Heat exchange device and electric device
By designing a transition channel in the heat exchanger to separate gas and liquid, the problems of complex flow and blockage caused by improper liquid inlet setting are solved, resulting in better heat exchange effect and fluid distribution, and improved heat exchange efficiency.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- CALB GROUP CO LTD
- Filing Date
- 2025-07-29
- Publication Date
- 2026-07-21
AI Technical Summary
In existing heat exchangers, the liquid inlet is located at one end of the liquid inlet plate along the width of the flow channel, which leads to complex mixing and flow of gas and liquid, causing blockage and affecting the heat exchange effect.
Design a heat exchange device comprising an inlet plate, a flow channel plate, and a transition channel. The cross-sectional area of the transition channel is smaller than that of the collection chamber. Gas is separated from the liquid and transported to the second collection chamber through the transition channel, thereby controlling the flow resistance and optimizing the fluid distribution.
It improves the heat exchange effect of the heat exchange device, ensures uniform fluid distribution and gas separation, reduces flow resistance, and improves the overall heat exchange efficiency.
Smart Images
Figure CN224537128U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of battery technology, and more specifically, to a heat exchange device and an electrical device. Background Technology
[0002] In electric vehicles and energy storage systems, efficient heat dissipation of the battery pack is crucial for ensuring battery performance and extending its lifespan. Heat exchangers are typically used to transfer heat from the battery pack. As the energy density of battery packs continues to increase, their structures are becoming more compact. This necessitates that heat exchangers not only achieve efficient heat exchange within a limited space but also consider compatibility and layout rationality with other external components of the battery pack.
[0003] The heat exchanger includes an inlet plate and a flow channel plate communicating with the inlet plate. The flow channel plate contains a flow channel, and the inlet plate has an inlet communicating with the flow channel. Due to structural limitations of the battery pack, or to avoid interference from other components adjacent to the battery pack, the inlet is located at one end of the inlet plate along the width of the flow channel in related technologies. This results in an asymmetrical arrangement of the inlets along the width of the flow channel. Based on this asymmetrical arrangement of the inlets, when the liquid contains gas, the gas and liquid mix and flow. Due to the differences in physical properties between the gas and liquid, the flow resistance of the mixed fluid is more complex than that of a pure liquid, which may cause blockage in the flow channel, leading to a localized reduction in flow velocity and affecting the heat exchange effect.
[0004] Therefore, in related technologies, the liquid inlet is set at one end of the liquid inlet plate along the width of the flow channel, resulting in poor heat exchange effect of the heat exchange device. Utility Model Content
[0005] The main objective of this invention is to provide a heat exchange device and an electrical device to solve the problem in related technologies where the liquid inlet is located at one end of the liquid inlet plate along the width of the flow channel, resulting in poor heat exchange performance of the heat exchange device.
[0006] To achieve the above objectives, according to one aspect of the present invention, a heat exchange device is provided. The heat exchange device includes an inlet plate and a flow channel plate communicating with the inlet plate. A cavity communicating with the flow channel plate is provided within the inlet plate, and an inlet port communicating with the cavity is provided on the inlet plate. The cavity includes a first collecting cavity, a second collecting cavity, and a transition channel. The inlet port is directly connected to the first collecting cavity, which has a first opening communicating with the flow channel plate. The flow area of the first opening is greater than half of the flow area of the cavity communicating with the flow channel plate. The second collecting cavity is connected to the first collecting cavity and has a second opening communicating with the flow channel plate. The transition channel connects the first collecting cavity and the second collecting cavity. Along the thickness direction of the inlet plate, the cross-sectional area of the transition channel is smaller than the cross-sectional area of the first collecting cavity, and the cross-sectional area of the transition channel is smaller than the cross-sectional area of the second collecting cavity.
[0007] According to another aspect of the present invention, an electrical device is provided, including a heat exchange device, wherein the heat exchange device is the heat exchange device described above.
[0008] By applying the above technical solution, since the cross-sectional area of the transition channel is smaller than that of both the first and second collecting chambers, the flow of fluid from the first to the second collecting chamber is effectively controlled. The smaller cross-sectional area of the transition channel allows pressure fluctuations to form as the fluid passes through it, which helps to separate the gas in the first collecting chamber from the fluid and transport it to the second collecting chamber. At least a portion of the gas contained in the fluid in the first collecting chamber is transported to the second collecting chamber through the transition channel, resulting in a lower gas content in the fluid in the first collecting chamber. This reduces the complexity of fluid flow resistance and allows for more uniform heat exchange in the portion of the flow channel plate connected to the first opening. Furthermore, since the flow area of the first opening of the first collecting chamber is greater than half the flow area connecting the chamber to the flow channel plate, the gas content in most of the flow channel plate is lower, allowing for more uniform heat exchange in most of the flow channel plate, thereby improving the heat exchange effect of the heat exchange device. Because the cross-sectional area of the second manifold is larger than that of the transition channel, the fluid velocity decreases as it enters the second manifold through the transition channel due to the expansion of space. This facilitates the remixing and uniform distribution of gas and fluid, allowing for more uniform heat exchange within the flow channel plate connected to the second opening, thereby improving the heat exchange efficiency of the heat exchange device. Thus, even when the inlet is located at one end of the inlet plate, the heat exchange device can still achieve good heat exchange performance. Therefore, the technical solution of this application effectively solves the problem in related technologies where placing the inlet at one end of the inlet plate along the width of the flow channel results in poor heat exchange performance. Attached Figure Description
[0009] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:
[0010] Figure 1 A front view schematic diagram of an embodiment of the heat exchange device according to the present invention is shown;
[0011] Figure 2 It shows Figure 1 A cross-sectional schematic diagram of the heat exchange device;
[0012] Figure 3 It shows Figure 2 A partial cross-sectional view of the liquid inlet plate of the heat exchanger;
[0013] Figure 4 It shows Figure 1 A cross-sectional schematic diagram of the liquid inlet plate of the heat exchanger.
[0014] The above figures include the following reference numerals:
[0015] 10. Liquid inlet plate; 11. Liquid inlet; 12. First collection chamber; 121. First opening; 122. First inclined surface; 123. Second inclined surface; 124. Connecting line; 13. Second collection chamber; 131. Second opening; 14. Transition channel; 141. Third opening;
[0016] 20. Flow channel plate; 21. Flow channel;
[0017] 30. Preset plane;
[0018] 40. Liquid outlet plate. Detailed Implementation
[0019] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.
[0020] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.
[0021] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values of the components and steps described in these embodiments do not limit the scope of this invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all 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. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.
[0022] like Figures 1 to 4 As shown, in some embodiments of this application, a heat exchange device is provided, which includes an inlet plate 10 and a flow channel plate 20 communicating with the inlet plate 10. The inlet plate 10 is provided with a cavity communicating with the flow channel plate 20, and the inlet plate 10 is provided with an inlet port 11 communicating with the cavity. The cavity includes a first collecting cavity 12, a second collecting cavity 13, and a transition channel 14. The inlet 11 is directly connected to the first collecting cavity 12, which has a first opening 121 that communicates with the flow channel plate 20. The flow area of the first opening 121 is greater than half of the flow area of the cavity communicating with the flow channel plate 20. The second collecting cavity 13 is connected to the first collecting cavity 12, which has a second opening 131 that communicates with the flow channel plate 20. The transition channel 14 is connected between the first collecting cavity 12 and the second collecting cavity 13. Along the thickness direction of the inlet plate 10, the cross-sectional area of the transition channel 14 is smaller than the cross-sectional area of the first collecting cavity 12, and the cross-sectional area of the transition channel 14 is smaller than the cross-sectional area of the second collecting cavity 13.
[0023] By applying the above technical solution, since the cross-sectional area of the transition channel 14 is smaller than that of the first collecting cavity 12 and smaller than that of the second collecting cavity 13, the flow of fluid from the first collecting cavity 12 to the second collecting cavity 13 is effectively controlled. The smaller cross-sectional area of the transition channel 14 allows pressure fluctuations to form when the fluid passes through it, which helps to separate the gas in the first collecting cavity 12 from the fluid and transport it to the second collecting cavity 13. At least part of the gas contained in the fluid in the first collecting cavity 12 is transported to the second collecting cavity 13 by the transition channel 14, resulting in a lower gas content in the fluid in the first collecting cavity 12. This reduces the complexity of fluid flow resistance and allows for more uniform heat exchange in the portion of the flow channel plate 20 connected to the first opening 121. Furthermore, since the flow area of the first opening 121 of the first collecting cavity 12 is greater than half the flow area connecting the cavity to the flow channel plate 20, the gas content of the fluid in most of the flow channel plate 20 is relatively low, allowing for more uniform heat exchange in most of the flow channel plate 20, thereby improving the heat exchange effect of the heat exchange device. Since the cross-sectional area of the second collecting cavity 13 is larger than the cross-sectional area of the transition channel 14, when the fluid enters the second collecting cavity 13 through the transition channel 14, the expansion of space reduces the fluid velocity, which helps to remix the gas and fluid and achieve uniform distribution. This allows for more uniform heat exchange in the portion of the flow channel plate 20 connected to the second opening 131, thereby improving the heat exchange effect of the heat exchange device. Thus, even when the liquid inlet 11 is located at one end of the liquid inlet plate 10, the heat exchange device can still have a good heat exchange effect. Therefore, the above technical solution effectively solves the problem in related technologies where placing the liquid inlet at one end of the liquid inlet plate along the width direction of the flow channel results in poor heat exchange performance.
[0024] It should be noted that the transition channel 14 helps to separate the gas in the first collecting chamber 12 from the fluid and transport it to the second collecting chamber 13 because: the cross-sectional area of the transition channel 14 is smaller than that of the first collecting chamber 12 and smaller than that of the second collecting chamber 13. This means that the fluid undergoes a change in flow direction and velocity when passing through the transition channel 14. Gas has a lower viscosity than liquid, resulting in less flow resistance for the gas in the narrower transition channel 14, making it easier for the gas to change its flow direction and enter the transition channel 14. Gas has a lower density than liquid, making it easier for the gas to change its flow direction and thus easier to be pushed into the transition channel 14. Gas is more compressible than liquid; when the gas-liquid mixture passes through the transition channel 14, the narrow design of the transition channel 14 allows the more compressible gas to enter the transition channel 14 preferentially, enabling gas separation from the liquid. Furthermore, the change in flow velocity caused by the setting of the transition channel 14 will create a pressure gradient between the first collection chamber 12 and the second collection chamber 13. Since gas is more sensitive to pressure changes than liquid, gas will move more easily through the transition channel 14 to the second collection chamber 13 with lower pressure.
[0025] It should be noted that "direct connection between inlet 11 and first manifold 12" means that the fluid entering from inlet 11 directly enters the first manifold 12, and does not flow through other cavities before entering the first manifold 12. The fluid refers to a mixture of liquid and gas. The flow area connecting the cavity and the flow channel plate 20 refers to the total flow area when the cavity and flow channel plate 20 are connected.
[0026] The inventors discovered that in related technologies, when gas is freely dispersed throughout the entire flow channel plate, its low thermal conductivity causes it to randomly form localized areas of poor heat transfer efficiency. By applying the aforementioned technical solution, confining the gas to a small portion of the flow channel plate 20, the thermal conductivity and heat transfer efficiency of the liquid in the remaining majority of the flow channel plate 20 can be significantly increased, thus improving the heat transfer effect in most areas of the flow channel plate 20. Furthermore, in related technologies, when gas is freely dispersed throughout the entire flow channel plate, its presence disrupts the laminar flow state, generating localized turbulence and resulting in uneven fluid distribution, affecting the uniformity of heat transfer. However, by applying the aforementioned technical solution, confining the gas to a small portion of the flow channel plate 20, the fluid in most of the flow channel plate 20 corresponding to the first opening 121 can maintain a laminar flow state, contributing to the uniform distribution of heat energy. In this way, the heat transfer performance of most areas of the flow channel plate 20 is improved, and even if a small portion of the flow channel plate 20 may have lower heat transfer efficiency, the negative impact on the overall heat transfer effect of the flow channel plate 20 is significantly reduced. By directing gas to a small portion of the flow channel plate 20, the heat exchanger can maximize the utilization of the liquid's high thermal conductivity, reduce the thermal resistance and flow resistance caused by the gas, and avoid uneven heat distribution, ultimately achieving a significant improvement in heat exchange efficiency. Compared to the gas being freely dispersed throughout the entire flow channel plate 20, this technical solution ensures that the heat exchange efficiency of most of the flow channel plate 20 is at its optimal state, improving the heat exchange effect of the heat exchanger and providing a more efficient and reliable thermal management solution.
[0027] like Figures 2 to 4 As shown, the transition channel 14 has a third opening 141 communicating with the flow channel plate 20. The relationship between the flow areas S1 of the first opening 121, S2 of the second opening 131, and S3 of the third opening 141 satisfies: 0.5 < S1 / (S1+S2+S3) ≤ 0.8. By controlling the relationship between the flow areas S1 of the first opening 121, S2 of the second opening 131, and S3 of the third opening 141, the proportion of fluid with a lower gas content entering the flow channel plate 20 is adjusted, optimizing the distribution of fluid with a lower gas content within the flow channel plate 20, thereby improving the heat exchange effect of the heat exchange device. Furthermore, the above arrangement also facilitates the entry of gas into the transition channel 14 and the second manifold 13 by adjusting the proportion of fluid with a higher gas content entering the flow channel plate 20, thus enabling gas to easily enter the transition channel 14 and the second manifold 13 for gas-liquid separation.
[0028] Preferably, S1 / (S1+S2+S3) is 0.51, 0.55, 0.6, 0.65, 0.67, 0.7, 0.75 or 0.8.
[0029] like Figures 2 to 4As shown, the cavity wall of the first collecting cavity 12 includes a first inclined surface 122, which is disposed opposite to the first opening 121. The first inclined surface 122 is connected to the side wall of the transition channel 14, and the first inclined surface 122 gradually approaches the first opening 121 in the direction close to the transition channel 14. The design of the first inclined surface 122 helps to separate the liquid and the gas. When the gas in the liquid encounters the first inclined surface 122 in the first collecting cavity 12, the gas is more easily guided by the first inclined surface 122 and moves along the inclined direction of the first inclined surface 122 to enter the transition channel 14 due to its characteristic of easily changing the direction of movement. This allows the gas to be effectively separated from the liquid and guided to the second collecting cavity 13, further reducing the gas content of the fluid flowing from the first opening 121 to the flow channel plate 20 and improving the heat exchange effect of the heat exchange device.
[0030] like Figure 3 and Figure 4 As shown, the cavity wall of the first collecting cavity 12 also includes a second inclined surface 123. The first end of the second inclined surface 123 is connected to the end of the first inclined surface 122 away from the transition channel 14, and the second end of the second inclined surface 123 is connected to the first opening 121. The second inclined surface 123 and the first opening 121 are arranged opposite to each other, and the second inclined surface 123 gradually approaches the first opening 121 in the direction away from the transition channel 14. With the above arrangement, the second inclined surface 123 can guide the fluid in the first collecting cavity 12, so that the gas in the first collecting cavity 12 can move better and more fully to the first inclined surface 122, so that the gas in the first collecting cavity 12 can enter the transition channel 14 more fully and be transported to the second collecting cavity 13.
[0031] In some embodiments, the liquid inlet 11 is provided at the joint between the first inclined surface 122 and the second inclined surface 123.
[0032] Understandably, in other embodiments, the second inclined surface 123 may also be configured at right angles to facilitate the containment of liquid within the first collection cavity 12.
[0033] like Figure 3 and Figure 4As shown, a pre-defined plane 30 extends along the thickness direction of the inlet plate 10 and bisects the first opening 121. The first inclined surface 122 and the second inclined surface 123 connect to form a connecting line 124, which is located on the side of the pre-defined plane 30 away from the transition channel 14. This design optimizes the flow path of the fluid within the first collection chamber 12, allowing more gas within the fluid to be gradually guided to the transition channel 14 as it flows towards the first opening 121, while the liquid is effectively guided into the flow channel plate 20. This arrangement helps achieve effective separation and directional transport of gas within the fluid, reducing the amount of gas entering the first opening 121, thereby reducing the negative impact of gas on the heat exchange efficiency of the flow channel plate 20 and enhancing the heat exchange effect of the heat exchange device.
[0034] like Figure 3 and Figure 4 As shown, the inlet 11 is located on the side of the preset plane 30 away from the transition channel 14. This ensures that both the inlet 11 and the connecting line 124 are located on the side of the preset plane 30 away from the transition channel 14, increasing the probability that the fluid flowing out of the inlet 11 will come into contact with the first inclined surface 122. This allows the fluid in the first collecting cavity 12 to be better guided by the first inclined surface 122 into the transition channel 14, thereby further reducing the gas content entering the flow channel plate 20 from the first opening 121 and improving the heat exchange effect of the heat exchange device.
[0035] like Figure 3 and Figure 4 As shown, the included angle A between the first inclined plane 122 and the second inclined plane 123 satisfies: 130°≤A≤150°. By setting the included angle A between the first inclined plane 122 and the second inclined plane 123, the heat exchange device can improve the compactness of the liquid inlet plate 10 while ensuring a more uniform flow rate of the fluid in the first collection cavity 12 and effectively separating the gas in the fluid in the first collection cavity 12, thereby facilitating a reduction in the volume of the heat exchange device.
[0036] Preferably, A is 130°, 133°, 135°, 137°, 140°, 143°, 145° or 150°.
[0037] like Figure 3 and Figure 4As shown, the projection of the second manifold 13 onto a plane perpendicular to the thickness of the inlet plate 10 is rectangular. This rectangular projection helps provide a more stable containment space when fluid enters the second manifold 13 from the transition channel 14, further promoting uniform mixing of gas and liquid. The rectangular projection also reduces the likelihood of localized high-pressure areas forming within the second manifold 13, thereby reducing the risk of gas re-accumulation and blockage, and ensuring effective heat exchange when the fluid enters the flow channel plate 20 connected to the second opening 131.
[0038] like Figure 2 and Figure 3 As shown, the flow channel plate 20 has multiple spaced flow channels 21, with the number of flow channels 21 communicating with the first opening 121 being greater than the number of flow channels 21 communicating with the second opening 131. By ensuring that the number of flow channels 21 communicating with the first opening 121 is greater than the number communicating with the second opening 131, it can be ensured that most fluids with low gas content can directly enter the flow channel plate 20 communicating with the first opening 121, while fluids with high gas content enter the flow channel plate 20 communicating with the second opening 131 through the second collection chamber 13. This arrangement reduces the negative impact of gas on the heat exchange effect of most of the flow channel plate 20, improving the overall heat exchange effect of the heat exchange device.
[0039] like Figure 3 and Figure 4 As shown, the relationship between the maximum distance L1 between the wall of the first collecting cavity 12 and the first opening 121 and the maximum distance L2 between the wall of the second collecting cavity 13 and the second opening 131 satisfies: L1≥L2. This helps to ensure that the fluid can maintain a uniform distribution in the first collecting cavity 12 during the process of gas transfer from the first collecting cavity 12 to the second collecting cavity 13, and reduces excessive diffusion of gas in the second collecting cavity 13, ensuring the optimal distribution of fluid before entering the flow channel plate 20 and improving heat exchange efficiency. The relationship between the thickness D1 of the first collecting cavity 12 along the thickness direction of the liquid inlet plate 10, the thickness D2 of the second collecting cavity 13 along the thickness direction of the liquid inlet plate 10, and the thickness D3 of the transition channel 14 along the thickness direction of the liquid inlet plate 10 satisfies: D1=D2=D3. The first flow collecting cavity 12, the second flow collecting cavity 13, and the transition channel 14 have equal thicknesses along the thickness direction of the inlet plate 10, ensuring a smooth transition of the fluid within the first flow collecting cavity 12, the second flow collecting cavity 13, and the transition channel 14, thereby improving the flow efficiency of the fluid within the flow channel plate 20 and optimizing the heat exchange effect.
[0040] In some other embodiments, the maximum distance L1 between the wall of the first collecting cavity 12 and the first opening 121 and the maximum distance L2 between the wall of the second collecting cavity 13 and the second opening 131 satisfy the following relationship: L1 ≥ L2. Alternatively, the thickness D1 of the first collecting cavity 12 along the thickness direction of the liquid inlet plate 10, the thickness D2 of the second collecting cavity 13 along the thickness direction of the liquid inlet plate 10, and the thickness D3 of the transition channel 14 along the thickness direction of the liquid inlet plate 10 satisfy the following relationship: D1 = D2 = D3.
[0041] like Figure 1 As shown, the heat exchange device also includes a liquid outlet plate 40 connected to the flow channel plate 20. The flow channel plate 20 has a flow channel 21. The liquid inlet plate 10 is connected to the inlet of the flow channel 21, and the liquid outlet plate 40 is connected to the outlet of the flow channel 21. Multiple flow channel plates 20, liquid inlet plates 10, and liquid outlet plates 40 are arranged in a one-to-one correspondence. In two adjacent flow channel plates 20, the liquid inlet plate 10 of one flow channel plate 20 is adjacent to the liquid outlet plate 40 of the other flow channel plate 20, and the flow directions of the fluid in the two adjacent flow channel plates 20 are opposite. Thus, by adjusting the flow path and direction of the fluid in different flow channel plates 20, the flow path of the fluid in the heat exchange device is further optimized, ensuring that the entire heat exchange device can perform heat exchange more efficiently and uniformly, further improving the heat exchange effect of the heat exchange device.
[0042] An electrical device includes a heat exchanger, which is the heat exchanger described above. Because the heat exchanger described above can solve the problem in the related art where the inlet is located at one end of the inlet plate along the width direction of the flow channel, resulting in poor heat exchange performance, the electrical device having this heat exchanger can solve the same technical problem.
[0043] In the description of this utility model, it should be understood that "multiple" means two or more. Directional terms such as "front, back, up, down, left, right," "horizontal, vertical, perpendicular, horizontal," and "top, bottom" indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are used solely for the convenience of describing this utility model and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner or outer contours relative to the outline of each component itself.
[0044] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.
[0045] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.
[0046] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.
Claims
1. A heat exchange device, characterized in that, The system includes an inlet plate (10) and a flow channel plate (20) communicating with the inlet plate (10). The inlet plate (10) has a cavity communicating with the flow channel plate (20), and the inlet plate (10) has an inlet (11) communicating with the cavity. The cavity includes: The first collection cavity (12) is directly connected to the liquid inlet (11). The first collection cavity (12) has a first opening (121) connected to the flow channel plate (20). The flow area of the first opening (121) is greater than half of the flow area of the cavity connected to the flow channel plate (20). The second flow collection cavity (13) is connected to the first flow collection cavity (12), and the second flow collection cavity (13) has a second opening (131) connected to the flow channel plate (20); A transition channel (14) is connected between the first collection cavity (12) and the second collection cavity (13), wherein, along the thickness direction of the liquid inlet plate (10), the cross-sectional area of the transition channel (14) is smaller than the cross-sectional area of the first collection cavity (12), and the cross-sectional area of the transition channel (14) is smaller than the cross-sectional area of the second collection cavity (13).
2. The heat exchange device according to claim 1, characterized in that, The transition channel (14) has a third opening (141) that communicates with the flow channel plate (20). The relationship between the flow area S1 of the first opening (121), the flow area S2 of the second opening (131), and the flow area S3 of the third opening (141) satisfies: 0.5 < S1 / (S1+S2+S3) ≤ 0.
8.
3. The heat exchange device according to claim 1, characterized in that, The cavity wall of the first collection cavity (12) includes a first inclined surface (122), the first inclined surface (122) is disposed opposite to the first opening (121), the first inclined surface (122) is connected to the side wall of the transition channel (14), and the first inclined surface (122) gradually approaches the first opening (121) in the direction close to the transition channel (14).
4. The heat exchange device according to claim 3, characterized in that, The cavity wall of the first collection cavity (12) further includes a second inclined surface (123). The first end of the second inclined surface (123) is connected to the end of the first inclined surface (122) away from the transition channel (14). The second end of the second inclined surface (123) is connected to the first opening (121). The second inclined surface (123) is disposed opposite to the first opening (121). The second inclined surface (123) gradually approaches the first opening (121) in the direction away from the transition channel (14).
5. The heat exchange device according to claim 4, characterized in that, The plane extending along the thickness direction of the liquid inlet plate (10) and bisecting the first opening (121) is a preset plane (30). The first inclined surface (122) and the second inclined surface (123) are connected to form a connecting line (124). The connecting line (124) is located on the side of the preset plane (30) away from the transition channel (14).
6. The heat exchange device according to claim 5, characterized in that, The liquid inlet (11) is located on the side of the preset plane (30) away from the transition channel (14).
7. The heat exchange device according to claim 4, characterized in that, The included angle A between the first inclined plane (122) and the second inclined plane (123) satisfies: 130°≤A≤150°.
8. The heat exchange device according to claim 1, characterized in that, The projection of the second collection cavity (13) in a plane perpendicular to the thickness of the liquid inlet plate (10) is rectangular.
9. The heat exchange device according to claim 1, characterized in that, The flow channel plate (20) has a plurality of spaced flow channels (21), and the number of flow channels (21) communicating with the first opening (121) is greater than the number of flow channels (21) communicating with the second opening (131).
10. The heat exchange device according to claim 1, characterized in that, The relationship between the maximum distance L1 between the wall of the first collecting cavity (12) and the first opening (121) and the maximum distance L2 between the wall of the second collecting cavity (13) and the second opening (131) satisfies: L1 ≥ L2; and / or, The relationship between the thickness D1 of the first collecting cavity (12) along the thickness direction of the liquid inlet plate (10), the thickness D2 of the second collecting cavity (13) along the thickness direction of the liquid inlet plate (10), and the thickness D3 of the transition channel (14) along the thickness direction of the liquid inlet plate (10) satisfies: D1 = D2 = D3.
11. The heat exchange device according to any one of claims 1 to 10, characterized in that, The heat exchange device also includes an outlet plate (40) connected to the flow channel plate (20). The flow channel plate (20) is provided with a flow channel (21). The inlet plate (10) is connected to the inlet of the flow channel (21), and the outlet plate (40) is connected to the outlet of the flow channel (21). There are multiple flow channel plates (20), inlet plates (10), and outlet plates (40) arranged in a one-to-one correspondence. In two adjacent flow channel plates (20), the inlet plate (10) of one flow channel plate (20) is arranged adjacent to the outlet plate (40) of the other flow channel plate (20), and the flow direction of the fluid in the two adjacent flow channel plates (20) is opposite.
12. An electrical appliance, comprising a heat exchange device, characterized in that, The heat exchange device is the heat exchange device according to any one of claims 1 to 11.