Heat exchanger

Abstract

The heat exchanger comprises a first plate sheet and a second plate sheet which are arranged in a stacked mode, a first inter-plate flow channel and a second inter-plate flow channel are formed between the first plate sheet and the second plate sheet, a separation part is arranged in the first inter-plate flow channel and the second inter-plate flow channel, the separation part is provided with a communicating part, and the communicating part communicates areas on the two sides of the separation part. The extending direction perpendicular to the partition parts is defined as the first direction, the communicating parts are arranged in a staggered mode relative to the center line of the plate sheet in the first direction, and the number of the partition parts of the first inter-plate flow channel is larger than that of the partition parts of the second inter-plate flow channel; the number of the partition parts of the first inter-plate flow channel is larger than that of the partition parts of the second inter-plate flow channel, the length of the first inter-plate flow channel is increased, then the width of the first inter-plate flow channel is reduced, the flow speed of a refrigerant is increased, and then the heat exchange effect of the refrigerant and cooling liquid is improved; and the width of the first inter-plate flow channel is reduced, so that the pressure drop on the cooling liquid side cannot be influenced, the heat exchange effect can be enhanced while the pressure drop on the cooling liquid side is kept stable, and the performance of the heat exchanger is improved.

Description

Technical Field

[0001] The present application relates to the field of thermal management technology, and in particular to a heat exchanger. Background Art

[0002] The optimization direction of the heat exchanger is to reduce the fluid pressure drop and / or improve the heat exchange performance. Therefore, how to improve the heat exchange performance is an important technical issue of the heat exchanger. Summary of the invention

[0003] The purpose of the present application is to provide a heat exchanger, which utilizes a partition to increase the path length of the first inter-plate flow channel and the second inter-plate flow channel, and the path of the first inter-plate flow channel is longer than that of the second inter-plate flow channel. Compared with the technical solution in which the paths of the first inter-plate flow channel and the second inter-plate flow channel are equal, since the total area of ​​the plate remains unchanged, the length of the first inter-plate flow channel increases, which reduces the width of the first inter-plate flow channel, resulting in an increase in the refrigerant flow rate, thereby improving the heat exchange effect between the refrigerant and the coolant, and the reduction in the width of the first inter-plate flow channel will not increase the pressure drop on the coolant side, which can enhance the heat exchange effect without increasing the pressure drop on the coolant side, thereby improving the performance of the heat exchanger.

[0004] One embodiment of the present application provides a heat exchanger, comprising a first plate and a second plate arranged in a stacked manner, wherein the first plate and the second plate both comprise a first plate surface and a second plate surface, the heat exchanger having a first inter-plate flow channel and a second inter-plate flow channel, the first inter-plate flow channel being located between the first plate surface of the first plate and the second plate surface of the second plate on one side adjacent thereto, the second inter-plate flow channel being located between the second plate surface of the first plate and the first plate surface of the second plate on the other side adjacent thereto, the first inter-plate flow channel and the second inter-plate flow channel being not connected, the heat exchanger comprising a partition, the partition located in the first inter-plate flow channel being defined as a first partition, the partition located in the second inter-plate flow channel being defined as a second partition, the partition extending from one side of the plate to the other opposite side, a connecting portion being provided between an end of the partition and a side of the plate along an extending direction of the partition, the connecting portion connecting areas on both sides of the partition, and the number of the first partitions being greater than the number of the second partitions.

[0005] In the above technical solution, partitions are arranged in the first inter-plate flow channel and the second inter-plate flow channel of the heat exchanger, and the number of first partitions in the first inter-plate flow channel is greater than the number of second partitions in the second inter-plate flow channel, thereby increasing the length of the first inter-plate flow channel and reducing the width. Compared with the technical solution with the same number of first partitions and second partitions, since the total area of ​​the plates remains unchanged, the increase in the length of the first inter-plate flow channel reduces the width of the first inter-plate flow channel, resulting in an increase in the refrigerant flow rate, thereby improving the heat exchange effect between the refrigerant and the coolant, and the reduction in the width of the first inter-plate flow channel will not affect the pressure drop on the coolant side, and can maintain the pressure drop on the coolant side unchanged while enhancing the heat exchange effect, thereby improving the performance of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0006] Figure 1 It is a three-dimensional structural schematic diagram of an implementation mode of the heat exchanger of the present application;

[0007] Figure 2 is a schematic diagram of the stacking structure of the first plate and the second plate in the present application;

[0008] Figure 3 yes Figure 1 A schematic diagram of the cross-sectional structure of the heat exchanger in the AA direction is shown;

[0009] Figure 4 yes Figure 3 A partial enlarged view of point B in the middle;

[0010] Figure 5 yes Figure 1 A schematic cross-sectional structure diagram of ;

[0011] Figure 6 yes Figure 2 A schematic structural diagram of a first implementation scheme of the first plate;

[0012] Figure 7 is with Figure 6 A schematic structural diagram of a first implementation mode of a second plate corresponding to the first plate;

[0013] Figure 8 The refrigerant is Figure 6 A schematic diagram of the flow path in the first plate structure shown;

[0014] Fig. 9 Is the coolant in Figure 7 A schematic diagram of the flow path in the second plate structure shown;

[0015] Fig.10 It is a schematic diagram of the structure of the second embodiment of the first plate of the present application and the flow path of the refrigerant;

[0016] Fig.11 is with Fig.10A schematic diagram of a second embodiment structure of a second plate corresponding to the first plate and a flow path of a coolant;

[0017] Fig.12 1 is a schematic diagram of the structure of the third embodiment of the first plate of the present application and the flow path of the refrigerant;

[0018] Fig.13 is with Fig.12 A schematic diagram of a third embodiment structure of a second plate corresponding to the first plate and a flow path of a coolant;

[0019] Fig.14 1 is a schematic diagram of the structure of the fourth embodiment of the first plate of the present application and the flow path of the refrigerant;

[0020] Fig.15 is with Fig.14 A schematic diagram of a fourth embodiment structure of a second plate corresponding to the first plate and a flow path of a coolant;

[0021] Fig.16 1 is a schematic diagram of the structure of the fifth embodiment of the first plate of the present application and the flow path of the refrigerant;

[0022] Fig.17 is with Fig.16 A schematic diagram of a fifth embodiment structure of a second plate corresponding to the first plate and a flow path of a coolant;

[0023] Fig.18 1 is a schematic diagram of the structure of the sixth embodiment of the first plate of the present application and the flow path of the refrigerant;

[0024] Fig.19 is with Fig.18 A sixth embodiment structure of the second plate corresponding to the first plate and a schematic diagram of the flow path of the coolant;

[0025] Fig. 20 1 is a schematic diagram of the structure of the seventh embodiment of the first plate of the present application and the flow path of the refrigerant;

[0026] Fig.21 is with Fig. 20 A schematic diagram of a seventh embodiment structure of a second plate corresponding to the first plate and a flow path of a coolant;

[0027] Fig. 22 1 is a schematic diagram of the structure of the eighth embodiment of the first plate of the present application and the flow path of the refrigerant;

[0028] Fig.23 is with Fig. 22 An eighth embodiment structure of the second plate corresponding to the first plate and a schematic diagram of the flow path of the coolant;

[0029] Fig.24 1 is a schematic diagram of the structure of the ninth embodiment of the first plate of the present application and the flow path of the refrigerant;

[0030] Fig.25 is with Fig.24 A schematic diagram of a ninth embodiment of the structure of the second plate corresponding to the first plate and a flow path of the coolant;

[0031] Fig.26 is with Fig.24 A schematic diagram of the structure of the first plate;

[0032] Fig. 27 is with Fig.26 Enlarged schematic diagram of the structure at C in the middle.

[0033] Reference numerals:

[0034] Plate 1, first plate 2, second plate 3, first plate surface 11, partition 111, first partition 111A, second partition 111B, connecting portion 1111, first connecting portion 1111A, second connecting portion 1111B, groove 112, protrusion 113, recess 114, drainage portion 115, second plate surface 12, edge 13, first inter-plate flow channel 14, first inflow portion 141, first outflow portion 142, first flow channel 143, second flow channel 144, third flow channel 145, second inter-plate flow channel 15, second inflow portion 151, second outflow portion 152, first corner hole 16, second corner hole 17, third corner hole 18, fourth corner hole 19, first convex portion 20, second convex portion 21, channel 211, 22, first channel; 23, second channel. DETAILED DESCRIPTION

[0035] Specific embodiments are now described in detail with reference to the accompanying drawings. In order to fully understand the present invention, many specific details are mentioned in the following detailed description, but those skilled in the art should understand that the specific components, devices and features illustrated in the drawings and described herein are merely exemplary and should not be considered as limiting. The directional words such as "upper", "lower", "left" and "right" mentioned in this specification are all based on the drawings of the specification. The ordinal numbers such as "first", "second" and "third" of the component names introduced for ease of description are also introduced for ease of description, but this information should not be limited to these descriptions. These terms are only used to distinguish the same type of information from each other.

[0036] Embodiment 1

[0037] Please refer to Figure 1-Figure 5The first embodiment shown in the figure specifically discloses a heat exchanger, including a first plate 2 and a second plate 3 arranged in a stacked manner, wherein the first plate 2 and the second plate 3 both include a first plate surface 11 and a second plate surface 12, and the heat exchanger has a first inter-plate flow channel 14 and a second inter-plate flow channel 15, wherein the first inter-plate flow channel 14 is located between the first plate surface 11 of the first plate 2 and the second plate surface 12 of the second plate 3 on one side adjacent thereto, and the refrigerant flows in the first inter-plate flow channel 14, and the second inter-plate flow channel 15 is located between the second plate surface 12 of the first plate 2 and the first plate surface 12 of the second plate 3 on the other side adjacent thereto. The first plate inter-plate flow channel 14 and the second plate inter-plate flow channel 15 are not connected, the coolant and the refrigerant are not in contact, and the coolant and the refrigerant exchange heat through the plate 1. It should be noted that the plate 1 mentioned here refers to any one of the first plate 2 and the second plate 3. The heat exchanger includes a partition 111. The partition 111 and the plate 1 are an integral structure. For example, the partition 111 is formed by stamping the plate 1, or the partition 111 is welded and fixed to the plate 1. The partition 111 located in the first plate inter-plate flow channel 14 is defined as the first partition 1. 11A, the partition 111 located in the second inter-plate flow channel 15 is defined as the second partition 111B, the partition 111 extends from one side of the plate 1 to the other opposite side, along the extension direction of the partition 111, there is a connecting portion 1111 between the end of the partition 111 and the side of the plate 1, and the connecting portion 1111 connects the areas on both sides of the partition 111. It should be noted that the area described here refers to the first inter-plate flow channel 14 and the second inter-plate flow channel 15. The coolant and the refrigerant bypass the partition 111 and flow from one side of the partition 111 to the other side through the connecting portion 1111. The partitions 111 increase the flow paths of the coolant and the refrigerant. The number of first partitions 111A is greater than the number of second partitions 111B, and the number of second partitions 111B can be zero, which results in the length of the first inter-plate flow channel 14 being longer than the length of the second inter-plate flow channel 15. Compared with the technical solution with the same number of first partitions 111A and second partitions 111B, since the total area of ​​the plate 1 remains unchanged, the length of the first inter-plate flow channel 14 is increased, which reduces the width of the first inter-plate flow channel 14, thereby increasing the refrigerant flow rate and enhancing the heat exchange effect on the coolant.

[0038] Embodiment 2

[0039] Specifically, refer to Figure 1 — Fig.11The second embodiment of the present application shown in the figure specifically discloses a heat exchanger, including a first plate 2 and a second plate 3 arranged in a stacked manner, the first plate 2 and the second plate 3 both including a first plate surface 11 and a second plate surface 12, the heat exchanger having a first inter-plate flow channel 14 and a second inter-plate flow channel 15, the first inter-plate flow channel 14 is located between the first plate surface 11 of the first plate 2 and the second plate surface 12 of the second plate 3 on one side adjacent thereto, the refrigerant flows in the first inter-plate flow channel 14, the second inter-plate flow channel 15 is located between the second plate surface 12 of the first plate 2 and the first plate surface 11 of the second plate 3 on the other side adjacent thereto, the coolant flows in the second inter-plate flow channel 15, the first The first inter-plate flow channel 14 and the second inter-plate flow channel 15 are not connected, the coolant and the refrigerant are not in contact, the coolant and the refrigerant exchange heat through the plate 1, the heat exchanger includes a partition 111, the partition 111 is formed by stamping the plate 1, the partition 111 extends from one side of the plate 1 to the other side opposite, three first partitions 111A are arranged in the first inter-plate flow channel 14, the first direction is defined as a first direction perpendicular to the extension direction of the partition 111, the three first partitions 111A are distributed along the first direction, the first partition 111A protrudes toward the second plate surface 12 of the adjacent second plate 3, and there is a first space between the end of the first partition 111A and the side of the first plate 2 A connecting portion 1111A, the first connecting portion 1111A connects the areas on both sides of the first partition 111A, along the first direction, the first connecting portion 1111A is staggered about the center line of the first plate 2, the length of the first inter-plate flow channel 14 is increased, the heat exchange time between the refrigerant and the coolant is increased, and the heat exchange effect is enhanced. It should be noted that the staggered arrangement mentioned here means that the two adjacent first connecting portions 1111A are located on different sides of the center line of the first plate 2, and a second partition 111B is arranged in the second inter-plate flow channel 15, the second partition 111B is formed by stamping the second plate 3, and the second partition 111B is toward the second plate surface of the adjacent first plate 2 The second partition 111B is protruding in the direction 12, and a second connecting portion 1111B is provided between the end of the second partition 111B and the side of the second plate 3. The second connecting portion 1111B connects the areas on both sides of the second partition 111B. The stacking direction of the first plate 2 and the second plate 3 is defined as the second direction, and the surface perpendicular to the second direction is defined as the first surface. The orthographic projection of the first partition 111A on the first surface does not overlap with the orthographic projection of the second partition 111B on the first surface. The groove 112 formed by the partition 111 on the second plate surface 12 does not overlap with the partition 111 of the adjacent plate 1 along the first direction, so as to prevent the coolant and the refrigerant from flowing through the gap between the groove 112 and the partition 111.

[0040] The plate 1 includes an edge 13, and the partition 111 is sealed and connected to the first plate surface 11 of the plate 1 where the partition 111 is located, the edge 13 of the adjacent plate 1, and the second plate surface 12 of the adjacent plate 1. The three first partitions 111A divide the first inter-plate flow channel 14 into four areas, and the four areas are connected only by the first connecting part 1111A, so that the refrigerant bypasses the three first partitions 111A through the first connecting part 1111A and flows through the four areas of the first inter-plate flow channel 14. A second partition 111B divides the second inter-plate flow channel 15 into two areas, and the two areas are connected only by the second connecting part 1111B, so that the coolant bypasses the second partition 111B through the second connecting part 1111B and flows through the two areas of the second inter-plate flow channel 15.

[0041] Reference Figure 2 , Figure 5 , Figure 8 and Fig. 9The plate 1 has a first corner hole 16, a second corner hole 17, a third corner hole 18, and a fourth corner hole 19. The third corner hole 18 and the fourth corner hole 19 of the first plate 2 are formed with a first convex portion 20 protruding from the first plate surface 11, and the first convex portion 20 does not contact the edge of the first plate 2. The first corner hole 16 and the second corner hole 17 of the second plate 3 are formed with a second convex portion 21 protruding from the first plate surface 11, and the second convex portion 21 does not contact the edge of the second plate 3. The first convex portion 20 is sealed and connected to the second plate surface 12 of the second plate 3, and the second convex portion 21 is sealed and connected to the second plate surface 12 of the first plate 2. The refrigerant flows into the first inter-plate flow channel 14 through the second corner hole 17. The refrigerant bypasses the third corner hole 18 and the fourth corner hole 19 in the first inter-plate flow channel 14 due to the shielding of the first convex portion 20 and flows out through the first corner hole 16. The coolant flows into the second inter-plate flow channel 15 through the third corner hole 18. The coolant bypasses the first corner hole 16 and the second corner hole 17 in the second inter-plate flow channel 15 due to the shielding of the second convex portion 21 and flows out through the fourth corner hole 19. Along the second direction, the first corner hole 16, the second corner hole 17, the third corner hole 18, and the fourth corner hole 19 of the adjacent plates 1 correspond to each other. Along the second direction, the refrigerant passes through the plurality of The channels 211 formed by the second protrusions 21 of the plates 1 flow through the plurality of first inter-plate flow channels 14, and the coolant flows through the channels 211 formed by the first protrusions 20 of the plurality of plates 1 through the plurality of second inter-plate flow channels 15. The first inter-plate flow channel 14 has a first inflow portion 141 and a first outflow portion 142, and the second inter-plate flow channel 15 has a second inflow portion 151 and a second outflow portion 152. Along the first direction, the first inflow portion 141 and the second corner hole 17 are located on the same side of the first partition 111A. It should be noted that the first partition 111A mentioned here refers to all the channels located in the first inter-plate flow channel 14. The first partition 111A, the first outflow portion 142 and the first corner hole 16 are located on the other side of the first partition 111A, the refrigerant flows from the second inflow portion 151 and the third corner hole 18 on the same side of the second partition 111B, the second outflow portion 152 and the fourth corner hole 19 are located on the other side of the second partition 111B, and the refrigerant passes through the first partition 111A when flowing in the first inter-plate flow channel 14, thereby increasing the heat exchange effect. Along the stacking direction of the first plate 2 and the second plate 3, the first corner holes 16, the second corner holes 17, the third corner holes 18, and the fourth corner holes 19 of the plurality of plates 1 correspond to each other in upper and lower positions.

[0042] Reference Figure 3-5The first plate surface 11 of the plate 1 is provided with a protrusion 113, and the protrusion 113 is set with a gap. The protrusion 113 is sealed and connected with the second plate surface 12 of the adjacent plate 1. The protrusion 113 contacts the second plate surface 12 of the adjacent plate 1, disturbs the coolant and the refrigerant, and improves the heat exchange effect. The protrusion 113 is formed with a corresponding recess 114 on the second plate surface 12 of the plate 1. The protrusion 113 is formed by stamping the plate 1, which is convenient for processing. The orthographic projection of the protrusion 113 of the first plate 2 on the first surface does not overlap with the orthographic projection of the protrusion 113 of the second plate 3 on the first surface, that is, the protrusion 113 does not overlap with the recess 114 of the adjacent plate 1, thereby increasing the flow path of the coolant and the refrigerant.

[0043] Reference Figure 8 and Fig. 9 , along the extending direction of the partition 111, the first corner hole 16 and the second corner hole 17 are located on one side of the plate 1, the third corner hole 18 and the fourth corner hole 19 are located on the other side of the plate 1, the second corner hole 17 and the third corner hole 18 are arranged diagonally, the first corner hole 16 and the fourth corner hole 19 are arranged diagonally, the refrigerant flowing between the first corner hole 16 and the second corner hole 17 will be blocked by the first partition 111A and change the flow direction, the coolant flowing between the third corner hole 18 and the fourth corner hole 19 will also be blocked by the second partition 111B and change the flow direction, the first connecting portion 1111A near the first corner hole 16 and the first connecting portion 1111A near the second corner hole 17 are located at the third corner hole 1 8 and the fourth corner hole 19, the middle connecting portion 1111 is located between the first corner hole 16 and the second corner hole 17, so that the first corner hole 16 can bypass the first partition 111A based on the first inter-plate flow channel 14 and communicate with the second corner hole 17 through the first connecting portion 1111A, increase the length of the first inter-plate flow channel 14, increase the heat exchange time between the refrigerant and the coolant, and enhance the heat exchange effect. Along the first direction, the second connecting portion 1111B is located between the first corner hole 16 and the second corner hole 17, so that the third corner hole 18 can bypass the second partition 111B based on the second inter-plate flow channel 15 and communicate with the fourth corner hole 19 through the second connecting portion 1111B; of course, you can also refer to Fig.10 and Fig.11 The second corner hole 17 and the fourth corner hole 19 are arranged diagonally, and the first corner hole 16 and the third corner hole 18 are arranged diagonally.

[0044] Reference Figure 4 , Figure 8 and Fig.10Along the first direction, the first inter-plate flow channel 14 has a first flow channel 143 and a second flow channel 144. The first flow channel 143 is located on the side of the first partition 111A closest to the second corner hole 17 and close to the second corner hole 17, and the second flow channel 144 is located on the other side of the first partition 111A relative to the first flow channel 143. The ratio of the width of the second flow channel 144 to the width of the first flow channel 143 is in the range of 1-3. Since the refrigerant has more liquid phase and a lower flow rate in the first flow channel 143, the width of the first flow channel 143 is reduced to increase the flow rate of the refrigerant in the first flow channel 143 and enhance the heat exchange effect.

[0045] Embodiment 3

[0046] For details, please refer to Fig.12 , Fig.13 The third embodiment of the present application is shown, and the difference between this embodiment and the previous embodiment lies in that, along the extension direction of the partition 111, the first corner hole 16, the second corner hole 17, the third corner hole 18 and the fourth corner hole 19 are located on the same side of the plate 1, the third corner hole 18 and the fourth corner hole 19 are located on the inner side of the first corner hole 16 and the second corner hole 17, the third corner hole 18 is closer to the first corner hole 16 than the fourth corner hole 19, and the first plate surface 11 of the second plate 3 is provided with a drainage portion 115, the drainage portion 115 guides the coolant to flow to the outside of the plate 1, thereby enhancing the heat exchange effect between the refrigerant and the coolant.

[0047] Of course, you can also refer to Fig.14 and Fig.15 In the arrangement, the fourth corner hole 19 is closer to the first corner hole 16 than the third corner hole 18.

[0048] In this embodiment, along the extension direction of the partition 111, the first corner hole 16, the second corner hole 17, the third corner hole 18 and the fourth corner hole 19 are located on the same side, that is, the inlets and outlets of the coolant and the refrigerant are located on the same side, and the inlet and outlet of the coolant are located on the inner side of the inlet and outlet of the refrigerant, resulting in uneven flow distribution of the coolant. More coolant flows along a path close to the second partition 111B, and less coolant flows along a path away from the second partition 111B. The coolant is guided to flow to the outside through the drainage portion 115, and the coolant on the outside is kept flowing on the outside, so as to adjust the flow distribution and enhance the heat exchange effect.

[0049] Embodiment 4

[0050] For details, please refer to Fig.16 , Fig.17The fourth embodiment of the present application is shown, and the difference between this embodiment and the second embodiment lies in that the first partition 111A of the first inter-plate flow channel 14 is one, the second partition 111B of the second inter-plate flow channel 15 is zero, and the protrusions 113 of the second plate 3 are denser than the protrusions 113 of the first plate 2. The denser protrusions 113 cause the flow resistance to increase, but because there is no second partition 111B, the length of the second inter-plate flow channel 15 is reduced by half, and the width of the second inter-plate flow channel 15 is increased, thereby reducing the flow resistance, compensating for the increased flow resistance due to the denser protrusions 113, and keeping the overall pressure drop on the coolant side stable. The denser protrusions 113 can enhance the heat exchange effect, and improve the heat exchange effect while maintaining the pressure drop on the coolant side.

[0051] The first corner hole 16, the second corner hole 17 and the fourth corner hole 19 are located on one side of the plate 1, the third corner hole 18 is located on the other side of the plate 1, the fourth corner hole 19 is located between the first corner hole 16 and the second corner hole 17, the first partition 111A is located between the second corner hole 17 and the fourth corner hole 19, the refrigerant bypasses the first partition 111A, the flow path is increased, and the heat exchange effect is improved. Along the first direction, the first inter-plate flow channel 14 has a first flow channel 143 and a second flow channel 144, the first flow channel 143 is located on the side of the first partition 111A close to the second corner hole 17, the second flow channel 144 is located on the other side of the first partition 111A relative to the first flow channel 143, the width of the second flow channel 144 is in the range of 1.2-4 to the width of the first flow channel 143, because the refrigerant has more liquid phase and lower flow rate in the first flow channel 143, the width of the first flow channel 143 is reduced, the flow rate of the refrigerant in the first flow channel 143 is increased, and the heat exchange effect is enhanced.

[0052] Reference Fig.18 and Fig.19 Of course, the third corner hole 18 can also be located on one side of the plate 1 together with the first corner hole 16 and the second corner hole 17, the third corner hole 18 is located between the first corner hole 16 and the second corner hole 17, the fourth corner hole 19 is located on the other side of the plate 1, and the first partition 111A is located between the second corner hole 17 and the third corner hole 18.

[0053] Embodiment 5

[0054] For details, please refer to Figure 20-23The fifth embodiment of the present application shown in the figure is different from the second embodiment in that the first partition 111A of the first inter-plate flow channel 14 is two, the first corner hole 16 is located on one side of the plate 1, and the second corner hole 17 is located on the other side opposite to the plate 1, the first corner hole 16 and the second corner hole 17 are arranged diagonally, and the length of the first inter-plate flow channel 14 is increased and the width is reduced by the two first partitions 111A, thereby enhancing the heat exchange effect, and the second partition 111B of the second inter-plate flow channel 15 is one , the third corner hole 18 and the fourth corner hole 19 are located on the same side of the plate 1, and the second inter-plate flow channel 15 is increased in length and reduced in width through a second partition 111B, thereby enhancing the heat exchange effect. The second corner hole 17, the third corner hole 18 and the fourth corner hole 19 are located on the same side of the plate 1, and along the first direction, the fourth corner hole 19 is located between the second corner hole 17 and the third corner hole 18, and one first partition 111A is located between the third corner hole 18 and the fourth corner hole 19, and another The first partition 111A is located between the fourth corner hole 19 and the second corner hole 17, and the second partition 111B is located between the fourth corner hole 19 and the third corner hole 18. In this embodiment, the refrigerant bypasses the first partition 111A, and the coolant bypasses the second partition 111B, the flow path is increased, and the heat exchange effect is improved. The refrigerant flows into the first inter-plate flow channel 14 through the second corner hole 17, and the refrigerant bypasses the third corner hole 18 and the fourth corner hole 19 in the first inter-plate flow channel 14 and flows out through the first corner hole 16. The coolant flows through the third The corner hole 18 flows into the second inter-plate flow channel 15, and the coolant bypasses the first corner hole 16 and the second corner hole 17 in the second inter-plate flow channel 15 and flows out through the fourth corner hole 19. Of course, the refrigerant can also flow into the first inter-plate flow channel 14 through the first corner hole 16, and the refrigerant bypasses the third corner hole 18 and the fourth corner hole 19 in the first inter-plate flow channel 14 and flows out through the second corner hole 17, and the coolant flows into the second inter-plate flow channel 15 through the fourth corner hole 19, and the coolant bypasses the first corner hole 16 and the second corner hole 17 in the second inter-plate flow channel 15 and flows out through the third corner hole 18.

[0055] Further, along the first direction, the first inter-plate flow channel 14 has a first flow channel 143, a second flow channel 144 and a third flow channel 145, the first flow channel 143, the second flow channel 144 and the third flow channel 145 are separated and formed by two first partitions 111A, the second flow channel 144 is located between the first flow channel 143 and the third flow channel 145, along the first direction, the first flow channel 143 is farther away from the first angular hole 16 than the second flow channel 144, the refrigerant flows into the first flow channel 143, the second flow channel 144, and the third flow channel 145 through the second angular hole 17, and flows out from the first angular hole 16, along the first direction, the ratio of the width of the second flow channel 144 to the width of the first flow channel 143 is in the range of 1-3, because the refrigerant flows into the first inter-plate flow channel 14 from the second angular hole 17, the liquid phase is more in the first flow channel 143 and the flow rate is lower, and the liquid phase is less in the second flow channel 144 than in the first flow channel 143, so the first The width of the flow channel 143 is reduced to increase the flow rate of the refrigerant in the first flow channel 143, and the width of the second flow channel 144 is increased to reduce the flow rate in the second flow channel 144, while reducing the temperature difference between the refrigerant in the first flow channel 143 and the second flow channel 144, thereby enhancing the heat exchange effect. The ratio of the width of the third flow channel 145 to the width of the second flow channel 144 is in the range of 1-3, and the ratio of the width of the third flow channel 145 to the width of the second flow channel 144 is in the range of 1-3. The refrigerant flows into the first inter-plate channel 14 from the second corner hole 17, passes through the second channel 144 first and then flows into the third channel 145. The refrigerant has more liquid phase and a lower flow rate in the second channel 144, and the liquid phase in the third channel 145 is less than that in the second channel 144. Therefore, the width of the third channel 145 is made larger than the width of the second channel 144 to reduce the flow rate in the third channel 145 and reduce the temperature difference between the refrigerant in the second channel 144 and the third channel 145, thereby enhancing the heat exchange effect.

[0056] Furthermore, there is more gas phase in the third flow channel 145, and the width ratio of the first flow channel 143, the second flow channel 144, and the third flow channel 145 is 1:2:3, which reduces the temperature difference of the refrigerant in the first inter-plate flow channel 14, thereby enhancing the heat exchange effect.

[0057] Reference Fig. 22 and Fig.23 Of course, the first corner hole 16, the third corner hole 18 and the fourth corner hole 19 may also be located on one side of the plate 1, and along the first direction, the third corner hole 18 is located between the first corner hole 16 and the fourth corner hole 19, the first partition 111A is located between the fourth corner hole 19 and the third corner hole 18, and the second partition 111B is located between the fourth corner hole 19 and the third corner hole 18. Embodiment 6

[0058] For details, please refer to Figure 24-Figure 27 The sixth embodiment of the present application is shown. The difference between this embodiment and the fifth embodiment is that the second partition 111B of the second inter-plate flow channel 15 is zero. Along the extension direction of the partition 111, the first corner hole 16 and the second corner hole 17 are located on different sides of the plate 1, and the third corner hole 18 and the fourth corner hole 19 are located on different sides of the plate 1. Along the first direction, the first partition 111A is located between the first corner hole 16 and the second corner hole 17. The two first partitions 111A increase the length and reduce the width of the first inter-plate flow channel 14, thereby enhancing the heat exchange effect. At least one of the first partitions 111A is located between the third corner hole 18 and the fourth corner hole 19. In this embodiment, the refrigerant bypasses the first partition 111A. The flow path is increased to improve the heat exchange effect. The refrigerant flows into the first inter-plate flow channel 14 through the second angular hole 17. The refrigerant bypasses the third angular hole 18 and the fourth angular hole 19 in the first inter-plate flow channel 14 and flows out through the first angular hole 16. The coolant flows into the second inter-plate flow channel 15 through the third angular hole 18. The coolant bypasses the first angular hole 16 and the second angular hole 17 in the second inter-plate flow channel 15 and flows out through the fourth angular hole 19. Of course, the refrigerant can also flow into the first inter-plate flow channel 14 through the first angular hole 16. The refrigerant bypasses the third angular hole 18 and the fourth angular hole 19 in the first inter-plate flow channel 14 and flows out through the second angular hole 17. The coolant flows into the second inter-plate flow channel 15 through the fourth angular hole 19. The coolant bypasses the first angular hole 16 and the second angular hole 17 in the second inter-plate flow channel 15 and flows out through the third angular hole 18.

[0059] Further, along the first direction, the first inter-plate flow channel 14 has a first flow channel 143, a second flow channel 144 and a third flow channel 145, the first flow channel 143, the second flow channel 144 and the third flow channel 145 are separated and formed by two first partitions 111A, the second flow channel 144 is located between the first flow channel 143 and the third flow channel 145, along the first direction, the first flow channel 143 is farther away from the first angular hole 16 than the second flow channel 144, the refrigerant flows into the first flow channel 143, the second flow channel 144, and the third flow channel 145 through the second angular hole 17, and flows out from the first angular hole 16, along the first direction, the ratio of the width of the second flow channel 144 to the width of the first flow channel 143 is in the range of 1-3, because the refrigerant flows into the first inter-plate flow channel 14 from the second angular hole 17, the liquid phase is more in the first flow channel 143 and the flow rate is lower, and the liquid phase is less in the second flow channel 144 than in the first flow channel 143, so the first The width of the flow channel 143 is reduced to increase the flow rate of the refrigerant in the first flow channel 143, and the width of the second flow channel 144 is increased to reduce the flow rate in the second flow channel 144, while reducing the temperature difference between the refrigerant in the first flow channel 143 and the second flow channel 144, thereby enhancing the heat exchange effect. The ratio of the width of the third flow channel 145 to the width of the second flow channel 144 is in the range of 1-3, and the ratio of the width of the third flow channel 145 to the width of the second flow channel 144 is in the range of 1-3. The refrigerant flows into the first inter-plate channel 14 from the second corner hole 17, passes through the second channel 144 first and then flows into the third channel 145. The refrigerant has more liquid phase and a lower flow rate in the second channel 144, and the liquid phase in the third channel 145 is less than that in the second channel 144. Therefore, the width of the third channel 145 is made larger than the width of the second channel 144 to reduce the flow rate in the third channel 145 and reduce the temperature difference between the refrigerant in the second channel 144 and the third channel 145, thereby enhancing the heat exchange effect.

[0060] Furthermore, there is more gas phase in the third flow channel 145, and along the first direction, the width ratio of the second flow channel 144 to the first flow channel 143 is 4:3, and the width ratio of the third flow channel 145 to the second flow channel 144 is 1, which reduces the temperature difference of the refrigerant in the first inter-plate flow channel 14, thereby enhancing the heat exchange effect.

[0061] Further, refer to Fig.26 , Fig. 27Along the first direction, a first channel 22 is provided between the first partition 111A and the adjacent protrusion 113, and the refrigerant flows through the first channel 22. A second channel 23 is provided between the adjacent protrusions 113, and the refrigerant flows through the second channel 23. The width of the first channel 22 is smaller than the width of the second channel 23. The width of the first channel 22 is smaller than the width of the second channel 23, and it is more difficult for the refrigerant to flow from the first channel 22. The refrigerant is prevented from flowing from the first channel 22, and the bypass of the refrigerant is reduced, thereby enhancing the heat exchange effect.

[0062] It should be noted that: the heat exchanger provided by the present application is introduced in detail above. Specific examples are used in this article to illustrate the principles and implementation methods of the present application. The description of the above embodiments is only used to help understand the core idea of ​​the present application. It should be pointed out that for ordinary technicians in this technical field, without departing from the principles of the present application, several improvements and modifications can be made to the present application, and these improvements and modifications also fall within the scope of protection of the claims of the present application.

Claims

1. A heat exchanger, characterized in that , comprising a first plate (2) and a second plate (3) arranged in a stacked manner, wherein the first plate (2) and the second plate (3) both comprise a first plate surface (11) and a second plate surface (12), the heat exchanger having a first inter-plate flow channel (14) and a second inter-plate flow channel (15), the first inter-plate flow channel (14) being located between the first plate surface (11) of the first plate (2) and the second plate surface (12) of the second plate (3) on one side adjacent thereto, the second inter-plate flow channel (15) being located between the second plate surface (12) of the first plate (2) and the first plate surface (11) of the second plate (3) on the other side adjacent thereto, the first inter-plate flow channel (14) and the second inter-plate flow channel (15) being not connected The heat exchanger comprises a partition (111), wherein the partition (111) located in the first inter-plate flow channel (14) is defined as a first partition (111A), and the partition (111) located in the second inter-plate flow channel (15) is defined as a second partition (111B), wherein the partition (111) extends from one side of the plate (1) to the other opposite side, and along the extension direction of the partition (111), a connecting portion (1111) is provided between the end of the partition (111) and the side of the plate (1), and the connecting portion (1111) connects the areas on both sides of the partition (111), and the number of the first partitions (111A) is greater than the number of the second partitions (111B).

2. The heat exchanger according to claim 1, characterized in that: The plate (1) comprises an edge portion (13), and the partition portion (111) is sealedly connected to a first plate surface (11) of the plate (1) where the partition portion (111) is located, an edge portion (13) of an adjacent plate (1), and a second plate surface (12) of an adjacent plate (1).

3. The heat exchanger according to claim 2, characterized in that: The plate (1) has a first corner hole (16), a second corner hole (17), a third corner hole (18), and a fourth corner hole (19); the first inter-plate flow channel (14) has a first inflow portion (141) and a first outflow portion (142); the second inter-plate flow channel (15) has a second inflow portion (151) and a second outflow portion (152); a first direction is defined as a direction perpendicular to the extension direction of the partition (111); along the first direction, the first inflow portion (141) and the second corner hole (17) are located on the same side of the first partition (111A); the first outflow portion (142) and the first corner hole (16) are located on the other side of the first partition (111A); the second inflow portion (151) and the third corner hole (18) are located on the same side of the second partition (111B); the second outflow portion (152) and the fourth corner hole (19) are located on the other side of the second partition (111B).

4. The heat exchanger according to claim 3, characterized in that The first plate surface (11) of the plate (1) is provided with a protrusion (113), the protrusion (113) is arranged with a gap, and the protrusion (113) is sealed and connected to the second plate surface (12) of the adjacent plate (1).

5. The heat exchanger according to claim 3 or 4, characterized in that: Three first partitions (111A) are arranged in the first inter-plate flow channel (14), and the three first partitions (111A) are distributed along the first direction. At most two second partitions (111B) are arranged in the second inter-plate flow channel (15), and along the first direction, the connecting parts (1111) are staggered about the center line of the plate (1).

6. The heat exchanger according to claim 5, characterized in that Along the extension direction of the partition (111), the first corner hole (16) and the second corner hole (17) are located on one side of the plate (1), and the third corner hole (18) and the fourth corner hole (19) are located on the other side of the plate (1); a first convex portion (20) protruding from the first plate surface (11) is formed around the third corner hole (18) and the fourth corner hole (19) of the first plate (2); the first convex portion (20) is not in contact with the edge of the first plate (2); a second convex portion (21) protruding from the first plate surface (11) is formed around the first corner hole (16) and the second corner hole (17) of the second plate (3); the second convex portion (21) is not in contact with the edge of the second plate (3); the first convex portion (20) is sealed to the second plate surface (12) of the second plate (3); and the second convex portion (21) is sealed to the second plate surface (12) of the first plate (2); The second corner hole (17) and the third corner hole (18) are arranged diagonally, and the first corner hole (16) and the fourth corner hole (19) are arranged diagonally; or, the second corner hole (17) and the fourth corner hole (19) are arranged diagonally, and the first corner hole (16) and the third corner hole (18) are arranged diagonally; The connecting portion (1111) corresponding to the first partition portion (111A) is defined as a first connecting portion (1111A); along the first direction, the first connecting portion (1111A) close to the first corner hole (16) and the first connecting portion (1111A) close to the second corner hole (17) are located between the third corner hole (18) and the fourth corner hole (19); and the first connecting portion (1111A) in the middle is located between the first corner hole (16) and the second corner hole (17); The connecting portion (1111) corresponding to the second partition portion (111B) is defined as a second connecting portion (1111B), and along the first direction, at least one second connecting portion (1111B) is located between the first corner hole (16) and the second corner hole (17).

7. The heat exchanger according to claim 5, characterized in that Along the extension direction of the partition (111), the first corner hole (16), the second corner hole (17), the third corner hole (18) and the fourth corner hole (19) are located on the same side of the plate (1), the third corner hole (18) and the fourth corner hole (19) are located on the inner side of the first corner hole (16) and the second corner hole (17), and a first convex portion (20) protruding from the first plate surface (11) is formed on the peripheral side of the third corner hole (18) and the fourth corner hole (19) of the first plate (2), and the first convex portion (20) is in contact with the first plate surface (11). The edges of the plates (2) are not in contact, the first corner hole (16) and the second corner hole (17) of the second plate (3) are formed with second protrusions (21) protruding from the first plate surface (11), the second protrusions (21) are not in contact with the edges of the second plate (3), the first protrusions (20) are sealedly connected to the second plate surface (12) of the second plate (3), the second protrusions (21) are sealedly connected to the second plate surface (12) of the first plate (2), and the first plate surface (11) of the second plate (3) is provided with a drainage portion (115).

8. The heat exchanger according to any one of claims 2 to 7, characterized in that: Along the first direction, the first inter-plate flow channel (14) has a first flow channel (143) and a second flow channel (144), the first flow channel (143) is located on a side of the first partition (111A) closest to the second corner hole (17) and close to the second corner hole (17), and the second flow channel (144) is located on the other side of the first partition (111A) relative to the first flow channel (143), and the ratio of the width of the second flow channel (144) to the width of the first flow channel (143) is in the range of 1-3.

9. The heat exchanger according to claim 4, characterized in that: The first partition (111A) of the first inter-plate flow channel (14) is at least one, the second partition (111B) of the second inter-plate flow channel (15) is zero, and the protrusions (113) of the second plate (3) are denser than the protrusions (113) of the first plate (2); A first convex portion (20) protruding from the first plate surface (11) is formed around the third corner hole (18) and the fourth corner hole (19) of the first plate (2), and the first convex portion (20) does not contact the edge of the first plate (2); a second convex portion (21) protruding from the first plate surface (11) is formed around the first corner hole (16) and the second corner hole (17) of the second plate (3), and the second convex portion (21) does not contact the edge of the second plate (3); the first convex portion (20) is sealed to the second plate surface (12) of the second plate (3), and the second convex portion (21) is sealed to the second plate surface (12) of the first plate (2); The first corner hole (16), the second corner hole (17) and the fourth corner hole (19) are located on one side of the plate (1), the third corner hole (18) is located on the other side opposite to the plate (1), the fourth corner hole (19) is located between the first corner hole (16) and the second corner hole (17), and the first partition (111A) is located between the second corner hole (17) and the fourth corner hole (19); or, the first corner hole (16), the third corner hole (18) and the second corner hole (17) are located on one side of the plate (1), the third corner hole (18) is located between the first corner hole (16) and the second corner hole (17), the fourth corner hole (19) is located on the other side opposite to the plate (1), and the first partition (111A) is located between the second corner hole (17) and the third corner hole (18).

10. The heat exchanger according to claim 9, characterized in that Along the first direction, the first inter-plate flow channel (14) has a first flow channel (143) and a second flow channel (144), the first flow channel (143) is located on one side of the first partition (111A) close to the second corner hole (17), and the second flow channel (144) is located on the other side of the first partition (111A) relative to the first flow channel (143), and the ratio of the width of the second flow channel (144) to the width of the first flow channel (143) is in the range of 1.2-4.

11. The heat exchanger according to claim 4, characterized in that The first partitions (111A) of the first inter-plate flow channel (14) are two, the second partitions (111B) of the second inter-plate flow channel (15) are one, the first corner hole (16) is located on one side of the plate (1), the second corner hole (17) is located on the other side opposite to the plate (1), and the third corner hole (18) and the fourth corner hole (19) are located on the same side of the plate (1); The second corner hole (17), the third corner hole (18) and the fourth corner hole (19) are located on the same side of the plate (1); along the first direction, the fourth corner hole (19) is located between the second corner hole (17) and the third corner hole (18); one of the first partitions (111A) is located between the third corner hole (18) and the fourth corner hole (19); another of the first partitions (111A) is located between the fourth corner hole (19) and the second corner hole (17); and the second partition (111B) is located between the third corner hole (18) and the fourth corner hole (19). between the four corner holes (19) and the third corner hole (18); or, the first corner hole (16), the third corner hole (18) and the fourth corner hole (19) are located on one side of the plate (1), and along the first direction, the third corner hole (18) is located between the first corner hole (16) and the fourth corner hole (19), the first partition (111A) is located between the fourth corner hole (19) and the third corner hole (18), and the second partition (111B) is located between the fourth corner hole (19) and the third corner hole (18).

12. The heat exchanger according to claim 11, characterized in that Along the first direction, the first inter-plate flow channel (14) comprises a first flow channel (143), a second flow channel (144) and a third flow channel (145); the first flow channel (143), the second flow channel (144) and the third flow channel (145) are separated and formed by two first partitions (111A); the second flow channel (144) is located between the first flow channel (143) and the third flow channel (145); along the first direction, the first flow channel (143) is farther from the first corner hole (16) than the second flow channel (144); Along the first direction, the ratio of the width of the second flow channel (144) to the width of the first flow channel (143) is in the range of 1-3, and / or the ratio of the width of the third flow channel (145) to the width of the second flow channel (144) is in the range of 1-3.

13. The heat exchanger according to claim 4, characterized in that The number of the first partitions (111A) of the first inter-plate flow channel (14) is two, and the number of the second partitions (111B) of the second inter-plate flow channel (15) is zero; Along the extension direction of the partition (111), the first corner hole (16) and the second corner hole (17) are located on different sides of the plate (1), the third corner hole (18) and the fourth corner hole (19) are located on different sides of the plate (1), and along the first direction, the first partition (111A) is located between the first corner hole (16) and the second corner hole (17), and at least one of the first partitions (111A) is located between the third corner hole (18) and the fourth corner hole (19).

14. The heat exchanger according to claim 13, characterized in that Along the first direction, the first inter-plate flow channel (14) comprises a first flow channel (143), a second flow channel (144) and a third flow channel (145); the first flow channel (143), the second flow channel (144) and the third flow channel (145) are separated and formed by two first partitions (111A); the second flow channel (144) is located between the first flow channel (143) and the third flow channel (145); along the first direction, the first flow channel (143) is farther from the first corner hole (16) than the second flow channel (144); Along the first direction, the ratio of the width of the second flow channel (144) to the width of the first flow channel (143) is in the range of 1-3, and / or the ratio of the width of the third flow channel (145) to the width of the second flow channel (144) is in the range of 1-3.

15. The heat exchanger according to claim 13, characterized in that Along the first direction, the ratio of the width of the second flow channel (144) to the width of the first flow channel (143) is 4:3, and the ratio of the width of the third flow channel (145) to the width of the second flow channel (144) is 1.

16. The heat exchanger according to any one of claims 13 to 15, characterized in that: Along the first direction, a first channel (22) is provided between the first partition (111A) and the adjacent protrusions (113), and a second channel (23) is provided between the adjacent protrusions (113), and the width of the first channel (22) is smaller than the width of the second channel (23).

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