first lines 26A1 and one or more (three in the illustrated example) downstream side first lines 26A2, and the three second lines 26B are grouped into one or more (one in the illustrated example) upstream side second lines 26B1 and one or more (two in the illustrated example) downstream side second lines 26B 2. In the flow direction of the refrigerant, the tubes 26 are arranged in the order of one upstream-side first tube 26a1, one upstream-side second tube 26B1, three downstream-side first tubes 26a2, and two downstream-side second tubes 26B2 from the upstream side.

In the fourth embodiment, the pipes 26 have the same shape as each other. Therefore, the sum of the areas of the heat exchange surfaces with the battery 10 of the three downstream side first pipelines 26a2 is larger than the sum of the areas of the heat exchange surfaces with the battery 10 of the two downstream side second pipelines 26B 2. Therefore, also in the fourth embodiment, the same effects as those in the first to third embodiments can be obtained.

From another point of view, the first to fourth embodiments described above are considered to have the following common features (1) to (4).

(1) The plurality of tubes 26 constitute at least a first tube group including at least one downstream-most tube (26B; 26A 2; 26B2) located on the downstream-most side in the refrigerant flow direction, and a second tube group including at least one tube (26A; 26B; 26A2) provided in the battery 10 adjacent to the first tube group. The "most downstream side pipe line" is a pipe line constituting a refrigerant flow path closest to the refrigerant outflow portion (222,242) in the refrigerant flow direction among the plurality of pipe lines 26.

(2) The pipe line (26A; 26B; 26A2) belonging to the second pipe line group is provided immediately upstream of the most downstream pipe line (26B; 26A 2; 26B2) belonging to the first pipe line group in the flow direction of the refrigerant.

(3) The refrigerant flows from one of the first header 22 and the second header 24 to the other in the most downstream side tube line (26B; 26A 2; 26B2) belonging to the first tube group, and the refrigerant flows from the other of the first header and the second header to the one in the tube line (26A; 26B; 26A2) belonging to the second tube group. When there are a plurality of pipe lines 26 belonging to one pipe line group, the plurality of pipe lines 26 are arranged in parallel with each other between the first header 22 and the second header 24.

(4) The number of lines (26A; 26B; 26A2) belonging to the second line group is greater than the number of lines (26B; 26A 2; 26B2) belonging to the first line group. That is, the sum of the areas of the heat exchange surfaces with the battery (10) of the tubes (26A; 26B; 26A2) belonging to the second tube group is larger than the sum of the areas of the heat exchange surfaces with the battery (10) of the tubes (26B; 26A 2; 26B2) belonging to the first tube group.

According to the above condition (1), the liquid phase content of the refrigerant flowing through the pipe line (26A; 26B; 26A2) belonging to the second pipe line group is greater than the liquid phase content of the refrigerant flowing through the pipe line (26B; 26A 2; 26B2) belonging to the most downstream pipe line group. Therefore, it is understood that the same effects as those of the first to fourth embodiments can be obtained by satisfying the conditions (1) to (4) described above.

In the above embodiment, the header (22,24,28,30) extends in the vertical direction, and the plurality of pipes (26A,26B,32A,32B) extend in the horizontal direction and are arranged in the vertical direction, but the present invention is not limited thereto. The header (22,24,28,30) may extend in a first horizontal direction, and the plurality of pipes (26A,26B,32A,32B) may extend in a second horizontal direction orthogonal to the first horizontal direction and may be arranged in the first horizontal direction.

Description of the reference numerals

10 batteries (battery modules); 20, a cooling module; 22 a first header; 221 a refrigerant inflow part; 222,242 refrigerant outflow part; 24 a second header; 26 pipelines; 26A first conduit; 26B second line.

Claims

1. A cooling module (20) for cooling a battery (10) for a vehicle,

comprises a first header (22), a second header (24) and a plurality of pipelines (26),

the first header 22 has a refrigerant inflow portion 221 and a refrigerant outflow portion 222,

the refrigerant inflow part (221) is used for allowing the refrigerant which exchanges heat with the battery (10) to flow in,

the refrigerant outflow part (222) flows out the refrigerant which exchanges heat with the battery,

the plurality of tubes (26) being arranged between the first header (22) and the second header (24) for exchanging heat with the cells,

the plurality of pipelines (26) are composed of more than one first pipeline (26A) and more than one second pipeline (26B),

the one or more first tubes (26A) are used for flowing the refrigerant from the first header (22) to the second header (24),

the one or more second tubes (26B) are used for enabling the refrigerant to flow from the second header (24) to the first header (22),

the sum of the areas of the heat exchange surfaces of the one or more first pipelines and the battery (10) is larger than the sum of the areas of the heat exchange surfaces of the one or more second pipelines and the battery (10).

2. The cooling module of claim 1,

three or more lines having the same shape as each other are provided as the plurality of lines (26),

the number of the first lines (26A) is larger than the number of the second lines (26B).

3. The cooling module of claim 1 or 2,

further comprising a third header (28), a fourth header (30), and one or more third tube lines (32A) and one or more fourth tube lines (32B) arranged between the third header and the fourth header,

the refrigerant is configured to flow into the one or more second tubes (26B) after flowing out from the one or more first tubes (26A), sequentially through the second header (24), the third header, the one or more third tubes (32A), the fourth header (30), the one or more fourth tubes, the third header (28), and the second header.

4. A cooling module (20) for cooling a battery (10) for a vehicle,

the cooling module (20) is provided with a first header (22), a second header (24) and a plurality of pipelines (26),

the first header 22 has a refrigerant inflow portion 221 into which a refrigerant for exchanging heat with the battery 10 flows,

the second header pipe (24) has a refrigerant outflow portion (242) from which a refrigerant having exchanged heat with the battery flows out,

the first pipeline (26A) has more than one upstream side first pipeline and more than one downstream side first pipeline,

the one or more upstream-side first pipes are disposed upstream of the second pipe in a flow direction of the refrigerant,

the one or more downstream side first pipelines are arranged at the downstream side of the second pipeline in the flowing direction of the refrigerant,

the sum of the areas of the heat exchange surfaces of the one or more second tubes with the battery (10) is larger than the sum of the areas of the heat exchange surfaces of the one or more downstream side first tubes with the battery (10).

5. A cooling module (20) for cooling a battery (10) for a vehicle,

the first pipeline has more than one upstream side first pipeline and more than one downstream side first pipeline,

the second pipeline has more than one upstream side second pipeline and more than one downstream side second pipeline,

the one or more upstream-side first pipelines, the one or more upstream-side second pipelines, the one or more downstream-side first pipelines, and the one or more downstream-side second pipelines are arranged in this order from the upstream side in the flow direction of the refrigerant,

the sum of the areas of the heat exchange surfaces of the one or more downstream side first tubes with the battery (10) is larger than the sum of the areas of the heat exchange surfaces of the one or more downstream side second tubes with the battery (10).

6. A cooling module (20) for cooling a battery (10) for a vehicle,

the plurality of tubes (26) are disposed between the first header (22) and the second header (24) so as to allow a refrigerant to flow between the first header (22) and the second header (24) and exchange heat with the battery,

either the first header 22 or the second header 24 is provided with a refrigerant outflow portion 222,242 through which a refrigerant having exchanged heat with the battery flows out,

the plurality of pipes (26) forming at least a first pipe group and a second pipe group,

the first pipe line group comprises at least one downstream-most pipe line (26B; 26A 2; 26B2) which is located at the downstream-most side in the flowing direction of the refrigerant,

the second line set comprises at least one line (26A; 26B; 26A2) arranged on the battery (10) adjacent to the first line set,

the at least one pipe (26A; 26B; 26A2) belonging to the second pipe group is arranged on the immediate upstream side of the most downstream side pipe (26B; 26A 2; 26B2) belonging to the first pipe group in the flow direction of the refrigerant,

the refrigerant flows from one of the first header and the second header to the other in the most downstream side pipe (26B; 26A 2; 26B2) belonging to the first pipe group,

and a refrigerant flows from the other of the first header and the second header toward the one of the tubes (26A; 26B; 26A2) belonging to the second tube group,

the sum of the areas of the heat exchange surfaces of the tubes (26A; 26B; 26A2) belonging to the second tube group with the battery (10) is greater than the sum of the areas of the heat exchange surfaces of the tubes (26B; 26A 2; 26B2) belonging to the first tube group with the battery (10).

7. The cooling module of any one of claims 1 to 6,

the plurality of pipes (26) are arranged in the vertical direction.

8. The cooling module of any one of claims 1 to 6,

the plurality of pipes (26) are arranged in a horizontal direction.

9. The cooling module of any one of claims 1 to 8,

the cooling module is provided in a pipe (9) that branches from a pipe of a refrigeration cycle device (1) of an air conditioning device for a vehicle.