Heat exchanger

Abstract

The heat exchanger comprises a first plate, the first plate comprises a first base plate and a plurality of first high-position sections, the distance between the center points of every two adjacent first high-position sections is d1, the first top distance of each first high-position section and the height of the first base plate are H2, and the ratio of d1 to H2 is 1.5-6, so that the first high-position sections can be densely arranged, and the heat exchange efficiency is improved. And the heat exchange effect can be improved.

Description

[0001] This application is a divisional application of application number 202311088493.4, and the invention name is: "A plate and a heat exchanger". Technical Field

[0002] The present application relates to the field of heat exchange technology, and in particular to a heat exchanger. Background Art

[0003] The heat exchanger includes a plurality of plates, and the heat exchanger has a first inter-plate channel and a second inter-plate channel. A first fluid, such as a refrigerant, flows in the first inter-plate channel, and a second fluid, such as a coolant, flows in the second inter-plate channel, and the two perform heat exchange. In order to increase the heat exchange effect, the plates are provided with protrusions, and the protrusions are provided too sparsely, which affects the heat exchange effect. Therefore, how to set the protrusions to improve the heat exchange effect is a technical problem that needs to be solved. Summary of the invention

[0004] The purpose of the present application is to provide a heat exchanger that is beneficial to improving the heat exchange effect.

[0005] To achieve the above purpose, an implementation method of the present application adopts the following technical solution:

[0006] A heat exchanger includes a first plate, wherein the first plate includes a first substrate and a plurality of first high segments, wherein the first high segments are protruded relative to the first substrate, and the normal of one side of the first plate is defined as the F2 direction. Along the F2 direction, the distance between the center points of two adjacent first high segments is d1, and the distance between the first top of the first high segment and the height of the first substrate is H2, and the ratio of d1 to H2 is 1.5 to 6.

[0007] In one embodiment provided in the present application, a heat exchanger includes a first plate, the first plate includes a first substrate and a plurality of first high segments, along the F2 direction, the distance between the center points of two adjacent first high segments is d1, the distance between the first top of the first high segment and the height of the first substrate is H2, and the ratio of d1 to H2 is 1.5 to 6; the setting of the first high segment will thin the first plate, and d1 / H2 is controlled at 1.5 to 6. Under the condition of ensuring that the first plate is easy to form, the first high segment can also be arranged relatively densely, which is conducive to increasing the heat exchange area and improving the heat exchange effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a three-dimensional structural schematic diagram of a heat exchanger provided by the present application from one perspective;

[0009] Figure 2 is a three-dimensional structural schematic diagram of the heat exchanger provided by the present application from another perspective;

[0010] Figure 3 yes Figure 1 A structural schematic diagram of a local structure of a heat exchanger from one perspective;

[0011] Figure 4 yes Figure 3 A schematic cross-sectional structure diagram of a local structure of the heat exchanger along A7-A7;

[0012] Figure 5 yes Figure 3 An exploded structural diagram of a local structure of a heat exchanger;

[0013] Figure 6 yes Figure 5 A schematic diagram of a three-dimensional structure of the first plate from one viewing angle;

[0014] Figure 7 yes Figure 5 A schematic diagram of the three-dimensional structure of the first plate from another perspective;

[0015] Figure 8 yes Figure 7 A schematic diagram of the enlarged structure of the middle part A;

[0016] Fig. 9 yes Figure 3 A schematic diagram of the three-dimensional structure of the second plate from one viewing angle;

[0017] Fig.10 yes Figure 3 A schematic diagram of the three-dimensional structure of the second plate from another perspective;

[0018] Fig.11 yes Fig.10 A schematic diagram of the enlarged structure of the middle B part;

[0019] Fig.12 yes Figure 3 Another partial structural schematic diagram of the heat exchanger;

[0020] Fig.13 yes Fig.12 A schematic cross-sectional view of another local structure of the middle heat exchanger along A6-A6;

[0021] Fig.14 is a structural schematic diagram of a combined structure of a first rib portion and a second rib portion;

[0022] Fig.15 yes Fig.10 A schematic structural diagram of a partial structure of a second plate of a heat exchanger;

[0023] Fig.16 yes Fig.15 A schematic cross-sectional view of the partial structure of the second plate of the middle heat exchanger along the A1-A1 plane;

[0024] Fig.17 yes Figure 7 A schematic structural diagram of a local structure of the first plate;

[0025] Fig.18 yes Fig.17 A schematic cross-sectional view of the local structure of the first plate along the BB plane;

[0026] Fig.19 yes Fig.17 Schematic diagram of the cross-sectional structure of the local structure of the first plate along the CC plane. DETAILED DESCRIPTION

[0027] The present application is further described below with reference to the accompanying drawings and specific embodiments:

[0028] Combination Figure 1-Figure 19 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 one side, and a second inter-plate channel s2 is provided between the plate 5 and the plate 5 on the 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 are heat exchanged. 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 up and down directions of the heat exchanger 100 are defined as the height direction, F1 direction, and F2 direction of the heat exchanger 100 as shown in the attached drawings of the specification. Figure 1In the height direction, F1 direction, and F2 direction of the heat exchanger 100, in the present application, the height direction of the heat exchanger 100 is consistent with the stacking direction of the plate 5; in the present application, the F1 direction of the plate 5 is consistent with the F1 direction of the heat exchanger 100, and the F2 direction of the plate 5 is consistent with the F2 direction of the heat exchanger 100. In the present 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.

[0029] 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 high-level sections 12 and a first substrate 35, the first high-level section 12 protrudes toward the second plate 2 relative to the first substrate 35. The first substrate 35 refers to the first plate 1 before being stamped, and the second substrate 36 refers to the second plate 2 before being stamped.

[0030] In this embodiment, the first plate 1 includes a first substrate 35 and a plurality of first high-level segments 12. The first high-level segments 12 are arranged to be raised relative to the first substrate 35. The normal direction of one side of the first plate 1 is defined as the F2 direction. The distance between the center points of two adjacent first high-level segments 12 is d1. The distance between the first top 121 of the first high-level segment 12 and the height of the first substrate 35 is H2. The ratio of d1 to H2 is 1.5 to 6. The setting of the first high-level segment 12 will thin the first plate 1. By controlling d1 / H2 to be 1.5 to 6, the first high-level segments 12 can be arranged relatively densely while ensuring that the first plate 1 is easy to form. This is conducive to increasing the heat exchange area between the refrigerant and the coolant and improving the heat exchange effect. Define the F1 direction, which is the normal direction of the other side of the first plate 1, and the F1 direction is perpendicular to the F2 direction. The first high-level segments 12 are also arranged in an array along the F1 direction, and the first high-level segments 12 are also arranged in an array along the F2 direction. In this embodiment, the plate 5 is roughly rectangular, the F1 direction refers to the length direction of the plate 5, and the F2 direction refers to the width direction of the plate 5. In other embodiments, the F1 direction may also refer to the width direction of the plate 5, and the F2 direction may also refer to the length direction of the plate 5. In other embodiments, the plate 5 may also be roughly square, circular, oval, etc.

[0031] Combination Figure 1-Figure 11The plate 5 includes a body 3 and a flange 4, the flange 4 is arranged to be protruding relative to the body 3, and the flange 4 is arranged in the circumferential direction of the body 3. Along the F1 direction of the plate 5, the plate 5 includes a first end 51 and a second end 52. In this embodiment, the first high section 12 is located in the body 3, and specifically, the first high section 12 is at least located in the middle heat exchange area of ​​the body 3 (not shown in the figure).

[0032] Combination Figure 11-Figure 19 In this embodiment, along the F2 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 F2 direction. The ratio of the distance between adjacent first high sections 12 in the F2 direction to the maximum height of the first high section 12 from the plate surface of the first plate 1 can be 1.5 to 6, that is, the ratio between d1 and H2 is 1.5 to 6. In this embodiment, the ratio of the distance between adjacent first high sections 12 in the F2 direction to the maximum height of the first high section 12 from the plate surface of the first plate 1 is 2.3 to 5.5, that is, the ratio between d1 and H2 is 2.3 to 5.5. The higher the height of the first high-level segment 12, the sparser the first high-level segment 12 should be. Otherwise, the high and dense first high-level segment 12 will lead to a large thinning rate at the top of the first high-level segment 12, so that the plate 5 is not easy to form. The first high-level segment 12 is too sparse and cannot increase the turbulence of the refrigerant and strengthen the heat exchange. When the ratio between d1 and H2 is 2.3-5.5, the first high-level segment 12 can be set relatively densely, which is conducive to increasing the turbulence of the first high-level segment 12 on the refrigerant. The thinning rate of the first plate 1 will not be too low, so that the second plate 2 is easy to form. The ratio between d1 and H2 is applicable to point waves and herringbone waves.

[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 13 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 base plate 35 are opposite, and the recess 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 13 is conducive to increasing the heat exchange area of ​​the refrigerant. The joint setting of the recess and the first low-level section 13 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 addition, fins are usually set between adjacent plates 5 to enhance the heat exchange area to improve the heat exchange effect. In this embodiment, no fins are set between adjacent plates 5. By setting point waves on the plates 5 to enhance the heat exchange area, good heat exchange performance is achieved. Compared with the scheme of setting fins, fins are saved, which is conducive to the lightweight of the heat exchanger. In addition, the scheme for setting up the fins also includes a stacking process for the fins. This scheme only requires stacking the plates during assembly, which helps to simplify the assembly process of the heat exchanger 100 and reduce the manufacturing difficulty and cost of the heat exchanger 100; and the present application saves the assembly process for the fins, which can also improve the manufacturing efficiency of the heat exchanger 100 and save manufacturing time.

[0034] In other embodiments, the first plate 1 and the second plate 2 may be bonded. The first substrate 35 is a planar portion of the first plate 1, and the second substrate 36 is a planar portion of the second plate 2. In other embodiments, the recess 21 and the first high section 12 may be partially staggered, and the staggered setting means that the projections of the first high section 12 and the recess 21 on the plate surface of the first plate 1 overlap.

[0035] In this embodiment, the first plate 1 includes a plurality of first protrusions 11 and a first substrate 35. The first protrusion 11 protrudes toward the second plate 2 relative to the first substrate 35, and the first protrusion 11 has a second groove 122 on the side facing the second plate 2. The first protrusion 11 includes a first high section 12 and a first low section 13. 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, and the first high section 12 is closer to the second substrate 36 of the second plate 2 than the first low section 13. The second groove 122 is located in the first low section 13. The first substrate 35 refers to the first plate 1 before being stamped, and the second substrate 36 refers to the second plate 2 before being stamped.

[0036] The 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 1 includes a plurality of first protrusions 11, and the first protrusions 11 protrude relative to the first plate surface 31 of the first plate 1 toward the second plate 2 on the adjacent side, and the first protrusions 11 protrude upward.

[0037] Define the E direction and the F direction, the E direction intersects with the F direction, and one of the angles between the E direction and the F direction is toward the F2 direction of the heat exchanger 100. The plurality of first protrusions 11 are arranged in an array along the E direction and the F direction, the E direction intersects with the second direction F, and there is an angle α1 between the E direction and the F direction, α1 is toward the F2 direction of the heat exchanger, and α1 is less than 90 degrees.

[0038] 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.

[0039] 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.

[0040] In other embodiments, one or more groups of two adjacent first high segments 12 may not have a first low segment 13 between them, and the two adjacent first high segments 12 in the group may be connected by the first plate surface 31, and there may be a gap between the adjacent first high segments 12 in the group. 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.

[0041] 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. In this embodiment, the ratio of H1 to H2 is 0.25 to 0.75, and the height ratio of the first high section 12 and the first low section 13 is controlled. The top of the first high section 12 and the top of the recess 21 are welded, and the fluid can flow between the first low section 13 and the second substrate of the adjacent second plate 2, which is conducive to preventing the melting of the solder from blocking the space between the first low section 13 and the second substrate of the adjacent second plate 2.

[0042] Combination Figure 5-Figure 11, 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.

[0043] 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.

[0044] The 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 recess 21 of the second plate piece 2 is located on the third plate surface 33, and the recess 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 recess 21 is consistent with the protruding direction of the first high-level section 12. There is a first groove 212 between adjacent recesses 21, and the recess 21 has a groove 211 facing the first plate piece 1 on the other adjacent side.

[0045] 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.

[0046] 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.

[0047] 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.

[0048] The recess 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 recess and the dense convex structure match, which can better improve the heat exchange effect of the refrigerant and the coolant.

[0049] 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 first space S11 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 second space S12 is formed between the first low section 13 and the second substrate 36, and the width of the second space S12 is less than the width of the first space S11. The refrigerant flows from the second space S12 to the first space S11, and then to the second space S12. 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.

[0050] 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 concave portion 21 have different structures. The first high-level section 12 of the first plate 1 and the concave portion 21 of the second plate 2 on the adjacent side have a high degree of asymmetry, which is conducive to increasing the turbulence degree and boiling nucleation state of the refrigerant, so that the high heat exchange performance of the heat exchanger 100 can be achieved. In addition, in order to improve the heat exchange effect of the heat exchanger, fins are usually arranged between the plates 5. The flow channel formed by the fins is difficult to clean. In this application, the first plate 1 and the second plate 2 are stamped structures, and the heat exchanger 100 is easy to clean.

[0051] Combination Figure 4-Figure 6 In this embodiment, the first plate 1 further includes a third convex portion 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. The second low section 18 is recessed toward the first plate 1 relative to the second substrate 36, and 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, and the second high section 17 includes a second top 171, and the second top 171 is flush with the second plate surface 32.

[0052] 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.

[0053] 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.

[0054] 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.

[0055] Combination Figure 6-Figure 11 , α1 is the first distribution angle of the first high segment 12, α1 is also the first distribution angle of the first low segment 13, and α1 can be 15°~75°. In this embodiment, α1 is 20°~35°, including 20°~35. When α1 is other values, 20°~35, the first high segment 12 can be set 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 segment 17 is consistent with the first distribution angle of the first high segment 12, and the distribution angle of the second low segment 18 is also consistent with the first distribution angle of the first low segment 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 segment 17 and the first distribution angle of the first high segment 12 may also be inconsistent, and the first distribution angle of the second low segment 18 and the first distribution angle of the first low segment 13 may also be inconsistent.

[0056] α1 is the second distribution angle of the first high-level segment 12, and α1 is also the second distribution angle of the first low-level segment 13, so that the protrusion structure can be arranged relatively densely, which is beneficial to improving the heat exchange efficiency of the refrigerant and the coolant. In this embodiment, the second distribution angle of the second high-level segment 17 is consistent with the second distribution angle of the first high-level segment 12, and the distribution angle of the second low-level segment 18 is also consistent with the second distribution angle of the first low-level segment 13, which is beneficial to improve the density of the protrusion 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.

[0057] The recesses 21 are arranged in a line along the F direction, and the first distribution angle of the recesses 21 is also α1, and α1 is 20° to 35°, including 20° to 35. The recesses 21 can be arranged relatively densely, which is beneficial to increase the density of the recesses 21, increase the boiling heat transfer effect of the refrigerant, improve the heat exchange efficiency of the refrigerant and the coolant, and improve the heat exchange effect of the heat exchanger 100.

[0058] In this embodiment, along the F2 direction of the plate 5, the ratio of the distance in the F2 direction between adjacent second high sections 17 to the height of the second high section 17 is also 2.3 to 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 distance in the F2 direction 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 distance in the F2 direction between adjacent second high sections 17 to the maximum height of the second high section 17 can also be 1.5 to 2.3 or 5.5 to 6.

[0059] In this embodiment, along the F2 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, and d2 is the distance between adjacent recesses 21 in the F2 direction. The distance between the third top 213 of the recess 21 and the plate surface of the second plate 2 is H3. Specifically, the distance between the third top 213 of the recess 21 and the third plate surface 33 of the second plate 2 is H3. In this embodiment, the ratio of d2 to H3 is also 2.3 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.

[0060] 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.

[0061] 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.

[0062] 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.

[0063] In this embodiment, the first plate 1 includes a first rib 14, which extends in a curved shape along the F1 direction of the first plate 1, and the first rib 14 is welded and fixed to the plate surface of the second plate 2. The arrangement of the first rib 14 can make the refrigerant flow in a U-shaped loop, thereby increasing the heat exchange effect between the refrigerant and the coolant. The arrangement of the first rib 14 is curved, which increases the flow resistance of the flow path close to both sides of the first rib 14, reduces the distribution of the refrigerant on both sides of the first rib 14, and makes the distribution of the refrigerant in the first inter-plate channel S1 more uniform, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0064] In this embodiment, the first plate 1 and the second plate 2 are both provided with ribs to increase the flow path of the refrigerant and the coolant and improve the heat exchange. The second plate 2 includes a second rib 22, and the second rib 22 is arranged so that the coolant flows in a U-shaped loop. The second rib 22 extends roughly in a curved shape along the F1 direction of the first plate 2, and the second rib 22 and the first rib are arranged roughly in parallel, and roughly parallel includes parallel and approximately parallel. Along the height direction of the heat exchanger 100, the first rib 14 and the second rib 22 are staggered, and the staggered arrangement means that the projections of the first rib 14 and the second rib 22 on the first plate surface do not overlap, so that it is convenient to weld and fix the first rib 14 and the second plate 2, and to weld and fix the second rib 22 and the first plate 1. 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.

[0065] In this embodiment, the first rib 14 is located in the body 3, the first rib 14 is located in the first plate surface 31 of the first plate 1, the first rib 14 protrudes 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 other side. Along the F2 direction of the first plate 1, on the side of the first plate surface 31 of the first plate 1, there is a gap between the two sides of the first rib 14 and the first protrusion 11, and the gap can allow the refrigerant to flow. In this embodiment, the second rib 22 is located in the body 3, the second rib 22 is located in the third plate surface 33 of the second plate 2, the second rib 22 protrudes toward the first plate 1 on the adjacent side relative to the plate surface of the second plate 2, 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. Along the F2 direction of the second plate 2, on the third plate surface 33 side of the second plate 2, there is a gap between the two sides of the second rib 22 and the recess 21, and the gap can allow the coolant to flow.

[0066] 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.

[0067] Combination Figure 1 , Figure 11-Figure 19 In 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.

[0068] In this embodiment, the first rib 14 is arranged along the F1 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 F2 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. The second rib 22 is arranged along the F1 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 the 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 . The second rib 22 is located between the third side 23 and the fourth side 24 .

[0069] Combination Figure 5-Figure 14In this embodiment, the first rib 14 is serrated. The first rib 14 includes a first portion 142 and a second portion 143, which are alternately arranged along the F1 direction of the first rib 14, and adjacent first portions 142 and second portions 143 are connected. The first portion 142 and the second portion 143 are arranged at an angle, and the first portion 142 and an adjacent second portion 143 form a first recess (not shown in the figure), the first recess is recessed toward the first side 15 of the first plate 1, and the first recess is protruding toward the second side 16 of the first plate 1. When the refrigerant flows into the first channel 101 and flows around the first rib 14 to the second channel, the refrigerant near both sides of the first rib 14 flows along the first recess, which increases the flow resistance of the flow path near both sides of the first rib 14, reduces the distribution of the refrigerant on both sides of the first rib 14, and makes the distribution of the refrigerant in the first inter-plate channel S1 more uniform, which is beneficial to improving the heat exchange performance of the heat exchanger. In this embodiment, the connection between the first portion 142 and the second portion 143 is arc-shaped, and the arc-shaped setting can reduce the flow resistance of the refrigerant flowing into both sides of the first rib 14 and improve the heat exchange effect. In other embodiments, the connection between the first portion 142 and the second portion 143 can also be tapered.

[0070] In this embodiment, the second rib 22 is also serrated, and the second rib 22 and the first rib 14 are arranged roughly in parallel. The second rib 22 includes a third portion 222 and a fourth portion 223, and the third portion 222 and the fourth portion 223 are alternately arranged along the F1 direction of the second rib 22, and the adjacent third portions 222 and fourth portions 223 are connected. The third portion 222 and the fourth portion 223 are arranged at an angle, and the third portion 222 and an adjacent fourth portion 223 form a second recess (not shown in the figure), the second recess protrudes toward the fourth side 24 of the second plate, and the second recess is recessed toward the third side 23 of the second plate 2. The first portion 142 and the third portion 222 are arranged roughly in parallel, and the second portion 143 and the fourth portion 223 are arranged roughly in parallel. When the coolant flows in from the third channel 103 and flows around the second rib 22 to the fourth channel, the coolant near the two sides of the second rib 22 flows along the second recess, increasing the flow resistance of the flow path near the two sides of the second rib 22, reducing the distribution of the coolant on both sides of the second rib 22, and making the distribution of the coolant in the second inter-plate channel S2 more uniform, which is beneficial to improving the heat exchange performance of the heat exchanger. In this embodiment, the third part 222 and the fourth part 223 are also arc-shaped, which can reduce the flow resistance of the coolant flowing into the two sides of the second rib 22 and improve the heat exchange effect. In other embodiments, the first connection between the third part 222 and the fourth part 223 can also be tapered.

[0071] In this embodiment, the first part 142, the second part 143, the third part 222 and the fourth part 223 are all straight structures, and the first recessed part and the second recessed part are also straight. In this embodiment, the first part 142 and the second part 143 form an angle greater than or equal to 90°, and the third part 222 and the fourth part 223 form an angle greater than or equal to 90°. The first part 142 and the second part 143 are connected, and the first rib 14 forms a zigzag shape, which increases the flow resistance of the refrigerant near the first rib 14, avoids too much refrigerant flowing through here, thereby extending the flow path of the refrigerant and improving the heat exchange effect. The third part 222 and the fourth part 223 are connected, and the second rib 22 forms a zigzag shape, which increases the flow resistance of the coolant near the second rib 22, avoids too much coolant flowing through here, thereby extending the flow path of the coolant and improving the heat exchange effect. The connection between the first part 142 and the second part 143 may be arc-shaped, and the first connection between the third part 222 and the fourth part 223 may be arc-shaped. The arc-shaped setting can improve the heat exchange effect between the refrigerant and the coolant, wherein the arc can be a circular arc or other arcs.

[0072] In other embodiments, the included angle between the first portion 142 and the second portion 143 may also be an acute angle less than 90 degrees, and the included angle between the third portion 222 and the fourth portion 223 may also be an acute angle less than 90 degrees.

[0073] In another embodiment, the first portion 142, the second portion 143, the third portion 222 and the fourth portion 223 are all arc-shaped structures, the first recessed portion and the second recessed portion are also arc-shaped, the first portion 142 and the third portion 222 are arranged roughly in parallel, and the second portion 143 and the fourth portion 223 are arranged roughly in parallel, so that the distribution of the refrigerant and the coolant can be more uniform, and the heat exchange performance of the heat exchanger can be improved. Among them, the arc-shaped structure can be a circular arc or other arcs, so that the first rib portion 14 and the second rib portion 22 form a winding shape.

[0074] In another embodiment, the first part 142 is an arc-shaped structure, the second part 143 is a straight structure, the third part 222 is an arc-shaped structure, and the fourth part 223 is a straight structure. The first part 142 and the third part 222 are arranged roughly in parallel, and the second part 143 and the fourth part 223 are arranged roughly in parallel. This can also make the distribution of the refrigerant and the coolant more uniform, thereby improving the heat exchange performance of the heat exchanger.

[0075] In other embodiments, the first rib 14 may also be in a curved wave shape, and the second rib 22 may also be in a curved wave shape.

[0076] In this embodiment, along the F2 direction of the plate 5, the first rib 14 is offset and 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.

[0077] In this embodiment, along the F2 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.

[0078] In this embodiment, along the F2 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 process 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 process 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.

[0079] In this embodiment, along the F2 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.

[0080] Along the F2 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 F2 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.

[0081] In other embodiments, the first plate 1 may be provided with the first rib 14, and the second plate 2 may not be provided with the second rib 22; or, the first plate 1 may not be provided with the first rib 14, and the second plate 2 may be provided with the second rib 22, which may also improve the heat exchange effect between the refrigerant and the coolant.

[0082] In this embodiment, along the F1 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 F1 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 heat exchange between the refrigerant and the coolant can also be achieved.

[0083] The first plate 1 includes a first protrusion 11, which protrudes toward the second plate 2, and the first protrusion 11 is arranged along the F direction. Part of the first rib 14 extends parallel to the F direction, that is, the extension direction of part of the first rib 14 is consistent with the arrangement direction of the first protrusion 11, so that the flow path of the refrigerant near both sides of the first rib 14 can be consistent with the flow path between the first protrusions 11, which is beneficial to reducing the resistance of the refrigerant flow, making the refrigerant flow smoother, and making the refrigerant and the coolant have a higher heat exchange effect.

[0084] In this embodiment, the first portion 142 extends in a direction parallel to the F direction, that is, the extension direction of the first portion 142 is parallel to the arrangement direction of the first convex portion 11, and the second portion 143 extends in a direction parallel to the E direction, that is, the extension direction of the second portion 143 is also parallel to the arrangement direction of the first convex portion 11. This arrangement can make the shape of the first rib 14 consistent with the flow direction of the refrigerant, avoid the first rib 14 blocking the flow of the refrigerant, reduce the flow resistance of the refrigerant flow, make the refrigerant flow smoother, and make the refrigerant and the coolant have a higher heat exchange effect. Moreover, the extension direction of the first portion 142 is parallel to the arrangement direction of the first convex portion 11, and the extension direction of the second portion 143 is parallel to the arrangement direction of the first convex portion 11. This can reduce the gap between the first rib 14 and the first convex portion 11, making the channels on both sides of the first rib 14 narrower, thereby reducing the flow distribution of the refrigerant on both sides of the first rib 14, allowing more refrigerant to flow into the area where the first convex portion 1 is set, which is conducive to improving heat exchange. In this embodiment, the second rib 22 is also in a Z-shaped wave shape. The second rib 22 includes a third part 222 and a fourth part 223. The third part 222 extends in a direction parallel to the F direction, and the fourth part 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, reduce the flow resistance of the coolant flow, make the coolant flow smoother, and improve the heat exchange effect between the coolant and the refrigerant. In this way, the channels on both sides of the second rib 22 can be made narrower, thereby reducing the flow distribution of the coolant on both sides of the second rib 22, allowing more coolant to flow into the area where the recess 21 is set, which is conducive to improving heat exchange.

[0085] The angle between the F direction and the E direction is α1, and α1 is 15° to 75°, so that the first protrusion 11 and the recess 21 can be arranged more densely, which is conducive to increasing the heat exchange area between the refrigerant and the coolant and improving the heat exchange effect. In this embodiment, α1 is 20° to 35°, so that the first protrusion 11 and the recess 21 can be arranged more densely, and the heat exchange effect of the heat exchanger 100 is better; in addition, the first part 142 and the third part 222 extend along the E direction, and the second part 143 and the fourth part 223 extend along the F direction. Such an angle setting is conducive to making the first rib 14 and the second rib 22 form a more winding shape, increasing the flow resistance of the refrigerant near the first rib 14, avoiding excessive refrigerant from flowing there, thereby extending the flow path of the refrigerant, improving the heat exchange effect, and increasing the flow resistance of the coolant near the second rib 22, extending the flow path of the coolant, and improving the heat exchange effect.

[0086] In other embodiments, the first portion 142 may extend in a direction parallel to the F direction, the second portion 143 may not extend in a direction parallel to the E direction, the third portion 222 may be arranged in conjunction with the first portion 142 , and the fourth portion 223 may be arranged in conjunction with the second portion 143 . For example, the first part 142, the second part 143, the third part 222 and the fourth part 223 are all straight structures, and the first part 142 and the third part 222 extend in a direction parallel to the F direction, that is, the arrangement direction of the first part 142, the third part 222 and the first convex part 11 is consistent, and the second part 143 and the fourth part 223 do not extend in a direction parallel to the E direction, that is, the arrangement direction of the second part 143 and the first convex part 11 are inconsistent, and the arrangement direction of the fourth part 223 and the first convex part 11 are inconsistent; or, the second part 143 is an arc-shaped structure, the first part 142 is a straight structure, the fourth part 223 is an arc-shaped structure, and the third part 222 is a straight structure. The first part 142 and the third part 222 extend in a direction parallel to the F direction, and the second part 143 and the fourth part 223 do not extend in a direction parallel to the E direction.

[0087] 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.

[0088] In other embodiments, the first convex portion 11 may not include the first low-position segment 13, and the third convex portion 37 may not include the second low-position segment 18. The shapes of the first convex portion 11 and the third convex portion 37 are not limited. By controlling the ratio of d1 and H2, the first high-position segment 12 and the third convex portion 37 are arranged relatively densely, which can improve the heat exchange effect and make the plate easy to form.

[0089] 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), comprising a first plate (1), characterized in that: The first plate (1) comprises a first substrate (35) and a plurality of first high-level segments (12), wherein the first high-level segments (12) are arranged to be raised relative to the first substrate (35), and the normal of one side of the first plate (1) is defined as a direction F2. Along the direction F2, the distance between the center points of two adjacent first high-level segments (12) is d1, and the distance between the first top (121) of the first high-level segment (12) and the height of the first substrate (35) is H2, and the ratio of d1 to H2 is 1.5 to 6.

2. The heat exchanger (100) according to claim 1, characterized in that: The first base plate (35) comprises a first plate surface (31); along the height direction of the heat exchanger (100), the height of the first top (121) of the first high-position section (12) from the first plate surface (31) is H2, and the ratio of d1 to H2 is 2.3 to 5.

5.

3. The heat exchanger (100) according to claim 2, characterized in that: The heat exchanger (100) further comprises a second plate (2), a first inter-plate channel (S1) being provided between the first plate (1) and the second plate (2), the first high-position section (12) protruding toward the second plate (2), the second plate (2) comprising a recess (21) and a second base plate (36), the recess (21) being recessed relative to the second base plate (36) in a direction away from the first plate (1), along the height direction of the heat exchanger (100), the recess (21) and the first high-position section (12) being arranged opposite to each other and fixedly connected, along the F2 direction, the distance between the center points of adjacent recesses (21) is d2, the height of the third top (213) of the recess (21) from the third plate surface (33) of the second base plate (36) is H3, and the ratio of d2 to H3 is 2.3 to 5.

5.

4. The heat exchanger (100) according to any one of claims 1 to 3, characterized in that: The first plate (1) comprises a first convex portion (11), the first convex portion (11) comprises a first high section (12) and a first low section (13), and along the height direction of the heat exchanger (100), the height of the first low section (13) from the first plate surface (31) is H1, and H1 is smaller than H2.

5. The heat exchanger (100) according to claim 4, characterized in that: The ratio of H1 to H2 is 0.25 to 0.

75.

6. The heat exchanger (100) according to claim 5, characterized in that: The heat exchanger (100) comprises a plurality of plates (5), wherein the plates (5) comprise a first plate (1) and a second plate (2), wherein the first plate (1) and the second plate (2) are alternately stacked, wherein the plate (5) comprises a body (3), wherein the first convex portion (11) is located on the body (3), and defines an E direction and an F direction, wherein the E direction intersects with the F direction, wherein one of the angles between the E direction and the F direction is oriented toward the F2 direction of the heat exchanger (100), wherein the first convex portion (11) is arranged in an array along the E direction and the F direction, and wherein a first high-level segment (12) and a first low-level segment (13) are alternately arranged along the E direction and the F direction.

7. The heat exchanger (100) according to claim 6, characterized in that: An included angle between the E direction and the F direction is defined as α1, wherein α1 is directed toward the F2 direction of the heat exchanger (100), and α1 is in the range of 15° to 75°.

8. The heat exchanger (100) according to claim 7, characterized in that: The α1 is 20° to 35°.

9. The heat exchanger (100) according to claim 7 or 8, characterized in that: The recessed portions (21) are arranged along the F direction, the recessed portions (21) are arranged along the E direction, the recessed portions (21) and the first high-position segment (12) are arranged opposite to each other, and the third top portion (213) of the recessed portions (21) and the first high-position segment (12) are fixedly connected.

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