Heat exchanger

Abstract

The heat exchanger comprises a first plate and a second plate, the first plate comprises a plurality of first protruding parts and a first base plate, the first protruding parts protrude towards the second plate relative to the first base plate, each first protruding part comprises a first high-position section and a first low-position section, and the first high-position sections and the first low-position sections are arranged in the vertical direction of the first base plate. The first high-position section is closer to the second plate than the first low-position section, the second plate comprises a concave part, the second plate comprises a second base plate, the concave part is concave in the direction away from the first plate relative to the second base plate, and the concave part and the first high-position section are arranged in a staggered mode or partially arranged in a staggered mode in the height direction of the heat exchanger. The existence of the concave part is beneficial to enhancing boiling heat transfer of the refrigerant, the arrangement of the first high-position section and the first low-position section is beneficial to increasing the heat exchange area of the refrigerant, and the common arrangement of the concave part and the first low-position section is beneficial to improving the heat exchange effect of the heat exchanger.

Description

Technical Field

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

[0002] The heat exchanger includes a plurality of plates, a first inter-plate channel is provided between a plate and an adjacent plate, and a second inter-plate channel is provided between a plate and another adjacent plate. The coolant flows in the first inter-plate channel and the refrigerant flows in the second inter-plate channel, and the two exchange heat. How to increase the heat exchange effect is a technical problem. Summary of the invention

[0003] The purpose of the present application is to provide a heat exchanger that is beneficial to improving the heat exchange effect.

[0004] To achieve the above purpose, an implementation of the present application adopts the following technical solution:

[0005] A heat exchanger comprises a first plate and a second plate, wherein a first inter-plate channel is provided between the first plate and the second plate, wherein the first plate comprises a plurality of first protrusions and a first substrate, wherein the first protrusions protrude relative to the first substrate toward the second plate, wherein the first protrusions comprise a first high section and a first low section, wherein along the vertical direction of the first substrate, the first high section is closer to the second plate than the first low section, wherein the second plate comprises a recess, wherein the second plate comprises a second substrate, wherein the recess is recessed relative to the second substrate in a direction away from the first plate, and wherein along the height direction of the heat exchanger, the recess and the first high section are staggered or partially staggered.

[0006] In one embodiment provided in the present application, a heat exchanger includes a first plate and a second plate, the first plate includes a plurality of first protrusions and a first substrate, the first protrusions protrude toward the second plate relative to the first substrate, the first protrusions include a first high section and a first low section, along the vertical direction of the first substrate, the first high section is closer to the second plate than the first low section, the second plate includes a recessed portion, the second plate includes a second substrate, the recessed portion is recessed relative to the second substrate in a direction away from the first plate, along the height direction of the heat exchanger, the recessed portion and the first high section are staggered or partially staggered; the presence of the recessed portion is conducive to enhancing the boiling heat transfer of the refrigerant, the setting of the first high section and the first low section is conducive to increasing the heat exchange area of ​​the refrigerant, and the joint setting of the recessed portion and the first low section is conducive to improving the heat exchange effect of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Figure 1 is a three-dimensional structural schematic diagram of a first embodiment of the heat exchanger provided by the present application from one viewing angle;

[0008] Figure 2 yes Figure 1A three-dimensional structural schematic diagram of a local structure of a heat exchanger from one perspective;

[0009] Figure 3 yes Figure 1 A three-dimensional structural schematic diagram of a local structure of a heat exchanger from another perspective;

[0010] Figure 4 yes Figure 2 A schematic diagram of a top view of a local structure of a heat exchanger;

[0011] Figure 5 yes Figure 4 A schematic cross-sectional view of the local structure of the heat exchanger along AA;

[0012] Figure 6 yes Figure 4 A schematic cross-sectional view of a local structure of the heat exchanger along BB;

[0013] Figure 7 yes Figure 2 A schematic diagram of a three-dimensional structure of the first plate from one viewing angle;

[0014] Figure 8 yes Figure 2 A schematic diagram of the three-dimensional structure of the first plate from another perspective;

[0015] Fig. 9 yes Figure 2 A schematic diagram of the three-dimensional structure of the second plate from one viewing angle;

[0016] Fig.10 yes Figure 2 A schematic diagram of the three-dimensional structure of the second plate from another perspective;

[0017] Fig.11 yes Figure 2 A three-dimensional structural diagram of a partial structure of a local structure from one perspective;

[0018] Fig.12 yes Figure 2 A schematic diagram of a three-dimensional structure of a partial structure of another local structure from one viewing angle;

[0019] Fig.13 yes Figure 2 A schematic diagram of a partial three-dimensional structure of a combined structure of the first plate and the second plate;

[0020] Fig.14 yes Figure 2 A schematic diagram of a partial three-dimensional structure of another combined structure of the first plate and the second plate;

[0021] Fig.15is a three-dimensional structural schematic diagram of another partial structure of the second embodiment of the heat exchanger provided by the present application from one viewing angle;

[0022] Fig.16 is a three-dimensional structural schematic diagram of another local structure of the second embodiment of the heat exchanger provided by the present application from another perspective;

[0023] Fig.17 yes Fig.15 A schematic diagram of a three-dimensional structure of a partial structure of a local structure in another perspective;

[0024] Fig.18 yes Fig.15 A schematic diagram of a three-dimensional structure of the first plate from one viewing angle;

[0025] Fig.19 yes Fig.15 A schematic diagram of the three-dimensional structure of the first plate from another perspective;

[0026] Fig. 20 yes Fig.15 A schematic diagram of the three-dimensional structure of the second plate from one viewing angle;

[0027] Fig.21 yes Fig.15 A schematic diagram of the three-dimensional structure of the second plate from another perspective;

[0028] Fig. 22 is a schematic diagram of the flow field of the first fluid;

[0029] Fig.23 is a schematic diagram of the flow field of the second fluid. DETAILED DESCRIPTION

[0030] The present application is further described below with reference to the accompanying drawings and specific embodiments:

[0031] Combination Figure 1-Figure 14, showing a first embodiment of the heat exchanger 100, the heat exchanger 100 includes a plurality of plates 5, and the plurality of plates 5 are stacked. In this embodiment, a first inter-plate channel s1 is provided between the plate 5 and the plate 5 on the adjacent side, and a second inter-plate channel s2 is provided between the plate 5 and the plate 5 on the adjacent other side. The first inter-plate channel s1 and the second inter-plate channel s2 are alternately provided, and the first inter-plate channel s1 and the second inter-plate channel s2 are not connected. The first inter-plate channel s1 is provided for the flow of the first fluid, and the second inter-plate channel s2 is provided for the flow of the second fluid, and the first fluid and the second fluid perform heat exchange. The first inter-plate channel s1 and the second inter-plate channel s2 are alternately provided, so that the area for heat exchange between the first fluid and the second fluid is large, and the heat exchange effect of the heat exchanger 100 is relatively good. In other embodiments, there may be a first inter-plate channel s1 between the plate 5 and the plate 5 on the adjacent side, and there may also be a first inter-plate channel s1 between the plate 5 and the plate 5 on the adjacent other side, and there may be a second inter-plate channel s2 between the next layer of plates 5, that is, two layers of first inter-plate channels s1 are arranged continuously, and then one layer of second inter-plate channels s2 is arranged, so that heat exchange between the first fluid and the second fluid can be achieved. In other embodiments, two or more layers of second inter-plate channels s2 may be arranged continuously, and then several layers of first inter-plate channels s1 are arranged. In this embodiment, the second fluid refers to the coolant, which is mainly a coolant, such as cooling water or cooling oil. The first fluid in this application refers to the refrigerant, which is mainly a refrigerant, such as R134a, R1234yf, etc. For the convenience of description, the upper and lower directions are defined as those in the attached drawings of the specification. Figure 1 The upper and lower directions of the heat exchanger 100 are defined as the upper and lower directions of the heat exchanger 100, and the upper and lower directions only represent relative positions; the height direction, length direction, and width direction of the heat exchanger 100 are defined as the height direction, length direction, and width direction of the heat exchanger 100 in the attached drawings of the specification. Figure 1 In the height direction, length direction, and width direction of the heat exchanger 100, in this application, the height direction of the heat exchanger 100 is consistent with the stacking direction of the plate 5; in this application, the length direction of the plate 5 is consistent with the length direction of the heat exchanger 100, and the width direction of the plate 5 is consistent with the width direction of the heat exchanger 100. In this application, the directions of the adjacent sides are consistent, the directions of the adjacent sides are consistent, the adjacent side refers to the adjacent side facing upward, and the adjacent other side refers to the adjacent side facing downward; or, the adjacent side refers to the adjacent side facing downward, and the adjacent other side refers to the adjacent side facing upward.

[0032] In this embodiment, the plate 5 includes a first plate 1 and a second plate 2, the first plate 1 and the second plate 2 are alternately stacked, a first inter-plate channel s1 is provided between the first plate 1 and the second plate 2 on one side, a second inter-plate channel s2 is provided between the first plate 1 and the second plate 2 on the other side, and the first inter-plate channel s1 and the second inter-plate channel s2 are alternately provided. In this embodiment, the first plate 1 includes a plurality of first convex portions 11 and a first substrate 35, the first convex portion 11 protrudes toward the second plate 2 relative to the first substrate 35, and the first convex portion 11 has a second groove 122 on the side facing the second plate 2. The first convex portion 11 includes a first high-level segment 12 and a first low-level segment 13, along the vertical direction of the first substrate 35, the first high-level segment 12 is closer to the second plate 2 than the first low-level segment 13, the first high-level segment 12 is closer to the second substrate 36 of the second plate 2 than the first low-level segment 13, and the second groove 122 is located in the first low-level segment 13. The first substrate 35 refers to the first plate 1 before being punched, and the second substrate 36 refers to the second plate 2 before being punched.

[0033] In this embodiment, the second plate 2 includes a plurality of recesses 21, the recesses 21 protrude away from the first plate 1 relative to the first substrate 35 of the second plate 2, the second plate 2 includes the recesses 21, the recesses 21 include the grooves 211, and the recesses 21 have the grooves 211 on the side facing the first plate 1. In this embodiment, the second plate 2 includes the second substrate 36, the recesses 21 are recessed in the direction away from the first plate 1 relative to the second substrate 36, the recesses 21 are recessed in the direction away from the first substrate 35 relative to the second substrate 36, and along the height direction of the heat exchanger 100, the recesses 21 and the first high-level section 12 are staggered, and the staggered setting means that the projections of the first high-level section 12 and the recesses 21 on the plate surface of the first plate 1 do not overlap. The wall forming the first inter-plate channel s1 includes the first low-level section 122 and the second substrate 36, and the wall forming the first inter-plate channel s1 includes the first substrate 35 and the recesses 21. The first plate 1 and the second plate 2 are fixedly connected, the recess 21 and the first substrate 35 are opposite, and the groove 211 forms a part of the first inter-plate channel s1. The existence of the recess is conducive to strengthening the boiling heat transfer of the refrigerant. The setting of the first low-level section 122 is conducive to increasing the heat exchange area of ​​the refrigerant. The joint setting of the recess and the first low-level section 122 is conducive to improving the heat exchange effect of the heat exchanger. In this embodiment, the first plate 1 and the second plate 2 are welded and connected. After the plate exchange 5 is stacked, the whole is placed in a brazing furnace for brazing. The connection method of the first plate 1 and the second plate 2 is simple, and the molding process of the heat exchanger 100 is simple. In other embodiments, the first plate 1 and the second plate 2 can also be bonded. The first substrate 35 is the plane part of the first plate 1, and the second substrate 36 is the plane part of the second plate 2. In other embodiments, the recess 21 and the first high-level section 12 can also be partially staggered. The staggered setting refers to the overlap of the projection part of the first high-level section 12 and the recess 21 on the plate surface of the first plate 1.

[0034] Combination Figure 7-Figure 11 The plate 5 includes a body 3 and a flange 4. The flange 4 is protruded relative to the body 3 and is arranged in the circumferential direction of the body 3. Along the length direction of the plate 5, the plate 5 includes a first end 51 and a second end 52.

[0035] Combination Figure 1-Figure 3 , Figure 7-Figure 12 The heat exchanger 100 includes a first channel 101, a second channel 102, a third channel 103 and a fourth channel 104. The first channel 101 and the third channel 103 are arranged near the first end 51, and the second channel 102 and the fourth channel 104 are arranged near the second end 52. In this embodiment, the plate 5 includes four corner holes 53, two of which are arranged near the first end 51, and the other two of which are arranged near the second end 52. The plates 5 are stacked, and the four corner holes of each plate are aligned along the stacking direction of the plates 5. The four corner holes are aligned along the stacking direction of the plates 5 to form four channels, namely the first channel 101, the second channel 102, the third channel 103 and the fourth channel 104.

[0036] In this embodiment, the first channel 101 is for the refrigerant to flow into the heat exchanger 100, and the second channel 102 is for the refrigerant to flow out of the heat exchanger 100. At the first channel 101 and the second channel 102, the first inter-plate channel S1 is open, and the first channel 101 and the second channel 102 are connected through the first inter-plate channel S1. At the first channel 101 and the second channel 102, the second inter-plate channel S2 is not open, and the first channel 101 and the second channel 102 are not connected to the second inter-plate channel S2. In this embodiment, the third hole 103 is for the coolant to flow into the heat exchanger 100, and the fourth hole 104 is for the coolant to flow out of the heat exchanger 100. At the third hole 103 and the fourth hole 104, the second inter-plate channel S2 is open, and the third hole 103 and the fourth hole 104 are connected through the second inter-plate channel S2. At the third hole 103 and the fourth hole 104, the first inter-plate channel S1 is not open, and the third hole 103 and the fourth hole 104 are not connected to the first inter-plate channel S1. The refrigerant flows in the first inter-plate channel S1, and the coolant flows in the second inter-plate channel S2, and the refrigerant and the coolant exchange heat. In other embodiments, the second hole 102 can also be used to supply the refrigerant to flow into the heat exchanger 100, and the first hole 101 can be used to supply the refrigerant to flow out of the heat exchanger 100. In other embodiments, the fourth hole 104 can also be used to supply the coolant to flow into the heat exchanger 100, and the third hole 103 can be used to supply the coolant to flow out of the heat exchanger 100.

[0037] Combination Figure 2 , Figure 7-Figure 11The first substrate 35 includes a first plate surface 31 and a second plate surface 32, and the first plate surface 31 and the second plate surface 32 are arranged opposite to each other. The first plate sheet 1 includes a plurality of first protrusions 11, and the first protrusions 11 protrude toward the second plate sheet 2 on the adjacent side relative to the first plate surface 31 of the first plate sheet 1, and the first protrusions 11 protrude upward.

[0038] Define the F direction, the angle between the F direction and the length direction of the plate 5 is α, and α is 15° to 75°. In this embodiment, a plurality of first protrusions 11 are arranged along the F direction, and the first protrusions 11 are arranged in multiple rows along the F direction. In this embodiment, a plurality of first protrusions 11 are arranged along the E direction, and the first protrusions 11 are arranged in multiple rows along the E direction.

[0039] Define the E direction, the angle between the E direction and the length direction of the plate 5 is α, and α is 15° to 75°. In this embodiment, the first convex portions 11 are arranged straight along the E direction, and the first convex portions 11 are arranged straight along the E direction. In other embodiments, the first convex portions 11 can also be arranged in a curved manner along the F direction, and the first convex portions 11 can also be arranged in a curved manner along the E direction.

[0040] In this embodiment, there is a first low segment 13 between two adjacent first high segments 12. One end of the first low segment 13 is connected to the first high segment 12, and the other end of the first low segment 13 is connected to the first high segment 12. In this embodiment, along the F direction, two adjacent first convex portions 11 share one first high segment 12.

[0041] Combination Figure 2 , Figure 7-Figure 12 In this embodiment, the first high section 12 is located on the first plate surface 31 of the first plate 1, and the first high section 12 protrudes upward relative to the first plate surface 31 of the first plate 1. The first low section 13 is located on the first plate surface 31 of the first plate 1, and the first low section 13 protrudes upward relative to the first plate surface 31 of the first plate 1. In this embodiment, the minimum height of the first low section 13 from the first plate surface 31 of the first plate 1 is less than the maximum height of the first high section 12 from the first plate surface 31 of the first plate 1. Along the F direction, there is a second groove 122 between two adjacent first high sections 12. Along the E direction, there is a second groove 122 between two adjacent first high sections 12, and the second groove 122 is formed by the first low section 13. In this embodiment, along the F direction, the first high section 12 and the first low section 13 are alternately arranged, and the first high section 12 and the first low section 13 are connected together. The first high section 12 and the first low section 13 are both relatively raised structures. In this way, the raised structures are arranged more densely, which can increase the flow path of the refrigerant, increase the heat exchange area of ​​the refrigerant, and improve the heat exchange effect of the refrigerant and the coolant.

[0042] In other embodiments, one or more groups of two adjacent first high-level segments 12 may not have a first low-level segment 13 between them, and the two adjacent first high-level segments 12 in the group may be connected by a first plate surface 31 , and there may be a gap between the adjacent first high-level segments 12 in the group.

[0043] In other embodiments, along the F direction, there may be two or more first low segments 13 between two adjacent first high segments 12 , and along the E direction, there may be two or more first low segments 13 between two adjacent first high segments 12 .

[0044] In this embodiment, along the height direction of the heat exchanger 100, the minimum height of the first low section 13 from the first plate surface 31 of the first plate 1 is defined as H1, and the maximum height of the first high section 12 from the first plate surface 31 of the first plate 1 is defined as H2, and H1 is less than H2. In this embodiment, the first high section 12 includes a first top 121, and the distance between the first top 121 and the plate surface of the first plate 1 is H2.

[0045] Combination Figure 2 , Figure 7-Figure 12, along the F direction and along the E direction, the first low-level segment 13 includes a trough 131, a first side wall 132 and a second side wall 133, one end of the first side wall 132 is connected to the first top 121 of the adjacent first high-level segment 12, the other end of the first side wall 132 is connected to the trough 131, one end of the second side wall 133 is connected to the trough 131, the other end of the second side wall 133 is connected to the first top 121 of the adjacent first high-level segment 12, and the trough 131 is located between the first side wall 132 and the second side wall 133. In this embodiment, the distance between the trough 131 and the first plate surface 31 of the first plate 1 is H1, and H1 is less than H2. When the first high-level segment 12 is provided on the first plate 1 and the first low-level segment 13 is not provided, when the first high-level segment 12 is provided relatively sparsely, the heat exchange effect between the refrigerant and the coolant is not good, and when the first high-level segment 12 is provided too densely, the first plate 1 is easy to be thinned, and the first plate 1 is difficult to form. In the present application, the first low-level segment 13 is connected to the adjacent first high-level segment 12. The first low-level segment 13 is arranged to be raised relative to the plate surface of the first plate 1. The plate 5 will not be too thin, and the plate 5 is easy to shape. The arrangement of the first low-level segment 13 can make the first high-level segment 12 arranged more densely, increase the flow path of the refrigerant, increase the heat exchange area between the refrigerant and the coolant, and improve the heat exchange effect of the heat exchanger; in addition, along the F direction, there is a second groove 122 between the two adjacent first high-level segments 12, and along the E direction, there is a second groove 122 between the two adjacent first high-level segments 12. The second groove 122 is located in the first low-level segment 13. The first high-level section 12 and the first low-level section 13 have a height difference. The setting of the first low-level section 13 increases the curved surface area of ​​the first plate 1, which can increase the heat exchange area between the refrigerant and the coolant, and improve the heat exchange effect of the heat exchanger 100.

[0046] In this embodiment, along the F direction, the first side wall 132 and the second side wall 133 are symmetrically arranged relative to the trough 131, along the E direction, the first side wall 132 and the second side wall 133 are symmetrically arranged relative to the trough 131, and the two adjacent first high-level sections 12 are symmetrically arranged relative to the trough 131, so that the structure of the first plate 1 is regular, which is convenient for controlling the flow direction of the refrigerant and also convenient for welding the first plate 1 and the second plate 2. In other embodiments, the first side wall 132 and the second side wall 133 can also be asymmetrically arranged relative to the trough 131, and the two adjacent first high-level sections 12 can also be asymmetrically arranged relative to the trough 131.

[0047] Combination Figure 2 , Figure 9-10The second substrate 36 includes a third plate surface 33 and a fourth plate surface 34, and the third plate surface 33 and the fourth plate surface 34 are arranged opposite to each other, and the third plate surface 33 is closer to the second plate surface 32 of the second plate piece 2 on the adjacent side relative to the fourth plate surface 34. In this embodiment, the concave portion 21 of the second plate piece 2 is located on the third plate surface 33, and the concave portion 21 protrudes toward the first plate piece 1 on the adjacent side relative to the third plate surface 33 of the second plate piece 2, and the protruding direction of the concave portion 21 is consistent with the protruding direction of the first high-level section 12. There is a first groove 212 between adjacent concave portions 21, and the concave portion 21 has a groove 211 facing the first plate piece 1 on the other adjacent side.

[0048] In this embodiment, a plurality of recesses 21 are arranged along the F direction, and the recesses 21 are arranged in a plurality of lines along the F direction. Along the F direction, the recesses 21 are arranged in parallel with the first convex portion 11. A plurality of recesses 21 are also arranged along the E direction, and the recesses 21 are arranged in a plurality of lines along the E direction, and the recesses 21 are arranged in parallel with the first convex portion 11 along the E direction. The recesses 21 are arranged in parallel with the first high-level section 12, which facilitates the welding of the first plate 1 and the second plate 2. The height of the recess 21 from the third plate surface of the second plate 2 is equal to the height of the first high-level section 12 from the first plate surface 31 of the first plate 1. In other embodiments, the height of the recess 21 from the third plate surface of the second plate 2 may also be greater than or less than the height of the first high-level section 12 from the first plate surface 31 of the first plate 1.

[0049] In this embodiment, two adjacent plates 5 are welded and fixed, and the first top 121 of the concave portion 21 and the third plate surface 33 of the second plate 2 are welded and fixed. In this embodiment, the concave portion 21 and the first convex portion 11 are arranged in parallel and staggered along the F direction, and the concave portion 21 and the first convex portion 11 are arranged in parallel and staggered along the E direction. Parallel arrangement and staggered arrangement means that along the F direction, the projections of the first high section 12 and the concave portion 21 on the first plate surface 31 do not overlap and are parallel, and along the E direction, the projections of the first high section 12 and the concave portion 21 on the first plate surface 31 do not overlap and are parallel. Along the height direction of the heat exchanger, the concave portion 21 and the first base plate 35 are arranged relative to each other, and the presence of the groove 211 of the concave portion 21 is conducive to strengthening the boiling heat transfer of the refrigerant and improving the heat exchange effect of the refrigerant and the coolant. In this embodiment, the top of the first high section 12 is a plane structure, which is conducive to increasing the welding surface with the second plate 2 on the adjacent side and enhancing the welding strength of the heat exchanger. In other embodiments, the first top 121 can also be an arc structure. In other embodiments, the concave portion 21 and the first convex portion 11 may also be arranged in parallel and partially staggered, and the parallel arrangement and partially staggered arrangement means that along the F direction, the projections of the first high section 12 and the concave portion 21 on the first plate surface 31 overlap and are parallel. In this way, the heat exchanger can also have a better heat exchange effect.

[0050] In other embodiments, part of the recess 21 may be arranged along the F direction. In other embodiments, the recess 21 may not be arranged along the F direction, the recess 21 and the first convex portion 11 are not arranged in parallel, and the recess 21 and the first substrate 35 are partially aligned along the height direction of the heat exchanger. In other embodiments, part of the recess 21 may be arranged along the E direction. In other embodiments, the recess 21 may not be arranged along the E direction, the recess 21 and the first convex portion 11 are not arranged in parallel, and part of the recess 21 and the first substrate 35 are partially aligned along the height direction of the heat exchanger.

[0051] Combination Figure 5-Figure 14 The concave portion 21 has a groove 211 on the second plate 2 facing the other adjacent side. The groove 211 is a part of the refrigerant flow channel. The refrigerant exchanges heat with the coolant. The existence of the groove 211 is beneficial to strengthen the boiling heat transfer of the refrigerant and improve the heat exchange effect of the heat exchanger 100. In addition, when the first plate 1 is only provided with the first high section 121 and the first plate 1 does not have the first low section 13, the first plate 1 and the second plate 2 have similar structures, and the convex structure on the first plate 1 is relatively sparse. In the present application, the first high section 12 and the first low section 13 form a dense convex structure, and the concave portion and the dense convex structure match, which can better improve the heat exchange effect between the refrigerant and the coolant.

[0052] In this embodiment, along the F direction, adjacent first high-level sections 121 have a second groove 122, and along the E direction, two adjacent first high-level sections 121 have a second groove 122. Along the height direction of the heat exchanger, the groove 211 and the first substrate 35 are aligned to form a space S3 (not shown in the figure) between the wall of the groove 211 and the first substrate 35, which is part of the first inter-plate channel S1. Along the E direction and the F direction, there is a second groove 122 between two adjacent first high sections 12, and the second groove 122 is formed by the first low section 13. The height of the recess 21 from the third plate surface 33 is equal to the height of the first high section 12 from the first plate surface 31, and the height of the first low section 13 from the first plate surface 31 is less than the height of the first high section 12 from the first plate surface 31. The height of the first low section 13 is less than the height of the recess 21. A space S4 (not shown in the figure) is formed between the first low section 13 and the second substrate 36, and the width of space S4 is less than the width of space S3. The refrigerant flows from space S4 to space S3, and then to space S4. The width of the refrigerant flow channel changes from narrow to wide and then from wide to narrow, which can further assist the transport of bubbles after the refrigerant "nucleates" and promote boiling enhanced heat exchange. In addition, the setting of the first high-position section 12 increases the area of ​​the first plate 1, and the setting of the recess 21 increases the area of ​​the second plate 2. The first plate 1 and the second plate 2 are used for heat transfer between the refrigerant and the coolant, which increases the heat transfer area of ​​the refrigerant and the coolant, and can further improve the heat exchange of the refrigerant and the coolant.

[0053] In addition, there is a first low section 13 between adjacent first high sections 12, and the first low section 13 protrudes relative to the first plate 1 toward the second plate 2 on the adjacent side, so that the distance between the first low section 13 and the second plate 2 on the adjacent side is small, so that the structure of the heat exchanger 100 is relatively compact; when the first plate 1 does not have the first low section 13, along the F direction, the depth of the second groove 122 between the two adjacent first high sections 12 is the height H2 of the first top 121 of the first high section 12 from the first plate surface 31, and when the first plate 1 has the first low section 13, the depth of the second groove 122 between the two adjacent first high sections 12 is the height H1 of the trough 131 of the first low section 13 from the first plate surface 31, H1 is smaller than H2, and the setting of the first low section 13 makes the flow space width of the refrigerant formed by the alignment of the second groove 122 and the second base plate 36 smaller, so that the refrigerant can have a higher pressure drop, the flow rate of the refrigerant is fast, and it is beneficial to enhance the heat exchange of the refrigerant. The first high-level section 12 and the recess 21 have different structures. The first high-level section 12 of the first plate 1 and the recess 21 of the second plate 2 on the adjacent side have a high degree of asymmetry, which is beneficial to increase the turbulence degree and boiling nucleation state of the refrigerant, thereby achieving high heat exchange performance of the heat exchanger 100.

[0054] In addition, in order to improve the heat exchange effect of the heat exchanger, fins are usually arranged between the plates 5. The flow channels formed by the fins are difficult to clean. In the present application, the first plate 1 and the second plate 2 are stamped structures, and the heat exchanger 100 is easy to clean.

[0055] Combination Figure 2-Figure 3 , Figure 7-Figure 8 In this embodiment, the first plate 1 further includes a third protrusion 37, which protrudes away from the second plate 2 relative to the first plate surface 31 and the first substrate 35, and includes a second high section 17 and a second low section 18.

[0056] The second low section 18 is recessed toward the first plate 1 relative to the second substrate 36 . Along the vertical direction with the second substrate 36 , the second high section 17 is closer to the second plate 2 than the first low section 13 . The second high section 17 includes a second top 171 , and the second top 171 is flush with the second plate surface 32 .

[0057] In this embodiment, the second high segment 17 and the second low segment 18 are arranged along the F direction, and the second high segment 17 and the second low segment 18 are arranged along the E direction. In this embodiment, along the F direction, there is a second low segment 18 between two adjacent second low segments 18, one end of the second low segment 18 is connected to an adjacent second high segment 17, and the other end of the second low segment 18 is connected to another adjacent second high segment 17. In this embodiment, along the E direction, there is a second low segment 18 between two adjacent second low segments 18, one end of the second low segment 18 is connected to an adjacent second high segment 17, and the other end of the second low segment 18 is connected to another adjacent second high segment 17, and there is a second groove 122 between adjacent second high segments 17, and the second groove 122 is located in the second low segment 18. In this embodiment, the structure of the second high segment 17 is substantially the same as that of the first high segment 12, and the structure of the second low segment 18 is substantially the same as that of the first low segment 13. Substantially the same includes identical and similar, and substantially the same refers to substantially identical size and shape. In other embodiments, the structure of the second high segment 17 may be different from that of the first high segment 12. In other embodiments, part of the second high segment 17 and the second low segment 18 may be arranged along the F direction, and part of the second high segment 17 and the second low segment 18 may be arranged along the E direction.

[0058] The first plate 1 and the second plate 2 are fixedly connected, and a second inter-plate channel s2 is provided between the first plate 1 and the second plate 2 on the other adjacent side. In this embodiment, the second high-level section 17 of the first plate 1 and the recess 21 of the second plate 2 on the other adjacent side are welded and fixed. In this embodiment, the second high-level section 17 includes a second top 171, and the recess 21 includes a third top 213, and the second top 171 and the third top 213 are in contact and welded. In this embodiment, the third top 213 is a planar structure, and the second top 171 is also a planar structure, which is conducive to increasing the welding surface of the third top 213 and the second top 171, and enhancing the welding strength of the heat exchanger. In other embodiments, the third top 213 can also be an arc-shaped structure, and the second top 171 can also be an arc-shaped structure, etc.

[0059] There is a first groove 212 between adjacent recesses 21, and there is a third groove 172 between adjacent second high-level sections 17. The third groove 172 is located in the second low-level section 18. Along the height direction of the heat exchanger, part of the first groove 212 and the first substrate 35 are arranged opposite to each other, forming a part of the second inter-plate channel s2 between the wall of the first groove 212 and the first substrate 35. Part of the first groove 212 and the third groove 172 are arranged in alignment, and part of the first groove 212 and the third groove 172 are aligned to form a part of the second inter-plate channel s2. The depth of the first groove 212 is consistent with the height of the recess 21. The space formed by the first groove 212 and the third groove 172 is relatively large, which provides a larger flow space for the flow of the coolant, so that the coolant has a lower pressure drop and a lower flow rate of the coolant, which can improve the heat exchange effect of the coolant and the refrigerant. The second high-level section 17 and the second low-level section 18 form a dense convex structure, which increases the heat exchange area of ​​the coolant and can further improve the heat exchange effect of the coolant and the refrigerant. In other embodiments, the second high section 17 and the recessed portion 21 may also be fixed by bonding.

[0060] Combination Figure 7-Figure 10 , α is the first distribution angle of the first high section 12, α is also the first distribution angle of the first low section 13, and α can be 15°~75°. In this embodiment, α is 20°~35°, including 20°~35. When α is other values, 20°~35, the first high section 12 can be arranged relatively densely, which is beneficial to improve the heat exchange efficiency of the refrigerant and the coolant. In this embodiment, the first distribution angle of the second high section 17 is consistent with the first distribution angle of the first high section 12, and the distribution angle of the second low section 18 is also consistent with the first distribution angle of the first low section 13, which is beneficial to improve the density of the protruding structure, increase the heat exchange area of ​​the coolant, increase the heat exchange area of ​​the coolant and the refrigerant, and improve the heat exchange effect of the heat exchanger 100. In other embodiments, the first distribution angle of the second high section 17 and the first distribution angle of the first high section 12 may also be inconsistent, and the first distribution angle of the second low section 18 and the first distribution angle of the first low section 13 may also be inconsistent.

[0061] In this embodiment, the angle between the E direction and the length direction of the plate 5 is β, β is the second distribution angle of the first high section 12, β is also the second distribution angle of the first low section 13, and β can be 15° to 75°. In this embodiment, β is 20° to 35°, including 20° to 35, so that the protruding structure can be arranged relatively densely, which is conducive to improving the heat exchange efficiency of the refrigerant and the coolant. In this embodiment, β and α are the same, which is conducive to the matching of the first plate 1 and the second plate 2. In other embodiments, β and α may also be different. In this embodiment, the second distribution angle of the second high section 17 is consistent with the second distribution angle of the first high section 12, and the distribution angle of the second low section 18 is also consistent with the second distribution angle of the first low section 13, which is conducive to increasing the density of the protruding structure, increasing the heat exchange area of ​​the coolant, increasing the heat exchange area of ​​the coolant and the refrigerant, and improving the heat exchange effect of the heat exchanger 100.

[0062] Combination Figure 4 , Figure 7-Figure 10 , the recesses 21 are arranged in a line along the F direction, and the first distribution angle of the recesses 21 is also α, α is 20° to 35°, including 20° to 35, and the recesses 21 can be arranged relatively densely, which is conducive to increasing the density of the recesses 21, increasing the boiling heat transfer effect of the refrigerant, improving the heat exchange efficiency of the refrigerant and the coolant, and improving the heat exchange effect of the heat exchanger 100. The recesses 21 are also arranged in a line along the E direction, and the first distribution angle of the recesses 21 is also β, β is 20° to 35°, including 20° to 35, and the recesses 21 can be arranged relatively densely, which is conducive to increasing the density of the recesses 21, increasing the boiling heat transfer effect of the refrigerant, improving the heat exchange efficiency of the refrigerant and the coolant, and improving the heat exchange effect of the heat exchanger 100.

[0063] Combination Figure 4 , Figure 7-Figure 10In this embodiment, along the width direction of the plate 5, the distance between two adjacent first high sections 12 is d1, d1 is the distance between the center points of the two adjacent first high sections 12, and d1 is the distance between the two adjacent first high sections 12 in the width direction. The ratio of the distance in the width direction between adjacent first high sections 12 and the maximum height of the first high section 12 from the plate surface of the first plate 1 can be 1.5-7, that is, the ratio between d1 and H2 is 1.5-7. In this embodiment, the ratio of the distance in the width direction between adjacent first high sections 12 and the maximum height of the first high section 12 from the plate surface of the first plate 1 is 2.5-5.5, that is, the ratio between d1 and H2 is 2.5-5.5. The higher the height of the first high section 12, the sparser the first high section 12 should be, otherwise the high and dense first high section 12 will cause a large thinning rate at the top of the first high section 12, so that the plate 5 is not easy to form, and the first high section 12 is too sparse to increase the turbulence of the refrigerant and enhance the heat exchange. When the ratio between d1 and H2 is 2.5-5.5, the first high-level segment 12 can be arranged relatively densely, which is beneficial to increasing the turbulent effect of the first high-level segment 12 on the refrigerant, and the thinning rate of the first plate 1 will not be too low, so that the second plate 2 is easy to form.

[0064] In this embodiment, along the width direction of the plate 5, the ratio of the width direction distance between adjacent second high sections 17 to the height of the second high section 17 is also 2.5-5.5, so that the second high section 17 can be arranged relatively densely, which is conducive to increasing the turbulent effect of the second high section 17 on the coolant, and the second plate 2 is also easy to form. In this embodiment, the ratio of the width direction distance between adjacent second high sections 17 to the height of the second high section 17 is the same as the ratio between d1 and H2, so that the first plate 1 and the second plate 2 are easy to form, and the flow rates of the refrigerant and the coolant are adapted, which is conducive to improving the heat exchange efficiency of the coolant and the refrigerant. In other embodiments, the ratio of the width direction distance between adjacent second high sections 17 to the maximum height of the second high section 17 can also be 1.5-2.5 or 5.5-7.

[0065] In this embodiment, along the width direction of the plate 5, the distance between adjacent recesses 21 is d2, and d2 is the distance between the center points of adjacent recesses 21. In this embodiment, d2 is the distance between the third tops 213 of adjacent recesses 21, d2 is the distance between adjacent recesses 21 in the width direction, and the distance between the third top 213 of the recess 21 and the plate surface of the first plate 1 is H3. In this embodiment, the ratio of d2 to H3 is also 2.5 to 5.5, so that the recesses 21 can be arranged more densely, and the second plate 2 is also easy to shape; in addition, the recesses 21 can be arranged more densely, which is conducive to improving the boiling heat transfer on the refrigerant side, and is also conducive to increasing the flow path of the coolant, and improving the heat exchange effect of the heat exchanger 100. In this embodiment, the ratio of d2 and H3 is the same as the ratio of d1 and H2, so that the structures of the first plate 1 and the second plate 2 can be more coordinated, and the refrigerant side can have a suitable flow space, the refrigerant has a suitable pressure drop, and the refrigerant has a higher flow rate; this can also allow the coolant to have a suitable flow space and pressure drop, the coolant has a lower flow rate, and the pressure drops on the coolant side and the refrigerant side are relatively suitable, which is beneficial to improving the heat exchange efficiency of the coolant and the refrigerant.

[0066] In another embodiment, along the F direction, there is no second low section 18 between the second high sections 17, the second high sections 17 are convexly arranged downward relative to the second base plate 36 of the second plate 2, and a third groove 172 is provided between two adjacent second high sections 17. The second top 171 of the second high section 17 and the third top 213 of the concave portion 21 are in contact and fixed by welding, so that the boiling heat transfer of the refrigerant can be enhanced and better heat exchange between the refrigerant and the coolant can be achieved.

[0067] Figure 15-Figure 23 In the second embodiment of the heat exchanger, both the first plate 1 and the second plate 2 are provided with ribs, and the refrigerant and the coolant flow in a U-shaped loop. In this embodiment, the first plate 1 includes a first rib 14, the first rib 14 is located on the body 3, the first rib 14 is located on the first plate surface 31 of the first plate 1, the first rib 14 is protruded toward the second plate 2 on the adjacent side relative to the first plate surface 31 of the first plate 1, and the first rib 14 has a first groove 141 toward the third plate surface 33 of the second plate 2 on the adjacent other side. The first rib 14 is arranged along the length direction of the first plate 1, one end of the first rib 14 is connected to the flange 4 near the first end 51, the other end of the first rib 14 is not connected to the flange 4 near the second end 52, and there is a gap between the other end of the first rib 14 and the flange 4 near the second end 52 for the flow of the refrigerant. In this embodiment, along the width direction of the plate 5 , the first plate 1 includes a first side 15 and a second side 16 , the first rib 14 is located between the first side 15 and the second side 16 , and the first side 15 and the second side 16 are located on the first plate surface 31 .

[0068] In this embodiment, the first channel 101 is the inflow channel of the refrigerant, and the second channel 102 is the outflow channel of the refrigerant. The refrigerant flows into the heat exchanger 100 from the first channel 101, first flows on the first side 15 of the plate 5, then flows around the first rib 14 to the second side 16 of the plate 5, and flows out of the heat exchanger 100 from the second channel 102. The refrigerant flows around the first rib 14 in a U-shaped line. The first rib 14 is provided so that the refrigerant flows around the first rib 14 in a U-shaped loop, so that the refrigerant has two flow sections, which can increase the flow path of the refrigerant, increase the heat exchange area between the refrigerant and the coolant, and improve the effect of the heat exchanger 100. In addition, the first rib 14 is provided so that the first channel 101 and the second channel 102 are located on the same side of the width of the heat exchanger 100, which is convenient for the heat exchanger 100 to cooperate with other components, such as the expansion valve.

[0069] Combination Figure 15-17 In this embodiment, along the width direction of the plate 5, the width of the first side 15 is smaller than the width of the second side 16. In this embodiment, the first side 15 is close to the inlet channel of the refrigerant, and the first side 15 is the first flow section of the refrigerant. The second side 16 is close to the outlet channel of the refrigerant, and the second side 16 is the second flow section of the refrigerant. When the refrigerant enters the heat exchanger 100, the dryness is low, and the heat exchange effect between the refrigerant and the coolant is good. After the refrigerant works for a period of time, the temperature of the refrigerant increases, and the dryness of the refrigerant becomes higher. The wider flow channel of the second side 16 is conducive to the flow of the refrigerant, controls the refrigerant to have a higher pressure drop, and reduces the heat exchange performance degradation caused by the enthalpy loss of the refrigerant. In other embodiments, the width of the first side 15 can also be equal to or greater than the width of the second side 16.

[0070] Combination Fig.18 and Fig.19 In this embodiment, the second plate 2 includes a second rib 22, the second rib 22 is located on the body 3, the second rib 22 is located on the third plate surface 33 of the second plate 2, the second rib 22 is protruded relative to the plate surface of the second plate 2 toward the first plate 1 on one side adjacent to the plate surface, and the second rib 22 has a second groove 221 toward the first plate surface 31 of the first plate 1 on the other side adjacent to the plate 5. The second rib 22 is arranged along the length direction of the plate 5, one end of the second rib 22 is connected to the flange 4 near the second end 52, the other end of the second rib 22 is not connected to the flange 4 near the first end 51, and there is a gap between the other end of the second rib 22 and the flange 4 near the first end 51 for the flow of coolant. The second plate 2 includes a third side 23 and a fourth side 24, the third side 23 and the fourth side 24 are located on the third plate surface 33, and the second rib 22 is located between the third side 23 and the fourth side 24.

[0071] Combination Figure 17-Figure 23In this embodiment, the third channel 103 is the inflow channel of the coolant, and the fourth channel 104 is the outflow channel of the coolant. The coolant flows into the heat exchanger 100 from the third channel 103, first flows on the first side 15 of the second plate 2, then flows around the second rib 22 to the second side 16 of the second plate 2, and flows out of the heat exchanger 100 from the fourth channel 104. The coolant flows around the second rib 22 in a U-shaped line. The setting of the second rib 22 can make the coolant have two flow sections, which can increase the flow path of the coolant and improve the heat exchange effect of the coolant and the refrigerant. In addition, the setting of the second rib 22 makes the third channel 103 and the fourth channel 104 located on the same side of the width of the heat exchanger 100, which is convenient for the heat exchanger 100 to cooperate with other components.

[0072] In this embodiment, along the length direction of the heat exchanger 100, the first channel 101 and the third channel 103 are located on the same side of the heat exchanger 100, and the second channel 102 and the fourth channel 104 are located on the same side of the heat exchanger 100, so that the flow directions of the refrigerant and the coolant are opposite, and the refrigerant and the coolant are countercurrent, which is conducive to improving the heat exchange effect of the two. In other embodiments, along the length direction of the heat exchanger 100, the first channel 101 and the fourth channel 104 can also be located on the same side of the heat exchanger 100, and the second channel 102 and the third channel 103 can be located on the same side of the heat exchanger 100, so that the heat exchange of the refrigerant and the coolant can also be achieved.

[0073] In this embodiment, along the width direction of the plate 5, the width of the third side 23 is equal to the width of the fourth side 24, so that the coolant can have a suitable pressure drop and a suitable flow rate, and the coolant can effectively exchange heat with the refrigerant.

[0074] Along the width direction of the plate 5, the first rib 14 is offset, the second rib 22 is centered, the first plate 1 and the second plate 2 are welded and fixed, the top of the first rib 14 and the fourth plate surface 34 of the second plate 2 on the adjacent side are welded and fixed, and the top of the second rib 22 and the second plate surface 32 of the first plate 1 on the adjacent side are welded and fixed. Along the width direction of the heat exchanger, the first rib 14 is close to the third side 23 of the second plate 2, the second rib 22 is close to the second side 16 of the first plate 1, and the second groove 221 is close to the second flow section of the refrigerant. The dryness of the refrigerant in the second flow section is high, and the heat exchange effect of the refrigerant is poor. The second groove 221 is part of the refrigerant flow channel, and the flow of the refrigerant in the second groove 221 is blocked. Placing the second groove 221 close to the second flow section of the refrigerant is conducive to reducing the influence of the second groove 221 on the heat exchange effect of the refrigerant. In this embodiment, the first rib 14 and the second rib 22 have the same height. Along the height direction of the heat exchanger, the first side wall 144 of the first rib 14 and the second side wall 224 of the second rib 22 are aligned, which is conducive to reducing the gap between the first rib 14 and the second rib 22, reducing the refrigerant flowing into the gap between the first rib 14 and the second rib 22, and improving the heat exchange effect of the heat exchanger 100. In addition, the gap between the first rib 14 and the second rib 22 is located in the second flow section of the refrigerant, which is conducive to preventing the pressure drop of the refrigerant from being low. In other embodiments, the width of the third side 23 and the width of the fourth side 24 may also be different.

[0075] When the height of the first high-position section 12 is different from the height of the recess 21, the height H2 of the first top 121 from the plate surface of the plate 5 is less than the height H3 of the third top 213 from the plate surface of the plate 5, the height of the second rib 22 is less than the height of the first rib 14, the depth of the first groove 141 of the second rib 22 toward the adjacent first plate 1 on the other side is less than the depth of the second groove 221 of the second rib 22 toward the adjacent second plate 2 on the other side, and the depth of the first groove 141 corresponding to the refrigerant side is less than the depth of the second groove 221 corresponding to the coolant side, which is conducive to reducing the flow space on the refrigerant side, increasing the flow space on the coolant side, making the refrigerant have a higher pressure drop, reducing the pressure drop of the coolant, and making the heat exchange efficiency between the coolant and the refrigerant better. In other embodiments, the height of the second rib 22 may also be greater than the height of the first rib 14, and the depth of the first groove 141 corresponding to the refrigerant side is greater than the depth of the second groove 221 corresponding to the coolant side. In other embodiments, H2 may also be greater than H3.

[0076] Combination Figure 18-Figure 21In this embodiment, the first rib 14 is in a Z-shaped wave shape, and the first rib 14 includes a first portion 142 and a second portion 143, which are alternately arranged along the length direction of the first rib 14, and adjacent first portions 142 and second portions 143 are connected. In this embodiment, the first portion 142 extends in a direction parallel to the F direction, and the extension direction of the second portion 143 extends in a direction parallel to the E direction. This arrangement can make the shape of the first rib 14 consistent with the flow direction of the refrigerant, avoid the first rib 14 from hindering the flow of the refrigerant, make the refrigerant flow more smoothly, and make the refrigerant and the coolant have a higher heat exchange effect. In this embodiment, the second rib 22 is also in a Z-shaped wave shape, and the second rib 22 includes a third portion 222 and a fourth portion 223. The third portion 222 extends in a direction parallel to the F direction, and the fourth portion 223 extends in a direction parallel to the E direction. This arrangement can make the shape of the second rib 22 consistent with the flow direction of the coolant, avoid the second rib 22 blocking the flow of the coolant, make the coolant flow more smoothly, and improve the heat exchange effect between the coolant and the refrigerant. In other embodiments, the first rib 14 can also be in a curved wave shape, and the second rib 22 can also be in a curved wave shape.

[0077] Combination Figure 18-19 , the first high section 12 is arranged close to the first rib 14, and the outer diameter of the first high section 12 close to the first rib 14 is greater than the outer diameter of the first high section 12 away from the first rib 14. In this embodiment, the second plate 2 includes an A zone and a B zone, and the B zone has two, the A zone is located between the two B zones, the first rib 14 is located in the A zone, and the B zone is far away from the first rib 14 relative to the A zone. In this embodiment, the first high section 12 in the A zone is arranged close to the first rib 14, which can reduce the gap between the first high section 12 and the first rib 14, reduce the amount of refrigerant flowing into the gap, thereby reducing the bypass of the refrigerant and improving the heat exchange effect of the heat exchanger 100. In this embodiment, the outer diameter of the first high section 12 in the A zone is greater than the outer diameter of the first high section 12 in the B zone, which can also reduce the gap between the first high section 12 and the first rib 14, reduce the bypass of the refrigerant, and improve the heat exchange effect of the heat exchanger 100. In other embodiments, the outer diameter of the first high section 12 in the A zone may also be equal to or smaller than the outer diameter of the first high section 12 in the B zone.

[0078] In this embodiment, the second high section 17 of the A zone is arranged close to the first rib 14, so that the gap between the second high section 17 and the first rib 14 can be reduced, the bypass of the coolant can be reduced, and the heat exchange effect of the heat exchanger 100 can be improved. Along the length direction of the plate 5, the outer diameter of the second high section 17 of the A zone is greater than the outer diameter of the second high section 17 of the B zone, so that the gap between the second high section 17 and the first rib 14 can be reduced, the bypass of the coolant can be reduced, the heat exchange between the coolant and the refrigerant can be improved, and the heat exchange effect of the heat exchanger 100 can be improved. In other embodiments, the outer diameter of the second high section 17 of the A zone can also be equal to or less than the outer diameter of the second high section 17 of the B zone.

[0079] It should be noted that: It should be noted that: the above embodiments are only used to illustrate the present application and are not intended to limit the technical solutions described in the present application. Although this specification has described the present application in detail with reference to the above embodiments, ordinary technicians in the field should understand that technicians in the relevant technical field can still modify or replace the application with equivalents, and all technical solutions and improvements that do not depart from the spirit and scope of the present application should be included in the scope of the claims of the present application.

Claims

1. A heat exchanger (100), characterized in that: The heat exchanger (100) comprises a first plate (1) and a second plate (2), wherein a first inter-plate channel (s1) is provided between the first plate (1) and the second plate (2), wherein the first plate (1) comprises a plurality of first protrusions (11) and a first substrate (35), wherein the first protrusions (11) protrude relative to the first substrate (35) toward the second plate (2), wherein the first protrusions (11) comprise a first high section (12) and a first low section (13), wherein along the vertical direction of the first substrate (35), the first high section (12) is closer to the second plate (2) than the first low section (13), wherein the second plate (2) comprises a recess (211), wherein the second plate (2) comprises a second substrate (36), wherein the recess (211) is recessed relative to the second substrate (36) in a direction away from the first plate (1), and wherein along the height direction of the heat exchanger (100), the recess (211) and the first high section (12) are staggered or partially staggered.

2. The heat exchanger (100) according to claim 1, characterized in that: A direction F is defined, wherein the angle between the direction F and the first direction of the plate (5) is α, and α is 15° to 75°; A plurality of the first convex portions (11) are arranged along the F direction, the concave portion (211) and the first convex portion (11) are arranged in parallel and staggered, or the concave portion (21) and the first convex portion (11) are arranged in parallel and partially staggered along the F direction.

3. The heat exchanger (100) according to claim 1 or 2, characterized in that: An E direction is defined, wherein an angle β between the E direction and the length direction of the plate (5) is 15° to 75°. The first convex portion (11) is arranged along the E direction, the concave portion (21) includes the concave portion (211), a plurality of the concave portions (21) are arranged along the E direction, the concave portion (21) and the first convex portion (11) are arranged in parallel and staggered, or the concave portion (21) and the first convex portion (11) are arranged in parallel and partially staggered.

4. The heat exchanger (100) according to claim 3, characterized in that: The α is 20° to 35°, and the β is 20° to 35°.

5. The heat exchanger (100) according to claim 4, characterized in that: The first substrate (35) comprises a first plate surface (31), the minimum height of the first low section (13) from the first plate surface (31) is smaller than the maximum height of the first high section (12) from the first plate surface (31), and the first high section (12) and the second substrate (36) are fixedly connected.

6. The heat exchanger (100) according to claim 5, characterized in that: Along the F direction, the wall forming the first inter-plate channel (s1) includes the first low-level section (122) and the second base plate (36), the wall forming the first inter-plate channel (s1) includes the first base plate (35) and the recess (211), the projections of the first high-level section (12) and the recess (21) on the first plate surface (31) do not overlap and are parallel; and / or, along the E direction, the projections of the first high-level section (12) and the recess (21) on the first plate surface (31) do not overlap and are parallel.

7. The heat exchanger (100) according to claim 5, characterized in that: Along the F direction, the projections of the first high section (12) and the recess (21) on the first plate surface (31) overlap and are parallel; and / or, along the E direction, the projections of the first high section (12) and the recess (21) on the first substrate (35) overlap and are parallel.

8. The heat exchanger (100) according to any one of claims 1 to 7, characterized in that: The first substrate (35) comprises a second plate surface (32), the second plate surface (32) and the first plate surface (31) are arranged opposite to each other, the first plate piece (1) comprises a third protrusion (37), the third protrusion (37) protrudes away from the second plate piece (2) relative to the first plate surface (31), the third protrusion (37) comprises a second high section (17) and a second low section (18), the second low section (18) is recessed toward the first plate piece (1) relative to the second substrate (36), and along a direction perpendicular to the second substrate (36), the second high section (17) is closer to the first plate piece (17) than the first low section (13). Near the second plate (2), the second high section (17) includes a second top (171), the second top (171) and the second plate surface (32) are flush, the heat exchanger (100) includes a second inter-plate channel (s2), the heat exchanger (100) also includes one of the first plates (1), a second inter-plate channel (s2) is provided between the first plate (1) and the second plate (2), a first groove (212) is provided between adjacent recesses (21), and a wall forming the second inter-plate channel (s2) includes a first base plate (35) and a wall forming the first groove (212).

9. The heat exchanger (100) according to claim 8, characterized in that: A plurality of the third convex portions (37) are arranged along the F direction, and the second high-position section (17) and the first convex portion (11) are arranged in parallel and staggered; and / or a plurality of the third convex portions (37) are arranged along the E direction, and the second high-position section (17) and the first convex portion (11) are arranged in parallel and staggered.

10. The heat exchanger (100) according to claim 1 or 9, characterized in that: The first plate (1) comprises a first rib (14), the first rib (14) extending along the length direction of the first plate (1), the first rib (14) protruding relative to the first substrate (35) toward the second plate (2), the protruding direction of the first rib (14) being consistent with that of the first protrusion (11), one end of the first rib (14) being connected to one end of the first plate (1), the other end of the first rib (14) being not connected to the other end of the first plate (1), and the first rib (14) dividing the first plate (1) into two parts; And / or, the second plate (2) comprises a second rib (22), the second rib (22) extends along the length direction of the second plate (2), the second rib (22) protrudes toward the first plate (1) relative to the second substrate (36), the protruding direction of the second rib (22) is consistent with the first protrusion (11), one end of the second rib (22) is connected to one end of the second plate (2), the other end of the second rib (22) is not connected to the other end of the second plate (2), and the second rib (22) divides the second plate (2) into two parts.

11. The heat exchanger (100) according to claim 10, characterized in that: The first rib (14) includes a first portion (142) and a second portion (143), the first portion (142) and the second portion (143) are alternately arranged, the first portion (142) extends along the F direction, and the second portion (143) extends along the E direction; and / or the second rib (22) includes a third portion (222) and a fourth portion (223), the third portion (222) and the fourth portion (223) are alternately arranged, the third portion (222) extends along the F direction, and the fourth portion (223) extends along the E direction.

12. The heat exchanger (100) according to claim 1, 2 or 11, characterized in that: Along the width direction of the plate (5), the distance between the center points of two adjacent first high-level sections (12) is d1, and the ratio of d1 to the height H2 of the first high-level section (12) from the first plate surface (31) of the first plate (1) is 2.5 to 5.5; And / or, the second substrate (36) includes a third plate surface (33), the distance between the center points of adjacent recesses (21) is d2, and the ratio of d2 to the height of the recess (21) from the third plate surface (33) of the second plate (2) is 2.5 to 5.

5.

13. The heat exchanger (100) according to claim 12, characterized in that: The outer diameter of the first high section (12) close to the first rib (14) is greater than or equal to the outer diameter of the first high section (12) away from the first rib (14).

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