Cooling heat exchanger

Abstract

The technical problem solved by this invention is to maintain the uniformity of temperature distribution in a battery. The solution is a cooling heat exchanger (30; 30A; 30B) having an inflow manifold (H1) with an inflow portion (31), an intermediate manifold (H2), an outflow manifold (H4) with an outflow portion (32), an upper pipe (Ta1; Ta2) connecting these manifolds, and a lower pipe (Tb1; Tb2). The interior of the intermediate manifold (H2) is divided by a partition (S2) into an upper space (42a) connecting the upper first pipe (Ta1) and the upper second pipe (Ta2), and a lower space (42b) connecting the lower first pipe (Tb1) and the lower second pipe (Tb2).

Description

Technical Field

[0001] This invention relates to a cooling heat exchanger for cooling high-temperature battery cells mounted in a vehicle. Background Technology

[0002] Electric vehicles and hybrid vehicles are driven by a motor powered by electricity stored in a rechargeable battery. The battery generates heat during charging, which contributes to its degradation. Therefore, battery cooling is necessary to suppress battery degradation. Patent Document 1 discloses a refrigerant-based heat exchanger for cooling batteries.

[0003] Patent Document 1 discloses a cooling heat exchanger comprising multiple flat pipes (refrigerant pipes) disposed between two manifolds (main pipes) and in contact with the battery. The manifolds are configured to extend vertically, and the pipes are thermally bonded to the sides of the battery. That is, the pipes are in contact with the sides of the battery in a manner that allows for heat exchange. During battery cooling, in the refrigerant flow path formed by the manifolds and pipes, the refrigerant flowing through the pipes on the upstream side is in a gas-liquid mixture state containing sufficient liquid, thus providing sufficient cooling capacity for the battery. As the refrigerant flows through the pipes, it is heated by the heat from the battery, thereby reducing the amount of liquid refrigerant by evaporation and increasing the proportion of gaseous refrigerant.

[0004] Patent Document 2 describes a battery module in which multiple batteries are arranged inside a battery pack housing. The batteries are stacked vertically and horizontally to form groups, and multiple groups are arranged inside a single battery pack housing.

[0005] When the cooling heat exchanger of Patent Document 1 is placed inside the battery pack housing of Patent Document 2 to cool each battery pack, it is necessary to focus on the shape of the cooling heat exchanger. That is, in the cooling heat exchanger of Patent Document 1, when there are two manifolds, it is preferable to increase the number of manifolds to three or more, and to arrange pipes between adjacent manifolds. If there are only two manifolds and the longer pipes come into contact with each battery pack, the pipes are prone to deformation due to their length, making it difficult to achieve thermal bonding between the pipes and the sides of the batteries. Therefore, by constructing the cooling heat exchanger with three or more manifolds and placing the middle manifold between the battery packs, it is possible to suppress accidental deformation of the pipes and achieve thermal bonding with the sides of each battery pack.

[0006] Existing technical documents

[0007] Patent documents

[0008] Patent Document 1: Japanese Patent Application Publication No. 2016-035378

[0009] Patent Document 2: Japanese Patent Application Publication No. 2015-072819 Summary of the Invention

[0010] The problem that the invention will solve

[0011] However, with an intermediate manifold, the liquid refrigerant that has entered the manifold from the upper part tends to move towards the lower part due to gravity. Therefore, the gas-liquid mixture of refrigerant flowing through the multiple pipes varies in mixing ratio between the upstream and downstream sides of the intermediate manifold. Downstream of the intermediate manifold, only the gaseous refrigerant tends to concentrate in the upper pipes. That is, the proportion of gaseous refrigerant in the upper pipes tends to be higher. Furthermore, if the proportion of gaseous refrigerant increases, there is a possibility of insufficient cooling capacity of the battery due to liquid refrigerant evaporation, and an inability to maintain uniform temperature distribution within the battery.

[0012] The purpose of this invention is to suppress the increase of the proportion of gaseous refrigerant in the upper pipe of a plurality of pipes arranged in the vertical direction downstream of the intermediate manifold in a cooling module of a battery, thereby maintaining the uniformity of the battery temperature distribution.

[0013] Methods for solving problems

[0014] In the following description, reference numerals in the accompanying drawings are marked with parentheses for ease of understanding of the invention, but this does not limit the invention to the illustrated manner.

[0015] According to one embodiment of the present invention,

[0016] A cooling heat exchanger (30; 30A; 30B) is provided, in which a refrigerant in a gas-liquid mixture flows, for cooling a battery cell (21) for a vehicle. The cooling heat exchanger is characterized by having:

[0017] The inlet section (31) is for the refrigerant to exchange heat with the battery cell (21);

[0018] The inflow manifold (H1) supplies the refrigerant that has passed through the inflow section (31);

[0019] The upper first pipe (Ta1) supplies a portion of the refrigerant that has passed through the inflow manifold (H1);

[0020] The lower first pipe (Tb1), which is positioned below the upper first pipe (Ta1) when the cooling heat exchanger is mounted on the vehicle, allows the remaining portion of the refrigerant that has passed through the inflow manifold (H1) to flow into it.

[0021] The intermediate manifold (H2) is supplied with refrigerant flowing through the upper first pipe (Ta1) and the lower first pipe (Tb1);

[0022] The upper second pipe (Ta2) supplies refrigerant that has passed through the intermediate manifold (H2);

[0023] The lower second pipe (Tb2), which is positioned below the upper second pipe (Ta2) when the cooling heat exchanger is mounted on the vehicle, allows refrigerant to flow in through the intermediate manifold (H2);

[0024] The outlet manifold (H4) allows refrigerant that has passed through the upper second pipe (Ta2) and the lower second pipe (Tb2) to flow in directly or indirectly.

[0025] The outlet (32) is for refrigerant to flow into through the outlet manifold (H4) and for refrigerant to flow out from the cooling heat exchangers (30; 30A; 30B); and

[0026] A partition component (S2) divides the interior of the intermediate manifold (H2) into an upper space (42a) and a lower space (42b). The upper space (42a) is connected to the upper first pipe (Ta1) and the upper second pipe (Ta2), and the lower space (42b) is connected to the lower first pipe (Tb1) and the lower second pipe (Tb2).

[0027] The preferred cooling heat exchangers (30; 30A; 30B) are...

[0028] It has multiple intermediate manifolds (H2; H3), which are connected to each other via upper conduits (Ta2; Ta3) and lower conduits (Tb2; Tb3).

[0029] The cooling heat exchanger has multiple partitions (S2; S3) that divide the interior of the multiple intermediate manifolds (H2; H3) into an upper space (42a; 43a) connected to any one of the upper pipes (Ta2; Ta3) and a lower space (42b; 43b) connected to any one of the lower pipes (Tb2, Tb3). This prevents the refrigerant flowing from the inflow manifold into the upper pipe from being affected by gravity and causing a decrease in the proportion of liquid refrigerant on its path to the outflow manifold.

[0030] The preferred cooling heat exchanger (30A) is...

[0031] The inflow manifold (H1) includes a throttling component (S1) with a throttling orifice (S1a). The area of ​​the throttling orifice (S1a) is smaller than the cross-sectional area of ​​the surface of the inflow manifold (H1) intersecting the length direction.

[0032] The throttling component (S1) divides the interior of the inflow manifold (H1) into an upper space (41a) connected to the upper first pipe (Ta1) and a lower space (41b) connected to the lower first pipe (Tb1), and connects the upper space (41a) and the lower space (41b). This increases the proportion of gas-liquid mixed refrigerant flowing into the inflow manifold into the upper and lower first pipes, and enables a balanced and efficient supply of refrigerant to the upper and lower pipes.

[0033] Invention Effects

[0034] According to the above-described embodiments, in the cooling module of a battery having a central manifold, for the refrigerant flowing in the upper pipe of one of the multiple pipes arranged in the vertical direction downstream of the central manifold, the proportion of gaseous refrigerant can be suppressed from increasing, thereby maintaining the uniformity of the battery temperature distribution. Attached Figure Description

[0035] Figure 1 This is an exploded perspective view showing the cooling heat exchanger, the battery pack equipped with the heat exchanger, and the battery of Embodiment 1.

[0036] Figure 2 This is a schematic cross-sectional view of the cooling heat exchanger of Example 1.

[0037] Figure 3 This describes the refrigerant that creates a gas-liquid mixture. Figure 2 A schematic cross-sectional view of the internal flow of the cooling heat exchanger, which cools the battery.

[0038] Figure 4 This is a schematic cross-sectional view of the cooling heat exchanger of Example 2.

[0039] Figure 5 This is a schematic cross-sectional view illustrating a cooling heat exchanger, a battery pack equipped with the heat exchanger, and a battery according to other embodiments. Detailed Implementation

[0040] The embodiments of the present invention will be described below with reference to the accompanying drawings. In the drawings, Le represents left, Ri represents right, Up represents top, and Dn represents bottom.

[0041] <Example 1>

[0042] Reference Figure 1 . Figure 1The diagram shows three battery stacks 20 for storing electricity, a cooling heat exchanger 30 for cooling these battery stacks 20, and a battery pack housing 10 that houses the battery stacks 20 and the cooling heat exchanger 30. These battery pack housings 10, battery stacks 20, and cooling heat exchangers 30 are, for example, mounted on electric vehicles driven by an electric motor, or hybrid vehicles whose power source consists of an internal combustion engine and an electric motor.

[0043] The battery pack casing 10 is mounted on the vehicle and is made of metal or resin. Figure 1 Although a container with an open top and housing the battery stack 20 and cooling heat exchanger 30 is shown, the interior of the battery pack housing 10 is generally configured as a sealed container to ensure a certain degree of airtightness. By ensuring airtightness, the battery cells 21, which are precision products, can be isolated and protected from dust, water, grease, and other contaminants from the outside.

[0044] Each battery stack 20 has multiple stacked battery cells 211 and a heat spreader 22 disposed on the surface opposite the cooling heat exchanger 30. The stacking direction of the battery cells 21 is not only as follows: Figure 1 As shown, the cells are stacked vertically, but there are also cases stacked horizontally or vertically (not shown). By providing a heat-spreading layer 22, the temperature distribution deviation of each battery cell 21 can be reduced. Materials with high thermal conductivity, such as aluminum alloy or stainless steel alloy, are used in the heat-spreading layer 22. The battery cells 21 have the function of storing electricity supplied to the motor (not shown) used for vehicle operation, and become high-temperature during charging. The heat-spreading layer 22 of the battery stack 20 is thermally bonded to the cooling heat exchanger 30, which conducts heat from the high-temperature battery cells 21 to the cooling heat exchanger 30.

[0045] A cooling heat exchanger 30 is connected to a refrigeration cycle (not shown), and is particularly positioned downstream of the expansion unit. When the refrigeration cycle is operating, a gas-liquid mixture of refrigerant circulates within it as a cooling heat medium. Examples of refrigerants that can be used include Freon-type refrigerants (HFC-134a, R-1234yf, R-12).

[0046] Reference Figure 2The cooling heat exchanger 30 is made of a material with high thermal conductivity, such as aluminum alloy or copper alloy. The cooling heat exchanger 30 has four cylindrical manifolds H (inflow manifold H1, intermediate manifold H2, intermediate manifold H3, and outflow manifold H4) extending vertically; heat exchange pipes T (upper pipes Ta1, Ta2, Ta3; lower pipes Tb1, Tb2, Tb3) supported by these manifolds H and through which refrigerant flows; an inflow section 31 connected to the upper part of the inflow manifold H1 for refrigerant to flow in; and an outflow section 32 connected to the lower part of the outflow manifold H4 for refrigerant to flow out. The interior of the intermediate manifold H2 is divided by a partition S2 into an upper space 42a and a lower space 42b located below the upper space 42a. The interior of the intermediate manifold H3 is divided by a partition S3 into an upper space 43a and a lower space 43b located below the upper space 43a.

[0047] The inflow section 31 has a circumferential flange on the metal tube, which is inserted into the hole formed in the inflow manifold H1. The downstream end of the inflow section 31 opens into the internal space 41 of the inflow manifold H1.

[0048] The outlet section 32 has a circumferential flange on the metal tube and is inserted into the hole formed in the outlet manifold H4. The upstream end of the outlet section 32 is open to the internal space 44 of the outlet manifold H4.

[0049] The heat exchange pipe T is a flat cylindrical body, or it can have multiple walls formed inside along the refrigerant flow direction (see reference). Figure 5 During manufacturing, extrusion molding, bonding of two pipe plates, and rolling of a single pipe plate are used. The upper first pipe Ta1 connects the internal space 41 of the inflow manifold H1 to the upper space 42a of the intermediate manifold H2. The lower first pipe Tb1 connects the internal space 41 of the inflow manifold H1 to the lower space 42b of the intermediate manifold H2. The upper second pipe Ta2 connects the upper space 42a of the intermediate manifold H2 to the upper space 43a of the intermediate manifold H3. The lower second pipe Tb2 connects the lower space 42b of the intermediate manifold H2 to the lower space 43b of the intermediate manifold H3. The upper third pipe Ta3 connects the upper space 43a of the intermediate manifold H3 to the internal space 44 of the outflow manifold H4. The lower third pipe Tb3 connects the lower space 43b of the intermediate manifold H3 to the internal space 44 of the outflow manifold H4.

[0050] The four manifolds H1, H2, H3, and H4 include an inflow manifold H1 with an inflow section 31; an intermediate manifold H2 located downstream of the inflow manifold H1 and connected to the upper first pipeline Ta1 and the lower first pipeline Tb1; an intermediate manifold H3 located downstream of the intermediate manifold H2 and connected to the upper second pipeline Ta2 and the lower second pipeline Tb2; and an outflow manifold H4 located downstream of the intermediate manifold H3 and connected to the upper third pipeline Ta3 and the lower third pipeline Tb3. Figures 1 to 3 In this designation, the four manifolds H1, H2, H3, and H4 are indicated to have the same length, but the invention is not limited to this. For example, when the heights of the multiple battery stacks 20 differ, the lengths of each manifold H1, H2, H3, and H4 can be appropriately varied accordingly. Furthermore, the vertical positions of the upper pipe Ta and the lower pipe Tb can be appropriately varied based on the above considerations. This avoids localized cooling of the battery stack 20 and cooling at offset locations, thus maintaining the battery stack 20 at a uniform temperature.

[0051] The cooling heat exchanger 30 is preferably integrally joined by brazing four manifolds H, eight heat exchange pipes T, inlet section 31, outlet section 32, and partition components S2 and S3. This ensures high rigidity.

[0052] Reference Figure 1 as well as Figure 3 The arrows in the diagram indicate the direction and flow rate of the refrigerant, and the black dots represent liquid refrigerant.

[0053] The gas-liquid mixture of refrigerant flowing in the inlet section 31 and into the inlet manifold H1 is generally separated vertically within the internal space 41 of the inlet manifold H1. A portion flows into the upper first pipe Ta1, and the remainder flows into the lower first pipe Tb1. The refrigerant flowing through the upper first pipe Ta1 and the lower first pipe Tb1 exchanges heat with the battery unit 21 via the heat exchange layer 21. The refrigerant flowing out of the upper first pipe Ta1 flows into the upper space 42a of the intermediate manifold H2. The refrigerant flowing out of the lower first pipe Tb1 flows into the lower space 42b of the intermediate manifold H2.

[0054] The gas-liquid mixed refrigerant flowing into the upper space 42a of the intermediate manifold H2 flows into the upper second pipe Ta2. The gas-liquid mixed refrigerant flowing into the lower space 42b of the intermediate manifold H2 flows into the lower second pipe Tb2. The refrigerant flowing through the upper second pipe Ta2 and the lower second pipe Tb2 exchanges heat with the battery unit 21 via the heat exchange layer 21. The refrigerant flowing out of the upper second pipe Ta2 flows into the upper space 43a of the intermediate manifold H3. The refrigerant flowing out of the lower second pipe Tb2 flows into the lower space 43b of the intermediate manifold H3.

[0055] The gas-liquid mixture of refrigerant flowing into the upper space 43a of the intermediate manifold H3 flows into the upper third pipe Ta3. The gas-liquid mixture of refrigerant flowing into the lower space 43b of the intermediate manifold H3 flows into the lower third pipe Tb3. The refrigerant flowing through the upper third pipe Ta3 and the lower third pipe Tb3 exchanges heat with the battery cell 21 via the heat exchange layer 21. The refrigerant flowing out of the upper third pipe Ta3 flows into the internal space 44 of the outlet manifold H4. The refrigerant flowing out of the lower third pipe Tb3 flows into the internal space 44 of the outlet manifold H4.

[0056] The refrigerant flowing into and out of the manifold H4 from the upper third pipe Ta3 and the refrigerant flowing into and out of the manifold from the lower third pipe Tb3 merge in the internal space 44 of the manifold H4 and then flow into the refrigeration cycle (not shown) via the outflow section 32.

[0057] The proportion of liquid refrigerant in the gas-liquid mixture flowing into manifold H1 is relatively high. Liquid refrigerant has a greater density than gaseous refrigerant. Therefore, as... Figure 3 As shown, the larger the mass of the liquid refrigerant, the more likely it is to be affected by gravity and move downwards.

[0058] The refrigerant flowing into the intermediate manifold H2 has a lower proportion of liquid refrigerant compared to the refrigerant flowing into the manifold H1. This is because the refrigerant absorbs heat from the battery cell 21 as it flows through the upper first pipe Ta1 and the lower first pipe Tb1, causing a portion of the liquid refrigerant to evaporate and become gaseous refrigerant. However, the refrigerant flowing into the intermediate manifold H2 remains in a gas-liquid mixture state, meaning it has a certain degree of humidity. Therefore, as... Figure 3 As shown, in the intermediate manifold H2, there is also a tendency for the liquid refrigerant with a larger mass to move downwards more easily due to the influence of gravity.

[0059] The proportion of liquid refrigerant in the gas-liquid mixture flowing into the intermediate manifold H3 is further reduced compared to the refrigerant flowing in the intermediate manifold H2. This is because, as the refrigerant flows through the upper second pipe Ta2 and the lower second pipe Tb2, it absorbs heat from the battery cell 21, causing a portion of the liquid refrigerant to evaporate and change into gaseous refrigerant. However, the refrigerant flowing into the intermediate manifold H3 is still in a gas-liquid mixture state, that is, it has a certain degree of humidity. Therefore, as... Figure 3 As shown, in the intermediate manifold H3, there is also a tendency for the liquid refrigerant with a larger mass to move downwards more easily due to the influence of gravity.

[0060] The proportion of liquid refrigerant in the gas-liquid mixture flowing into and out of manifold H4 is further reduced compared to the refrigerant flowing in the intermediate manifold H3. This is because, as the refrigerant flows through the upper third pipe Ta3 and the lower third pipe Tb3, it absorbs heat from battery cell 21, causing a portion of the liquid refrigerant to evaporate and transform into gaseous refrigerant. The refrigerant flowing into and out of manifold H4 is as follows: Figure 3 As shown, it contains almost no liquid refrigerant, or is entirely in a gaseous state (not illustrated). That is, the humidity is approximately zero.

[0061] Here, a partition S2 is installed inside the intermediate manifold H2, completely separating the upper space 42a and the lower space 42b. Therefore, for the refrigerant flowing above the partition S2 in the gas-liquid mixture flowing into the intermediate manifold H2, even if the liquid phase refrigerant moves downwards inside the intermediate manifold H2 due to gravity, it will not move downwards compared to the partition S2. Thus, for the upper second pipe Ta2, connected to the upper part of the intermediate manifold H2 and supplying refrigerant from the intermediate manifold H2, the proportion of liquid phase refrigerant flowing through it can be ensured to a certain extent. That is, the proportion of gas phase refrigerant can be suppressed from becoming too high.

[0062] Similarly, a partition S3 is also provided inside the intermediate manifold H3, completely separating the upper space 43a and the lower space 43b. Furthermore, for the refrigerant flowing above the partition S3 in the gas-liquid mixture entering the intermediate manifold H3, even if the liquid refrigerant moves downwards inside the intermediate manifold H3 due to gravity, it will not move downwards compared to the partition S3. Therefore, for the upper third pipe Ta3 connected to the upper part of the intermediate manifold H3 and supplying refrigerant from the intermediate manifold H3, the proportion of liquid refrigerant flowing through it can be ensured to a certain extent. That is, the proportion of gaseous refrigerant can be suppressed from becoming too high.

[0063] Furthermore, it can suppress the reduction in cooling capacity of battery cells 21 in the upper pipe (upper second pipe Ta2) among the multiple pipes connected to the downstream side of the intermediate manifold H2 and the upper pipe (upper third pipe Ta3) among the multiple pipes connected to the downstream side of the intermediate manifold H3, and can maintain the uniformity of temperature distribution of the battery stack 20.

[0064] <Example 2>

[0065] Next, the cooling heat exchanger 30A of Embodiment 2 will be described with reference to the accompanying drawings.

[0066] Reference Figure 4The cooling heat exchanger 30A of Embodiment 2 is disposed inside the battery pack housing 10A. For the parts that are common to the cooling heat exchanger 30 of Embodiment 1, the reference numerals are used as in the drawings, and detailed descriptions are omitted.

[0067] The cooling heat exchanger 30A cools the battery stack 20. The difference between the cooling heat exchanger 30 and the one in Embodiment 1 is that the throttling member S1 is located at the point where the inflow manifold H1 is located.

[0068] The cooling heat exchanger 30A preferably integrates four manifolds H, eight heat exchange pipes T, inlet section 31, outlet section 32, partition components S2 and S3, and throttling component S1 by brazing. This ensures high rigidity.

[0069] The interior of the inflow manifold H1 is divided into an upper space 41a and a lower space 41b by a throttling component S1. The throttling component S1 has a throttling orifice S1a. The area of ​​the throttling orifice S1a is smaller than the cross-sectional area of ​​the interior space along a direction orthogonal to the length of the inflow manifold H1. Although the interior of the inflow manifold H1 is divided into the upper space 41a and the lower space 41b by the throttling orifice S1a, they are interconnected.

[0070] The upper first pipe Ta1 connects the upper space 41a of the inflow into manifold H1 to the upper space 42a of the middle manifold H2. The lower first pipe Tb1 connects the lower space 41b of the inflow into manifold H1 to the lower space 42b of the middle manifold H2.

[0071] The inflow section 31 has a circumferential flange on the metal tube, which is inserted into the hole formed in the inflow manifold H1. The downstream end of the inflow section 31 opens into the upper space 41a of the inflow manifold H1.

[0072] For the heat exchanger 30A used for cooling, the flow of the refrigerant is explained.

[0073] The inlet section 31 is installed above the throttling component S1 in the inlet manifold H1. The gas-liquid mixed refrigerant flowing through the inlet section 31 flows into the upper space 41a of the inlet manifold H1. The relatively denser liquid refrigerant moves downwards into the upper space 41a due to gravity and gathers near the throttling component S1. A portion of the refrigerant reaching the throttling component S1 moves into the lower space 41b through the throttling orifice S1a. The refrigerant that does not pass through the throttling orifice S1a flows into the upper first pipe Ta1.

[0074] The refrigerant flowing into the upper space 41a flows out through either the upper first pipe Ta1 or the throttling orifice S1a. Due to the throttling component S1, the flow resistance of the paths through the upper pipes Ta1, Ta2, and Ta3 (the flow resistance of the upper pipes) is relatively reduced compared to the flow resistance of the paths through the lower pipes Tb1, Tb2, and Tb3 (the flow resistance of the lower pipes). Therefore, the proportion of refrigerant flowing through the upper pipes Ta1, Ta2, and Ta3 can be increased. Furthermore, by adjusting the area of ​​the throttling orifice S1a, the proportion of refrigerant flowing through the upper pipes Ta1, Ta2, and Ta3 can be increased to a desired level, allowing for a balanced and efficient supply of refrigerant to the upper pipes Ta1, Ta2, and Ta3 and the lower pipes Tb1, Tb2, and Tb3. Moreover, it is possible to achieve uniform temperature distribution in the cooling heat exchanger 30A.

[0075] <Other Embodiments>

[0076] The cooling heat exchangers 30 and 30A have been described above through Embodiments 1 and 2. However, as long as the functions and effects of the present invention are achieved, the present invention is not limited to Embodiments 1 and 2. For example, although the number of intermediate manifolds is described as two, there can be one or more intermediate manifolds. When there is one intermediate manifold, the refrigerant flows directly into the outlet manifold (H4) through the upper second pipe Ta2 and the lower second pipe Tb2. When there are two or more intermediate manifolds, the refrigerant flows indirectly into the outlet manifold (H4) through the upper second pipe Ta2 and the lower second pipe Tb2.

[0077] Furthermore, when the cooling heat exchanger has two or more intermediate manifolds, it is preferable to equip all intermediate manifolds with a separator, but the cooling heat exchanger of the present invention also includes other configurations. In this case, in a cooling heat exchanger having two intermediate manifolds, it is preferable to equip the most upstream intermediate manifold H2 with a separator S2. The refrigerant flowing into the most upstream intermediate manifold H2 has a higher proportion of liquid refrigerant than the refrigerant flowing into the downstream intermediate manifold H3, and the liquid refrigerant tends to move downwards due to gravity. Here, by providing a separator S2 in the most upstream intermediate manifold H2, the decrease in the proportion of liquid refrigerant flowing into the upper second pipe Ta2 can be effectively suppressed.

[0078] Alternatively, the throttling orifice S1a provided in the throttling component S1 may have multiple orifices. Regarding the shape of the throttling orifice S1a, a circular or elliptical shape may also be appropriately selected.

[0079] Furthermore, the orientation of the cooling heat exchangers 30, 30A, and 30B is not limited to the vertical installation of the manifold H. The upper pipe Ta can also be positioned higher than the lower pipe Tb, and the entire cooling heat exchanger 30B can be arranged at an angle towards the battery stack 20. (See reference...) Figure 5 The cooling heat exchanger 30B is erected with the extension axis HX of the manifold H at an angle θ relative to the bottom surface 10a of the battery pack housing 10. The upper pipe Ta is in contact with the lower pipe Tb and the heat spreader 22 of the battery stack 20. In this case, considering the shape of the battery stack 20 and the effects of the present invention, it is preferable to assemble the battery stack with an angle θ in the range of 70 to 110 degrees.

[0080] Industrial availability

[0081] The battery cooling device of the present invention is suitable for use in electric vehicles and hybrid vehicles.

[0082] Explanation of reference numerals in the attached figures

[0083] 10… Battery pack casing

[0084] 10a…bottom

[0085] 20… Battery stack

[0086] 21… battery cells

[0087] 22…Easy-of-heat layer

[0088] 30, 30A, 30B... Cooling heat exchangers

[0089] 31…Inflow Section

[0090] 32…outflow part

[0091] 41… Interior Space

[0092] 41a… Upper space

[0093] 42b…lower side space

[0094] 42a… Upper space

[0095] 42b…lower side space

[0096] 43a… Upper space

[0097] 43b…lower side space

[0098] 44… Interior Space

[0099] H…management pipe

[0100] H1…flow into manifold

[0101] H2…Intermediate manifold

[0102] H3…Intermediate manifold

[0103] H4…outflow header

[0104] T…heat exchange piping

[0105] Ta1…First pipe on the upper side

[0106] Ta2…Second pipe on the upper side

[0107] Ta3… Third pipe on the upper side

[0108] Tb1…First pipe on the lower side

[0109] Tb2…Second pipe on the lower side

[0110] Tb3…Third pipe on the lower side

[0111] S1…Throttling component

[0112] S1a…Throttle orifice

[0113] S2…Separation component

[0114] S3…Separation component

[0115] θ…the angle of the extension axis of the manifold relative to the bottom surface

Claims

1. A heat exchanger (30; 30A; 30B) for cooling, wherein a refrigerant in a gas-liquid mixture flows inside, for cooling a battery cell (21) for a vehicle, characterized in that, The cooling heat exchanger has the following features: The inlet section (31) is for the refrigerant to exchange heat with the battery cell (21); The inflow manifold (H1) supplies the refrigerant that has passed through the inflow section (31); The upper first pipe (Ta1) is used to supply a portion of the refrigerant that has passed through the inflow manifold (H1); The lower first pipe (Tb1), which is positioned below the upper first pipe (Ta1) when the cooling heat exchanger is mounted on the vehicle, allows the remaining portion of the refrigerant that has passed through the inflow manifold (H1) to flow in. The intermediate manifold (H2) is supplied with refrigerant flowing through the upper first pipe (Ta1) and the lower first pipe (Tb1); The upper second pipe (Ta2) supplies refrigerant that has passed through the intermediate manifold (H2); The lower second pipe (Tb2), which is positioned below the upper second pipe (Ta2) when the cooling heat exchanger is mounted on the vehicle, allows refrigerant to flow in through the intermediate manifold (H2); The outlet manifold (H4) allows refrigerant that has passed through the upper second pipe (Ta2) and the lower second pipe (Tb2) to flow in directly or indirectly. The outlet (32) is for refrigerant to flow into through the outlet manifold (H4) and for refrigerant to flow out from the cooling heat exchangers (30; 30A; 30B); and A partition component (S2) divides the interior of the intermediate manifold (H2) into an upper space (42a) and a lower space (42b). The upper space (42a) is connected to the upper first pipe (Ta1) and the upper second pipe (Ta2), and the lower space (42b) is connected to the lower first pipe (Tb1) and the lower second pipe (Tb2). The upper first pipe (Ta1), the lower first pipe (Tb1), the intermediate manifold (H2), the upper second pipe (Ta2), and the lower second pipe (Tb2) are integrally joined by brazing.

2. The cooling heat exchanger (30; 30A; 30B) according to claim 1, characterized in that, The cooling heat exchanger has the following features: Multiple intermediate manifolds (H2; H3) are connected to each other via upper conduits (Ta2; Ta3) and lower conduits (Tb2; Tb3). Multiple partition components (S2; S3) divide the interior of the multiple intermediate manifolds (H2; H3) into an upper space (42a; 43a) connected to any one of the upper pipes (Ta2; Ta3) and a lower space (42b; 43b) connected to any one of the lower pipes (Tb2, Tb3).

3. The cooling heat exchanger (30A; 30B) according to claim 1 or 2, characterized in that, The inflow manifold (H1) includes a throttling component (S1) with a throttling orifice (S1a). The area of ​​the throttling orifice (S1a) is smaller than the cross-sectional area of ​​the surface of the inflow manifold (H1) intersecting the length direction. The throttling component (S1) divides the interior of the inflow manifold (H1) into an upper space (41a) connected to the upper first pipe (Ta1) and a lower space (41b) connected to the lower first pipe (Tb1), and connects the upper space (41a) and the lower space (41b).

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