Battery heat exchanger, battery pack and vehicle

Abstract

The application discloses a battery heat exchanger, a battery pack and a vehicle. The battery heat exchanger comprises a current collecting structure, the current collecting structure comprises a first flow channel, a second flow channel and a third flow channel, the cross-sectional area of the first flow channel is greater than the cross-sectional area of the second flow channel, and the cross-sectional area of the first flow channel is greater than the cross-sectional area of the third flow channel; wherein the first flow channel is in communication with a first interface of the battery heat exchanger, and the second flow channel and the third flow channel are in communication with a second interface of the battery heat exchanger. The application can improve the heat exchange performance of the battery heat exchanger.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of vehicles, and particularly relates to a battery heat exchanger, a battery pack and a vehicle. BACKGROUND

[0002] In the prior art, a battery heat exchanger is used to exchange heat for the batteries in a battery pack.

[0003] In the prior art, a harmonica tube is used as a battery heat exchanger, and the heat exchange medium changes between gas and liquid in the heat exchange. Each flow channel of the harmonica tube is a straight tube, which causes a large temperature difference between the temperature close to the inlet and the temperature far from the inlet, and further causes uneven battery heat exchange. Therefore, it is necessary to optimize the flow channel of the battery heat exchanger. When the flow channel has a flow splitting or flow converging function, the heat exchange medium will be split or converged in the heat exchanger. However, how to design the flow splitting and converging structure, optimize the flow resistance of the heat exchange medium in different flow channels, and make the battery heat exchanger exchange heat as evenly as possible to reduce the temperature difference of each part of the battery, is a problem that needs to be solved. SUMMARY

[0004] The purpose of the embodiments of the present application is to provide a battery heat exchanger with good heat exchange performance.

[0005] According to a first aspect of the embodiments of the present application, a battery heat exchanger is provided, which comprises a flow splitting and converging structure, the flow splitting and converging structure comprising a first flow channel, a second flow channel and a third flow channel;

[0006] The cross-sectional area of the first flow channel is greater than the cross-sectional area of the second flow channel, and the cross-sectional area of the first flow channel is greater than the cross-sectional area of the third flow channel.

[0007] The first flow channel is in communication with a first interface of the battery heat exchanger, and the second flow channel and the third flow channel are in communication with a second interface of the battery heat exchanger.

[0008] Optionally, h1 / b∈[1 / 3, 10], wherein h1 is the maximum depth of the first flow channel or the second flow channel or the third flow channel, and b is the thickness of the flow channel plate of the battery heat exchanger.

[0009] Optionally, h1 / s2∈[1 / 20, 1], wherein h1 is the maximum depth of the first flow channel or the second flow channel or the third flow channel, and s2 is the maximum width of the first flow channel or the second flow channel or the third flow channel.

[0010] Optionally, h1 / r2∈[1 / 7, 5 / 2], wherein h1 is the maximum depth of the first flow channel or the second flow channel or the third flow channel, and r2 is the radius of the second chamfer close to the base plate of the first flow channel or the second flow channel or the third flow channel.

[0011] Alternatively, h1 / b∈[1 / 3, 10], h1 / s2∈[1 / 20, 1], h1 / r2∈[1 / 7, 5 / 2], wherein h1 is the maximum depth of the first flow channel or the second flow channel or the third flow channel, b is the thickness of the flow channel plate of the battery heat exchanger, s2 is the maximum width of the first flow channel or the second flow channel or the third flow channel, and r2 is the radius of the second chamfer of the first flow channel or the second flow channel or the third flow channel close to the base plate of the battery heat exchanger.

[0012] Alternatively, h1 / b∈[1 / 3, 5 / 1], h1 / s2∈[1 / 15, 1 / 3], h1 / r2∈[1 / 7, 2 / 5], wherein h1 is the maximum depth of the first flow channel or the second flow channel or the third flow channel, b is the thickness of the flow channel plate of the battery heat exchanger, s2 is the maximum width of the first flow channel or the second flow channel or the third flow channel, and r2 is the radius of the second chamfer of the first flow channel or the second flow channel or the third flow channel close to the base plate of the battery heat exchanger.

[0013] Alternatively, a / s2≥0.05, wherein a is the thickness of the base plate of the battery heat exchanger, and s2 is the maximum width of the first flow channel or the second flow channel or the third flow channel.

[0014] Alternatively, s3 / s4∈[5 / 20, 4], wherein s3 is the maximum width of the outer surface of the second flow channel, and s4 is the maximum width of the outer surface of the third flow channel.

[0015] Alternatively, s3 / s4∈[1 / 3, 3 / 1], wherein s3 is the maximum width of the outer surface of the second flow channel, and s4 is the maximum width of the outer surface of the third flow channel.

[0016] Alternatively, s5≤15mm, s6≤45mm, wherein s5 is the maximum width of the outer surface of the first flow channel, and s6 is the minimum distance between any flow channel and the peripheral structure.

[0017] Alternatively, when the flow distribution and collection structure is used for flow distribution, the fluid of the first flow channel is distributed to the second flow channel and the third flow channel.

[0018] When the flow distribution and collection structure is used for flow collection, the fluid of the second flow channel and the third flow channel is collected into the first flow channel.

[0019] Alternatively, the cross-sectional area of the second flow channel is equal to the cross-sectional area of the third flow channel.

[0020] Optionally, r1≤r2, wherein r1 is a radius of a first chamfer of the first flow channel or the second flow channel or the third flow channel away from a substrate of the battery heat exchanger, and r2 is a radius of a second chamfer of the first flow channel or the second flow channel or the third flow channel close to the substrate of the battery heat exchanger.

[0021] Optionally, r1≤h1, wherein h1 is a maximum depth of the first flow channel or the second flow channel or the third flow channel.

[0022] Optionally, a=b, wherein a is a thickness of a substrate of the battery heat exchanger, and b is a thickness of a flow channel plate of the battery heat exchanger.

[0023] Optionally, h1>(a+b), wherein h1 is a maximum depth of the first flow channel or the second flow channel or the third flow channel, a is a thickness of a substrate of the battery heat exchanger, and b is a thickness of a flow channel plate of the battery heat exchanger.

[0024] Optionally, h1=0.5*h2, wherein h1 is a maximum depth of the first flow channel or the second flow channel or the third flow channel, and h2 is a total thickness of the battery heat exchanger.

[0025] Optionally, the split bus structure further comprises a fourth flow channel, the fourth flow channel being in communication with the first flow channel, and a flange protruding towards the split bus structure between the first flow channel and the fourth flow channel.

[0026] According to a second aspect of embodiments of the present application, a battery pack is provided, comprising:

[0027] a plurality of battery cells;

[0028] a first battery heat exchanger and a second battery heat exchanger, the first battery heat exchanger and the second battery heat exchanger being the battery heat exchanger according to any one of the preceding embodiments;

[0029] a substrate of the first battery heat exchanger is in contact with a first surface of the battery cells, and a substrate of the second battery heat exchanger is in contact with a second surface of the battery cells.

[0030] According to a third aspect of embodiments of the present application, a vehicle is provided, the vehicle being installed with the battery heat exchanger according to any one of the preceding embodiments, or the battery pack according to the preceding embodiment.

[0031] The technical effect of the embodiment of the present application is that, in the position of the flow-dividing and flow-collecting structure, the cross-sectional area of the first flow channel is greater than the cross-sectional area of the second flow channel, and the cross-sectional area of the first flow channel is greater than the cross-sectional area of the third flow channel, in other words, when the flow-dividing and flow-collecting structure divides the flow, the cross-sectional area of the first flow channel into which the refrigerant flows is greater than the cross-sectional area of any one of the flow channels from which the refrigerant flows out, which makes the pressure of any one of the flow channels not decrease sharply after the refrigerant in the first flow channel is divided to the second flow channel and the third flow channel, thereby ensuring that the refrigerant can be smoothly divided to the second flow channel and the third flow channel at the flow-dividing and flow-collecting structure, and any one of the second flow channel and the third flow channel cannot divide too much due to the sharp decrease in pressure, so that the heat exchange performance of the entire battery heat exchanger is improved. On the contrary, when the flow-dividing and flow-collecting structure collects the flow, the cross-sectional area of the first flow channel into which the refrigerant flows is greater than the cross-sectional area of any one of the flow channels into which the refrigerant flows, which makes the pressure of the first flow channel not increase sharply after the refrigerant in the second flow channel and the third flow channel is collected to the first flow channel, thereby ensuring that the refrigerant can be smoothly collected to the first flow channel at the flow-dividing and flow-collecting structure, and any one of the second flow channel and the third flow channel cannot cause too high flow resistance due to the sharp increase in pressure, which causes uneven collection, so that the heat exchange performance of the entire battery heat exchanger is improved.

[0032] Other features of the present application and its advantages will become apparent from the following detailed description of exemplary embodiments of the present application with reference to the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0033] The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate embodiments of the present application and, together with the description, serve to explain the principles of the present application.

[0034] Figure 1 It is an exploded view of the battery heat exchanger of the embodiment of the present application;

[0035] Figure 2 It is a top view of the battery heat exchanger of the embodiment of the present application;

[0036] Figure 3 It is a partial enlarged view along section A in Figure 2

[0037] Figure 4 It is a sectional view along line C-C in Figure 3

[0038] Figure 5 It is a sectional view along line D-D in Figure 3

[0039] Figure 6 It is a sectional view along line E-E in Figure 2 ​​​A magnified view of part B in the image;

[0040] Figure 7 This is a perspective view of the battery pack according to an embodiment of this application.

[0041] Explanation of reference numerals in the attached drawings: 1. Stud; 2. Flow channel plate; 201. Second flow channel; 202. Third flow channel; 203. First chamfer; 204. Diverter / combiner structure; 205. Second chamfer; 206. Flange; 207. First flow channel; 208. Fourth flow channel; 209. Flow channel; 210. Dummy flow channel; 3. Substrate; 4. Inlet / outlet assembly; 100. First battery heat exchanger; 200. Second battery heat exchanger; 300. Battery cell. Detailed Implementation

[0042] Various exemplary embodiments of the present application will now be described in detail with reference to the accompanying drawings. It should be noted that, unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the present application.

[0043] The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the scope of this application and its application or use.

[0044] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0045] In all the examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values.

[0046] It should be noted that similar labels and letters in the following figures indicate similar items; therefore, once an item is defined in one figure, it does not need to be discussed further in subsequent figures.

[0047] like Figures 1 to 6 As shown, the battery heat exchanger in this embodiment includes a flow channel plate 2 and a substrate 3. More specifically, flow channel grooves are formed on the flow channel plate 2 by, for example, a stamping process, and the substrate 3 is welded to the flow channel plate 2, such that the flow channel grooves are formed as shown in the figure. Figure 6 The multiple flow channels 209 shown.

[0048] The lower end of the stud 1 is provided with a boss with a height equal to the thickness b of the flow channel plate 2 for brazing positioning. The bottom of the boss is brazed to the substrate 3 as one piece, which can be used to fix heat dissipation components such as the bottom sealing plate of the battery.

[0049] The inlet / outlet assembly 4 is used for the refrigerant fluid to enter and exit the battery heat exchanger.

[0050] The flow channel plate 2 can be formed by molding or blowing, having the advantages of fast forming and light weight.

[0051] The flow channel plate 2 is punched at the welding position of the stud 1, and the hole diameter is the same as the boss diameter of the stud 1, which is used for welding positioning of the stud 1.

[0052] The base plate 3 is used for direct or indirect contact with the battery cell to exchange heat, and can ensure sufficient flatness. The connection between the base plate 3 and the inlet and outlet assembly 4 needs to be punched for welding positioning of the inlet and outlet assembly 4. The flow channel plate 2 and the base plate 3 can be formed by welding to form the internal flow channel of the refrigerant fluid. The inlet and outlet assembly 4 can be formed by welding with the base plate 3 through the brazing process.

[0053] As shown in Figure 2 For the battery heat exchanger, the flow channel distribution area is the heating area of the battery cell that needs to be cooled, and the number N of flow channel distribution strips of the battery heat exchanger can be calculated according to the width L of the heating area and the flow channel density p. As shown in Figure 3 Where s1 is the minimum distance between adjacent flow channels, and s2 will be described below. The values of various parameters in the battery heat exchanger meet the cooling requirements, as well as the pressure resistance requirements and welding quality requirements of the battery heat exchanger.

[0054] As shown in Figure 3 The battery heat exchanger includes a flow distribution structure 204, which includes a first flow channel 207, a second flow channel 201, and a third flow channel 202. The first flow channel 207 is in communication with the first interface of the battery heat exchanger, and the second flow channel 201 and the third flow channel 202 are in communication with the second interface of the battery heat exchanger. More specifically, when the flow distribution structure 204 is used for flow distribution, the fluid of the first flow channel 207 is distributed to the second flow channel 201 and the third flow channel 202, at which time the first flow channel 207 is directly or indirectly in communication with the first interface, which is the fluid inlet, and the second flow channel 201 and the third flow channel 202 are directly or indirectly in communication with the second interface of the battery heat exchanger, which is the fluid outlet; when the flow distribution structure 204 is used for flow distribution, the fluid of the second flow channel 201 and the third flow channel 202 flows into the first flow channel 207, at which time the first flow channel 207 is directly or indirectly in communication with the first interface, which is the fluid outlet, and the second flow channel 201 and the third flow channel 202 are directly or indirectly in communication with the second interface of the battery heat exchanger, which is the fluid inlet. In other words, the first interface and the second interface refer to different concepts according to the role of the flow distribution structure 204. In fact, as shown in Figure 2 ​As shown, in the refrigerant fluid flow path of the entire battery heat exchanger, part of the flow branching and merging structure 204 is used for flow branching, and part of the flow branching and merging structure 204 is used for flow merging.

[0055] like Figure 4 As shown in the diagram, only the cross-sections of the second flow channel 201 and the third flow channel 202 are displayed, with the cross-sectional area of ​​the second flow channel 201 labeled A2 and the cross-sectional area of ​​the third flow channel labeled A3. Figure 5 As shown, the cross-section of the first flow channel 207 can have a similar shape to that of the second flow channels 201 and 203, only with different dimensions. The cross-sectional area of ​​the first flow channel 207 is denoted as A1. The cross-sectional area A1 of the first flow channel 207 is larger than the cross-sectional area A2 of the second flow channel 201, and the cross-sectional area A1 of the first flow channel 207 is larger than the cross-sectional area A3 of the third flow channel 202; in other words, the cross-sectional area A1 of the first flow channel 207 is the largest among the three flow channels of the flow distribution structure 204. In this document, A1, A2, and A3 all refer to the area enclosed by the inner surfaces of the first flow channel 207, the second flow channel 201, and the third flow channel 2, which is also the cross-sectional area allowing fluid to pass through, excluding the cross-sectional area of ​​the substrate 3 and the flow channel plate 2. When the refrigerant flows through the manifold 204, the cross-sectional area of ​​the refrigerant flowing into the first channel 207 is larger than the cross-sectional area of ​​any refrigerant flowing out. This ensures that regardless of whether the refrigerant flowing into the first channel 207 is gaseous, liquid, or in a gas-liquid coexistence state, after being diverted to the second channel 201 and the third channel 202 by the manifold 204, no sudden drop in pressure will occur in any of the channels. This ensures that the refrigerant can be smoothly diverted to the second channel 201 and the third channel 202 at the manifold 204, preventing excessive diversion in either the second channel 201 or the third channel 202 due to a sudden drop in pressure. Therefore, the heat exchange performance of the entire battery heat exchanger is improved. Conversely, when the refrigerant flows into the first channel 207 through the manifold, the cross-sectional area of ​​the refrigerant flowing into the first channel 207 is larger than the cross-sectional area of ​​any other refrigerant inflow channel. This ensures that regardless of whether the refrigerant flowing into the second channel 201 or the third channel 202 is gaseous, liquid, or in a gas-liquid coexistence state, after flowing into the first channel 207 through the manifold structure 204, the first channel 207 will not experience a sharp increase in pressure. This ensures that the refrigerant can be smoothly flowed into the first channel 207 at the manifold structure 204, preventing either the second channel 201 or the third channel 202 from experiencing excessive flow resistance due to a sharp increase in pressure, thus preventing uneven flow. As a result, the heat exchange performance of the entire battery heat exchanger is improved.

[0056] like Figure 3As shown, the figure shows the shape of each flow channel observed from the outside. In the case where the cross-sectional area of the first flow channel 207, the second flow channel 201 and the third flow channel 202 satisfies the above condition, the maximum width s5 of the outer surface of the first flow channel 207, the maximum width s3 of the outer surface of the second flow channel 201, and the maximum width s4 of the outer surface of the third flow channel 202 can adopt the same or different values as shown in Table 1. s3, s4 and s5 include the thickness of the flow channel plate 2 constituting the flow channel.

[0057] As mentioned before, the shape of the cross section of the first flow channel 207, the second flow channel 201 and the third flow channel 202 can be similar, so for the sake of brevity, the maximum width of the first flow channel 207, the maximum width of the second flow channel 201 and the maximum width of the third flow channel 202 are collectively referred to as the maximum width s2 in the following. Figure 4 s2 can be the maximum width of the inner surface of the first flow channel 207, the maximum width of the inner surface of the second flow channel 201, the maximum width of the inner surface of the third flow channel 202, or the maximum width of the outer surface of the first flow channel 207, the maximum width of the outer surface of the second flow channel 201, the maximum width of the outer surface of the third flow channel 202. s2 of the first flow channel 207, the second flow channel 201 and the third flow channel 202 can also be the same or different in specific values.

[0058] As shown in Figure 4 h1 is the maximum depth of the first flow channel 207 or the second flow channel 201 or the third flow channel 202, a is the thickness of the substrate 3 of the battery heat exchanger, b is the thickness of the flow channel plate 2 of the battery heat exchanger, h2 is the total thickness of the battery heat exchanger (excluding the height of the stud 1 and the inlet and outlet assembly 4), r1 is the radius of the first chamfer 203 of the first flow channel 207 or the second flow channel 201 or the third flow channel 202 away from the substrate 3 of the battery heat exchanger, r2 is the radius of the second chamfer 205 of the first flow channel 207 or the second flow channel 201 or the third flow channel 202 close to the substrate 3 of the battery heat exchanger, s1 is the minimum distance between the second flow channel 201 and the third flow channel 202, and s2 is the maximum width of the first flow channel 207 or the second flow channel 201 or the third flow channel 202. For the sake of brevity, Figure 4 these parameters are partially concentrated in the second flow channel 201 or the second flow channel 202. The inventors have found that these parameters interact with each other and ultimately affect the pressure resistance performance, welding reliability and the like of the entire battery heat exchanger.

[0059] Since each flow channel is formed by machining the flow channel plate 2, the greater h1 is, the greater the thinning rate of the flow channel plate 2 is, and the lower the pressure resistance is, but at the same time, a greater s1 can be left under the condition that the cross-sectional area is unchanged, so that a greater welding width is obtained to improve the welding reliability, and therefore an optimal balance between the pressure resistance and the welding reliability needs to be achieved. The inventor finds that h1 / b ∈ [1 / 3, 10], that is, when the value of h1 / b is within the range of 1 / 3 (inclusive) to 10 (inclusive), a good balance between the pressure resistance and the welding reliability can be achieved.

[0060] Under the condition that the cross-sectional area of the flow channel is unchanged, the shape of the cross section is related to h1 and s2, and the shape of the cross section will affect the flow resistance of the flow channel, and the value of s2 will also affect the value of s1, and then affect the welding reliability, and h1 will affect the thinning rate and then affect the pressure resistance. The inventor finds that h1 / s2 ∈ [1 / 20, 1], that is, when the value of h1 / s2 is within the range of 1 / 20 (inclusive) to 1 (inclusive), a good balance between the flow resistance of the flow channel and the welding reliability can be achieved.

[0061] Similarly, under the condition that the cross-sectional area of the flow channel is unchanged, the shape of the cross section is also related to h1 and r2, and the shape of the cross section will affect the flow resistance of the flow channel, and the value of h1 will also affect the thinning rate and then affect the pressure resistance. The inventor finds that h1 / r2 ∈ [1 / 7, 5 / 2], that is, when the value of h1 / r2 is within the range of 1 / 7 (inclusive) to 5 / 2 (inclusive), a good balance between the flow resistance of the flow channel and the pressure resistance can be achieved.

[0062] The inventor further finds that h1 / b ∈ [1 / 3, 10], h1 / s2 ∈ [1 / 20, 1], and h1 / r2 ∈ [1 / 7, 5 / 2], and when the three conditions are met at the same time, the flow resistance of the flow channel, the pressure resistance performance, and the welding reliability of the battery heat exchanger can all achieve a good balance.

[0063] The inventor finds that h1 / b ∈ [1 / 3, 5 / 1], h1 / s2 ∈ [1 / 15, 1 / 3], and h1 / r2 ∈ [1 / 7, 2 / 5], and when the three conditions are met, the flow resistance of the flow channel, the pressure resistance performance, and the welding reliability of the battery heat exchanger reach an optimal state. The above numerical combination can reduce the thinning rate of the battery heat exchanger while ensuring the pressure resistance value of the battery heat exchanger, so that the battery heat exchanger can meet the demand for refrigerant pressure required by battery heat exchange, and the mass of the battery heat exchanger is reduced.

[0064] The thickness a of the substrate 3 cannot be too thin, otherwise the pressure resistance of the battery heat exchanger will be affected, and it also cannot be too thick, otherwise it will cause material waste, and the pressure resistance is also related to s2. The inventors found that when a / s2≥0.05, the pressure resistance performance brought by the thickness of the substrate 3 will be significantly improved. Of course, a / s2 cannot be infinitely large, and the maximum should not exceed 0.6, otherwise it will cause material waste. When a / s2≥0.05, the flow channel plate 2 is convenient for stamping forming, and at the same time the battery heat exchanger can meet the demand of the refrigerant pressure required by the battery heat exchange.

[0065] As shown in Figure 3 , the ratio of the maximum width of the second flow channel 201 and the third flow channel 202 will affect the distribution and collection effect, and if the ratio between the two is too small or too large, it will cause one flow channel to have too much fluid and the other flow channel to have too little fluid due to uneven flow resistance, which will damage the uniformity of the entire battery heat exchanger. The inventors found that when s3 / s4∈[5 / 20,4], that is, the maximum width ratio of the two flow channels is between 5 / 20 (inclusive) and 4 (inclusive), the uniformity of the battery heat exchanger can be guaranteed.

[0066] More preferably, s3 / s4∈[1 / 3,3 / 1], so that the flow resistance of the refrigerant in the two flow channels is closer.

[0067] As shown in Figure 3 and Figure 6 , s5 is the maximum width of the outer surface of the first flow channel, and s6 is the minimum distance between any flow channel and the surrounding structure. The surrounding structure can be an adjacent flow channel, or for example Figure 6 the stud 1 or the dummy flow channel 210. s6 directly affects the welding quality and the pressure resistance of the battery heat exchanger. If s6 is too small, the pressure in the flow channel is easy to cause the welding to fail, so that the second flow channel 201 and the third flow channel 202 are in communication, and cracking occurs between the flow channel and the surrounding structure, losing the refrigerant distribution function. If s6 is too large, it is easy to cause welding quality defects, such as inability to exhaust, etc., thereby affecting the overall performance of the battery heat exchanger. In this embodiment, 3mm≤s6≤45mm is designed, so as to balance the pressure resistance and the welding quality. The size of s5 not only affects the cross-sectional shape of the flow channel, but also affects the welding quality and the pressure resistance, so it is preferred that 5mm≤s5≤15mm, at which time the welding quality and the pressure resistance can be balanced. s3 / s4∈[1 / 3,3 / 1], 5mm≤s5≤15mm, 3mm≤s6≤45mm, this parameter combination can meet the welding performance of the battery heat exchanger, and ensure that no welding bubbles are left, and under the premise of meeting the processing feasibility of the battery heat exchanger, the pressure resistance of the battery heat exchanger meets the demand.

[0068] As shown in Figure 4As shown, radii r1 and r2 affect the thinning rate of the flow channel plate 2, and also affect the specific shape of the flow channel cross section. r1≤r2 means that the flow channel is smoother near the substrate 3 and sharper away from the substrate 3, which can avoid pressure concentration at the joint between the substrate 3 and the flow channel plate 2, causing welding failure.

[0069] Both r1 and h1 affect the thinning rate of the flow channel plate 2 at the flow channel. However, if r1 is too large, the bottom surface of the flow channel will form a sharp corner in order to achieve a suitable stamping depth h1. This will cause pressure concentration at the sharp corner and make the battery heat exchanger prone to cracking due to scratches during actual use. Therefore, it is preferable that r1≤h1, which ensures that the thinning rate meets the pressure resistance requirements while making the bottom surface of the flow channel away from the base plate 3 more gentle and preventing the formation of sharp corners.

[0070] Alternatively, the cross-sectional area of ​​the second flow channel 201 is equal to the cross-sectional area of ​​the third flow channel 202. The advantage of this structure is that the difference in cross-sectional area between the second flow channel 201 and the third flow channel 202 will not cause uneven distribution of the refrigerant, thus enabling the battery heat exchanger to achieve good temperature uniformity.

[0071] like Figure 4 As shown, taking the third flow channel 202 as an example, the third flow channel 202 has a first chamfer 203 away from the substrate 3 and a second chamfer 205 close to the substrate 3. The radius r1 of the first chamfer 203 is smaller than the radius r2 of the second chamfer 205. The shapes of other flow channels can be the same as the third flow channel 202, so they will not be described in detail. During the stamping process of forming the flow channel, if r1 is the same as or even exceeds r2, it will result in the inability to stamp the flow channel in the process. Therefore, r1 ≤ r2. The radii r1 and r2 affect the thinning rate of the flow channel plate 2. The smaller r1 and r2 are, the greater the thinning rate and the lower the pressure resistance of the battery heat exchanger. Therefore, it is preferable that r1 is smaller than the flow channel depth h1 to avoid insufficient pressure resistance, and at the same time, the flow channel can be stamped by the stamping process.

[0072] Alternatively, the thickness 'a' of the flow channel plate 2 is equal to the thickness 'b' of the substrate 3. Therefore, choosing a = b achieves a balance between pressure resistance and heat dissipation, ensuring that the substrate 3 or the flow channel plate 2 does not have excessively high pressure resistance relative to the other.

[0073] Alternatively, the maximum depth h1 of the flow channel is greater than the sum of the thickness b of the substrate 3 and the thickness a of the flow channel plate 2, i.e., h1>(a+b), so that the width s1 between the second flow channel 201 and the third flow channel 202 can be increased as much as possible under the same cross-sectional area of the flow channel, thereby avoiding the penetration of the second flow channel 201 and the third flow channel 202 due to insufficient pressure resistance of the battery heat exchanger. When h1 / (a+b)∈[3 / 2.8,2], the thinning rate and the pressure resistance are satisfied at the same time. Correspondingly, s1∈[4,15], and the welding quality requirement can also be met.

[0074] Alternatively, the depth h1 of the flow channel is equal to half of the total thickness h2 of the battery heat exchanger. As shown in Figure 4 the total thickness of the battery heat exchanger is the distance between the upper surface of the substrate 3 and the lower surface of the second flow channel 201 or the third flow channel 202. The advantage of this structure is that although the flow channel plate 2 is thinned by stamping at the flow channel, the limitation of the depth still ensures that the battery heat exchanger can obtain good pressure resistance, and at the same time, the value of s1 can meet the requirements.

[0075] As shown in Figure 3 the figure shows two sub-converging structures 204, wherein the right sub-converging structure 204 further includes a fourth flow channel 208, which communicates with the first flow channel 207. The fourth flow channel 208 communicates with the first flow channel 207 in the left sub-converging structure 204, thereby making the two sub-converging structures 204 parallel. The first flow channel 207 and the fourth flow channel 208 have a flange 206 protruding towards the sub-converging structure 204, which has the effect of making part of the refrigerant in the first flow channel 207 flow into the sub-converging structure 204, and part of the refrigerant flow into the next sub-converging structure 204 through the fourth flow channel 208, and also improving the welding quality. When the sub-converging structure 204 is used as a converging structure, the flange 206 can ensure smooth convergence, and the principle is just the opposite of the sub-converging structure.

[0076] As shown in Table 1, if only one factor is considered, taking an exemplary battery heat exchanger design as an example, the value range and beneficial effects of the parameters as shown in Figures 1 to 6 the table are shown in the columns of the table.

[0077] Table 1

[0078]

[0079] However, in the embodiments of the present application, because multiple factors such as heat dissipation performance, pressure resistance and welding quality are considered, various restrictions as described above are added, and therefore the finally selected parameters are:

[0080] s1 = 8 mm; s2 = 13 mm; h1 = 3 mm; a = 1.4 mm; b = 1.4 mm; h2 = 6 mm; r1 = 2.8 mm;

[0081] r2 = 4 mm; p = 7 mm; s3 = 11 mm; s4 = 11 mm; s5 = 12 mm; s6 = 10 mm. In other words, embodiments of the present application can achieve optimal performance of the battery heat exchanger.

[0082] As shown in FIG. 1, according to a first aspect of embodiments of the present application, a battery heat exchanger is provided, comprising: Figure 7

[0083] a cell 300;

[0084] a first battery heat exchanger 100 and a second battery heat exchanger 200, the first battery heat exchanger 100 and the second battery heat exchanger 200 being the battery heat exchanger as in any one of the preceding aspects;

[0085] the substrate 3 of the first battery heat exchanger 100 is in contact with a first surface of the cell 300, and the substrate 3 of the second battery heat exchanger 200 is in contact with a second surface of the cell 300. In Figure 7 specific embodiments, the first surface and the second surface are respectively an upper surface and a lower surface. Compared with a harmonica cold plate, a large-area stamped battery heat exchanger reduces the uniform temperature plate between the harmonica tube and the cell 300, and the substrate 3 plays the role of the uniform temperature plate. One side of the substrate 3 is in direct contact with the refrigerant, and the other side is in contact with the cell 300 through the heat-conducting structural adhesive. The heat generated by the cell 300 is directly transferred to the refrigerant through the substrate 3 to take out the battery pack, greatly improving the heat transfer efficiency of the battery heat exchanger, and significantly improving the heat dissipation effect of the battery pack. The battery heat exchanger itself can also serve as the cover plate of the battery pack, making the structure simpler and the cost lower.

[0086] According to a third aspect of embodiments of the present application, a vehicle is provided, the vehicle being installed with the battery heat exchanger as in any one of the preceding aspects, or the vehicle being installed with the battery pack as previously described.

[0087] Although some specific embodiments of the present application have been described in detail by examples, those skilled in the art should understand that the above examples are only for illustration, but not for limiting the scope of the present application. Those skilled in the art should understand that the above embodiments can be modified without departing from the scope and spirit of the present application. The scope of the present application is defined by the appended claims.​

Claims

1. A battery heat exchanger, characterized by, The battery heat exchanger comprises a branch and bus structure (204), the branch and bus structure (204) comprises a first flow channel (207), a second flow channel (201) and a third flow channel (202); The cross-sectional area (A1) of the first flow channel (207) is greater than the cross-sectional area (A2) of the second flow channel (201), and the cross-sectional area (A1) of the first flow channel (207) is greater than the cross-sectional area (A3) of the third flow channel (202); The first flow channel (207) is in communication with the first interface of the battery heat exchanger, and the second flow channel (201) and the third flow channel (202) are in communication with the second interface of the battery heat exchanger. h1 / b∈[1 / 3, 10], wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), and b is the thickness of the flow channel plate (2) of the battery heat exchanger.

2. The battery heat exchanger of claim 1, wherein, h1 / s2∈[1 / 20, 1], wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), and s2 is the maximum width of the first flow channel (207) or the second flow channel (201) or the third flow channel (202).

3. The battery heat exchanger of claim 1, wherein, h1 / r2∈[1 / 7, 5 / 2], wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), and r2 is the radius of the second chamfer of the first flow channel (207) or the second flow channel (201) or the third flow channel (202) close to the base plate (3) of the battery heat exchanger.

4. The battery heat exchanger according to any one of claims 1 to 3, characterized in that, h1 / b∈[1 / 3, 10], h1 / s2∈[1 / 20, 1], h1 / r2∈[1 / 7, 5 / 2], wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), b is the thickness of the flow channel plate (2) of the battery heat exchanger, s2 is the maximum width of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), and r2 is the radius of the second chamfer of the first flow channel (207) or the second flow channel (201) or the third flow channel (202) close to the base plate (3) of the battery heat exchanger.

5. The battery heat exchanger according to any one of claims 1 to 3, characterized in that, h1 / b∈[1 / 3, 5 / 1], h1 / s2∈[1 / 15, 1 / 3], h1 / r2∈[1 / 7, 2 / 5], wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), b is the thickness of the flow channel plate (2) of the battery heat exchanger, s2 is the maximum width of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), and r2 is the radius of the second chamfer of the first flow channel (207) or the second flow channel (201) or the third flow channel (202) close to the base plate (3) of the battery heat exchanger.

6. The battery heat exchanger of any one of claims 1 to 3, wherein, a / s2≥0.05, wherein a is the thickness of the substrate (3) of the battery heat exchanger, and s2 is the maximum width of the first flow channel (207) or the second flow channel (201) or the third flow channel (202).

7. The battery heat exchanger of claim 6, wherein, s3 / s4∈[5 / 20,4], wherein s3 is the maximum width of the outer surface of the second flow channel (201), and s4 is the maximum width of the outer surface of the third flow channel (202).

8. The battery heat exchanger of claim 6, wherein, s3 / s4∈[1 / 3,3 / 1], wherein s3 is the maximum width of the outer surface of the second flow channel (201), and s4 is the maximum width of the outer surface of the third flow channel (202).

9. The battery heat exchanger according to claim 7 or 8, characterized in that s5≤15mm, s6≤45mm, wherein s5 is the maximum width of the outer surface of the first flow channel (207), and s6 is the minimum distance between any flow channel and the peripheral structure.

10. The battery heat exchanger of claim 1, wherein, When the distribution and collection structure (204) is used for distribution, the fluid of the first flow channel (207) is distributed to the second flow channel (201) and the third flow channel (202); When the distribution and collection structure (204) is used for collection, the fluid of the second flow channel (201) and the third flow channel (202) is collected into the first flow channel (207).

11. The battery heat exchanger of claim 1, wherein, The cross-sectional area of the second flow channel (201) is equal to the cross-sectional area of the third flow channel (202).

12. The battery heat exchanger of claim 1, wherein, r1≤r2, wherein r1 is the radius of the first chamfer of the first flow channel (207) or the second flow channel (201) or the third flow channel (202) away from the substrate (3) of the battery heat exchanger, and r2 is the radius of the second chamfer of the first flow channel (207) or the second flow channel (201) or the third flow channel (202) close to the substrate (3) of the battery heat exchanger.

13. The battery heat exchanger of claim 12, wherein, r1≤h1, wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202).

14. The battery heat exchanger of claim 1, wherein, a=b, wherein a is the thickness of the substrate (3) of the battery heat exchanger, and b is the thickness of the flow channel plate (2) of the battery heat exchanger.

15. The battery heat exchanger of claim 1, wherein, h1>(a+b), wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), a is the thickness of the substrate (3) of the battery heat exchanger, and b is the thickness of the flow channel plate (2) of the battery heat exchanger.

16. The battery heat exchanger of claim 1, wherein, h1=0.5*h2, wherein h1 is the maximum depth of the first flow channel (207) or the second flow channel (201) or the third flow channel (202), and h2 is the total thickness of the battery heat exchanger.

17. The battery heat exchanger of claim 1, wherein, The distribution and collection structure (204) further comprises a fourth flow channel (208), the fourth flow channel (208) is in communication with the first flow channel (207), and the first flow channel (207) and the fourth flow channel (208) have a flange (206) protruding towards the distribution and collection structure (204).

18. A battery pack, characterized by Comprise: Battery cell (300); A first battery heat exchanger (100) and a second battery heat exchanger (200), the first battery heat exchanger (100) and the second battery heat exchanger (200) being the battery heat exchanger according to any one of claims 1 to 17; The substrate (3) of the first battery heat exchanger (100) is in contact with the first surface of the battery cell (300), and the substrate (3) of the second battery heat exchanger (200) is in contact with the second surface of the battery cell (300).

19. A vehicle characterized by comprising: The vehicle is provided with the battery heat exchanger according to any one of claims 1 to 17, or the battery pack according to claim 18.

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