Heat exchanger

Abstract

The heat exchanger comprises a first plate sheet and a second plate sheet, the first plate sheet comprises a plurality of first protruding parts and a first base plate, and the first protruding parts protrude towards the second plate sheet relative to the first base plate; the first plate sheet comprises a first rib part, and the protruding direction of the first rib part is consistent with the protruding direction of the first protruding part; the plurality of first convex parts comprise a first group of first convex parts and a second group of first convex parts, the first group of first convex parts are positioned on one side of the first rib part, the second group of first convex parts are positioned on the other side of the first rib part, and the first group of first convex parts are closer to the first rib part than the second group of first convex parts. And the flow between the first convex part and the first rib part in the first group is relatively reduced, so that the heat exchange performance of the heat exchanger is improved.

Description

[0001] This application is a divisional application with application number 202311088493.4 and invention name “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 heat exchange channels are formed between adjacent plates. Fluid can flow through the heat exchange channels to exchange heat with external equipment of the heat exchanger. How to improve the heat exchange performance of the heat exchanger is a technical problem that needs to be solved urgently. Summary of the invention

[0004] The purpose of the present application is to provide a heat exchanger, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0005] One embodiment of the present application provides a heat exchanger, including 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 includes 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 plate includes a first rib, wherein the first rib protrudes relative to the first substrate toward the second plate, and the protrusion direction of the first rib is consistent with the protrusion direction of the first protrusion; wherein the plurality of first protrusions include a first group of first protrusions and a second group of first protrusions, wherein the first group of first protrusions and the second group of first protrusions are both composed of first protrusions adjacent to the first rib; wherein a direction perpendicular to an extension direction of the first rib and parallel to an extension direction of the first substrate is defined as a first direction, wherein along the first direction, the first group of first protrusions is located on one side of the first rib, and the second group of first protrusions is located on the other side of the first rib; wherein the first group of first protrusions is adjacent to the first rib, and the second group of first protrusions is adjacent to the first rib; and along the first direction, the first group of first protrusions is closer to the first rib than the second group of first protrusions. In the heat exchanger provided in the embodiment of the present application, along the first direction, the first group of first protrusions are closer to the first rib than the second group of first protrusions. When the heat exchanger is working, the flow resistance between the first group of first protrusions and the first rib can be made smaller than the flow resistance between the second group of first protrusions and the first rib, so that the flow rate between the first group of first protrusions and the first rib is relatively reduced, so that the fluid flows more between the first protrusions, thereby improving the heat exchange performance of the heat exchanger.

[0006] Another embodiment of the present application provides a heat exchanger, comprising 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 plate comprises a first rib, wherein the first rib protrudes relative to the first substrate toward the second plate, and the protrusion direction of the first rib is consistent with the protrusion direction of the first protrusion; wherein the plurality of first protrusions comprises a first group of first protrusions and a second group of first protrusions, wherein the first group of first protrusions and the second group of first protrusions are both composed of first protrusions adjacent to the first rib; wherein a direction perpendicular to an extension direction of the first rib and parallel to an extension direction of the first substrate is defined as a first direction, wherein along the first direction, the first group of first protrusions is located on one side of the first rib, and the second group of first protrusions is located on the other side of the first rib; wherein the first group of first protrusions is adjacent to the first rib, and the second group of first protrusions is adjacent to the first rib; and wherein the width of a gap formed between the first group of first protrusions and the first rib is smaller than the width of a gap formed between the second group of first protrusions and the first rib along the first direction.

[0007] In a heat exchanger provided in another embodiment of the present application, along the first direction, the width of the gap formed between the first group of first protrusions and the first rib is smaller than the width of the gap formed between the second group of first protrusions and the first rib. When the heat exchanger is working, the flow resistance between the first group of first protrusions and the first rib can be smaller than the flow resistance between the second group of first protrusions and the first rib, thereby relatively reducing the flow rate between the first group of first protrusions and the first rib, allowing more fluid to flow between the first protrusions, thereby improving the heat exchange performance of the heat exchanger. 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 schematic diagram of the three-dimensional structure of the heat exchanger provided by the present application from another perspective;

[0010] Figure 3 yes Figure 1 A three-dimensional 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 5 A schematic diagram of the three-dimensional structure of the second plate from one viewing angle;

[0017] Fig.10 yes Figure 5 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 1 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 yes Fig.12 A schematic structural diagram of a combined structure of a first rib portion and a second rib portion of a heat exchanger;

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

[0023] Fig.16 yes Fig.15 A schematic diagram of the cross-sectional structure along the middle A2-A2 plane;

[0024] Fig.17 is a structural schematic diagram of a connection portion of a first plate of a heat exchanger;

[0025] Fig.18 A schematic diagram of the exploded structure of the first plate and the second plate in the heat exchanger is shown;

[0026] Fig.19 Shows Fig.18 The schematic diagram of the structure of the first plate at an angle is shown;

[0027] Fig. 20 Shows Fig.18 The schematic diagram of the partial three-dimensional structure of the second plate at position C is shown;

[0028] Fig.21 Shows Fig.19 The schematic diagram of the local structure of the first plate at position A is shown;

[0029] Fig. 22 Shows Fig.19 The schematic diagram of the local structure of the first plate at position B is shown;

[0030] Fig.23 Shows Fig.19 A schematic diagram of the local structure of the first plate at position B is shown. DETAILED DESCRIPTION

[0031] The present application is further described below with reference to the accompanying drawings and specific embodiments:

[0032] Combination Figure 1-Figure 23 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 only relative positions, and the height direction, length direction, and width direction of the heat exchanger 100 are defined as the attached drawings of the specification. Figure 1In the height direction, length direction and width 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 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.

[0033] like Figure 18-Figure 23 As shown, the plurality of plates 5 include a first plate 1 and a second plate 2 , and a portion of the heat exchanger may be formed by alternately stacking the first plate 1 and the second plate 2 .

[0034] A first inter-plate channel s1 is provided between the first plate 1 and the second plate 2. The first plate 1 includes a plurality of first protrusions 11 and a first substrate 35. The first protrusion 11 protrudes relative to the first substrate 35 toward the second plate 2. The first plate 1 includes a first rib 14. The protrusion direction of the first rib 14 is consistent with the protrusion direction of the first protrusion 11. The plurality of first protrusions 11 include a first group of first protrusions K1 and a second group of first protrusions K2. A direction perpendicular to the extension direction of the first rib 14 and parallel to the extension direction of the first substrate 35 is defined as a first direction. In the first direction, the first group of first protrusions K1 are located on one side of the first rib 14, and the second group of first protrusions K2 are located on the other side of the first rib 14. The first group of first protrusions K1 are adjacent to the first rib 14, and the second group of first protrusions K2 are adjacent to the first rib 14. Along the first direction, the first group of first protrusions K1 are closer to the first rib 14 than the second group of first protrusions K2. In other words, along the first direction, the width of the gap formed between the first group of first protrusions K1 and the first rib 14 is smaller than the width of the gap formed between the second group of first protrusions K2 and the first rib 14. The first direction is indicated by W in the figure. In this embodiment, the first plate 1 is rectangular as a whole, and the extension direction of the first rib 14 is substantially the same as the extension direction of the first rib 14. In other embodiments, the extension direction of the first rib 14 may also be substantially the same as the width direction of the first plate 1. It should be noted that the edge of the first protrusion 11 refers to the junction between the first protrusion 11 and the first substrate 35, the edge of the first rib 14 refers to the junction between the first rib 14 and the first substrate 35, and "the first group of first protrusions K1 is closer to the first rib 14 than the second group of first protrusions K2" means that the distance between the edge of the first group of first protrusions K1 and the edge of the first rib 14 is smaller than the distance between the edge of the second group of first protrusions K2 and the edge of the first rib 14.

[0035] like Fig.18 , Fig.21As shown, when the heat exchanger is working, the fluid flows through the first inter-plate channel s1, and along the first direction, the first group of first protrusions K1 are closer to the first rib 14 than the second group of first protrusions K2, so that the flow resistance between the first group of first protrusions K1 and the first rib 14 can be smaller than the flow resistance between the second group of first protrusions K2 and the first rib 14, so that the bypass flow formed between the first group of first protrusions K1 and the first rib 14 is relatively reduced, so that the fluid flows more to between the first protrusions 11, thereby improving the heat exchange performance of the heat exchanger. Fig.21 , Fig. 22 The black one-way arrow in the figure shows the flow path of the fluid between the first convex portion 11 and the first rib portion 14. It should be noted that: Fig.21 Only a portion of the first group of first protrusions K1 and a portion of the second group of first protrusions K2 are shown.

[0036] The heat exchanger includes a first channel 101 and a second channel 102. Along the first direction, the first channel 101 and the second channel 102 are located on both sides of the first rib 14. Along the direction parallel to the first substrate 35, one end of the first rib 14 is connected to the first end 51 of the first plate 1, and the other end of the first rib 14 is not connected to the second end 52 of the first plate 1. The first channel 101 and the second channel 102 are both connected to the first inter-plate channel, so that the fluid can flow in a U-shaped path around the first rib 14, so that the fluid has at least two flow sections. In this embodiment, the first channel 101 is used to introduce the fluid into the first inter-plate channel, and the second channel 102 is used to export the fluid from the first inter-plate channel, or in other words, the first channel 101 is the inflow channel of the fluid, and the second channel 102 is the outflow channel of the fluid. Along the first direction, the first group of first protrusions K1 and the first channel 101 are located on the same side of the first rib 14, and the second group of first protrusions K2 and the second channel 102 are located on the same side of the first rib 14. In this way, the fluid flow on the upstream side of the first inter-plate channel is more evenly distributed in the first direction, which is beneficial to improving the heat exchange performance of the heat exchanger.

[0037] In the direction perpendicular to the first substrate 35, the orthographic projection of the top end 225 of the second rib 22 on the first substrate 35 is located between the second group of first protrusions K2 and the first rib 14. Since the space between the second group of first protrusions K2 and the first rib 14 is relatively large, the welding area between the top end 225 of the second rib 22 and the first substrate 35 of another adjacent first plate 1 (not shown in the figure) is larger, thereby improving the firmness and sealing of the welding here.

[0038] The number of the first protrusions 11 in the first group of first protrusions K1 is more than two, and the first protrusions 11 in the first group of first protrusions K1 are arranged along the extension direction of the first rib 14. In this way, along the extension direction of the first rib 14, the bypass flow between the first protrusion 11 and the first rib 14 can be continuously reduced, thereby improving the heat exchange performance of the heat exchanger.

[0039] In this embodiment, along the first direction, the width of the first group of first protrusions K1 is greater than the width of the second group of first protrusions K2. The relatively wide first group of first protrusions K1 has a stronger fluid resistance, which can further reduce the fluid flow between the first group of first protrusions K1 and the first rib 14. In addition, in order to adapt to different heat exchange requirements, the width of the first plate 1 will have different widths according to design requirements. If the widths of all first protrusions 11 on the first plate 1 are the same, the first protrusions 11 may not be fully arranged in the first direction, resulting in a large gap between the first protrusions 11 and the first rib 14. In this embodiment, the width of the second group of first protrusions K2 can be the same as the width of the normal first protrusions 11. By increasing the width of the first group of first protrusions K1, the aforementioned gap is reduced, and then without changing the width of the normal first protrusion 11, the width of the first plate 1 can be adjusted within a smaller range (i.e., within the width of a normal first protrusion 11).

[0040] like Fig.18 , Fig.21 As shown, the end of the first rib 14 relatively close to the second end 52 of the first plate 1 is defined as the open end 142, and along the extension direction of the first rib 14, the second group of first protrusions K2 extends to the vicinity of the open end 142. On the one hand, since the fluid makes a sharp turn near the open end 142, the fluid is easily thrown away from the open end 142 near the open end 142. On the other hand, the distance between the second group of first protrusions K2 and the first rib 14 is relatively large, and the flow resistance of the channel between the second group of first protrusions K2 and the first rib 14 is relatively small, which makes it easier for the fluid to enter between the second group of first protrusions K2 and the first rib 14 from the vicinity of the open end 142. The above two effects are superimposed, which can make the flow near the open end 142 in a relatively moderate range.

[0041] In this embodiment, the first rib 14 extends in a curved shape along the first direction. The first rib 14 is arranged in a curved shape, 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.

[0042] 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 in a curved shape along the length direction of the first plate 2, and the second rib 22 and the first rib are arranged roughly parallel, and roughly parallel includes parallel and approximately parallel. 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 along the height direction of the heat exchanger 100, which facilitates the welding and fixing of the first rib 14 and the second plate 2, and facilitates the welding and fixing of the second rib 22 and the first plate 1.

[0043] like Fig.19 , Fig. 22 , Fig.23 As shown, along the extension direction of the first rib 14, the other end of the second group of first protrusions K2 is basically flush with one end of the second rib 22 of the second plate 2, which can adapt to the structure of the second rib 22 of the second plate 2 and facilitate strengthening the welding between the second rib 22 of the second plate 2 and the first plate 1. Fig.23 FIG. 2 shows an orthographic projection 22L of the top 225 of the second rib 22 on the first plate 1 . The top 225 of the second rib 22 can be welded to another adjacent first plate 1 .

[0044] Specifically, Fig. 22 , Fig.23 As shown, the plurality of first protrusions 11 include a third group of first protrusions K3. Along the first direction, the third group of first protrusions K3 and the second group of second protrusions K2 are located on the same side of the first rib 14. The first protrusions 11 in the third group of first protrusions K3 are all adjacent to the first rib 14. The first protrusions 11 in the third group of first protrusions K3 extend along the extension direction of the first rib 14. Along the extension direction of the first rib 14, the third group of first protrusions K3 are basically located between the orthographic projection of the second rib 22 of the first plate 1 and the first end 51 of the first plate 1. The distance between the third group of first protrusions K3 and the first rib 14 is defined as S1, and the distance between the first group of first protrusions K1 and the first rib 14 is defined as S2. S1 is the same or substantially the same as S2. It should be noted that, Fig. 22 Only a portion of the first group of first protrusions K1 , a portion of the second group of first protrusions K2 , and a portion of the third group of first protrusions K3 are shown.

[0045] In this embodiment, the edge of the first protrusion 11 is rhombus-shaped. In other embodiments, the edge of the first protrusion 11 may be triangular or hexagonal.

[0046] 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.

[0047] Combination Figure 1 , Figure 11-Figure 23 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.

[0048] In this embodiment, 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 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. 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 . The second rib 22 is located between the third side 23 and the fourth side 24 .

[0049] 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 length 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 protrudes toward the first side 15 of the first plate 1, and the first recess protrudes 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.

[0050] 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 length 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 of the second plate, and the second recess is recessed toward the third side of the second plate. 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, which increases the flow resistance of the flow path near the two sides of the second rib 22, reduces the distribution of the coolant on both sides of the second rib 22, and makes 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.

[0051] 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 concave part and the second concave 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. In other embodiments, the connection between the first portion 142 and the second portion 143 may be arc-shaped, and the connection between the third portion 222 and the fourth portion 223 may be arc-shaped, wherein the arc may be a circular arc or other arc shapes.

[0052] 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.

[0053] 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.

[0054] 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.

[0055] 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.

[0056] In this embodiment, along the width 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. 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.

[0057] 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.

[0058] 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 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.

[0059] 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.

[0060] 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.

[0061] 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.

[0062] 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.

[0063] The first protrusions 11 are arranged along the F direction, and part of the first ribs 14 extend parallel to the F direction, that is, the extension direction of part of the first ribs 14 is consistent with the arrangement direction of the first protrusions 11. In this way, the flow path of the refrigerant near the two sides of the first ribs 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 achieving a higher heat exchange effect between the refrigerant and the coolant.

[0064] 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 first portion 142 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 more smoothly, and make the refrigerant and the coolant have a higher heat exchange effect. In this embodiment, the second rib 22 is also Z-shaped and wavy. 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, reduce the flow resistance of the coolant flow, make the coolant flow more smoothly, and improve the heat exchange effect of the coolant and the coolant.

[0065] 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.

[0066] 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.

[0067] Combination Figure 1-Figure 23 The first inter-plate channel S1 includes a first sub-inter-plate channel S11, and the first sub-inter-plate channel S11 is located between the first rib 14 and the first convex portion 11. It should be noted that the first convex portion 11 here does not refer to a single convex portion, but a first convex portion group composed of a plurality of first convex portions 11 arranged side by side near the first rib 14 along the length direction of the plate 5. When the refrigerant flows into the first inter-plate channel S1 from the first channel 101, part of the refrigerant is diverted to the first sub-inter-plate channel S11. In the known technology, the first sub-inter-plate channel S11 has a small flow resistance, a fast flow rate, and a large relative flow volume compared to other first inter-plate channels S1 because there is no rib blocking it, which affects the heat exchange effect. In this embodiment, the first plate 15 includes a connecting portion 8, the connecting portion 8 is located between the first rib 14 and the above-mentioned first convex portion group, the connecting portion 8 protrudes toward the second plate 25 relative to the first substrate 35, and along the height direction of the heat exchanger 100, at least part of the first convex portion 11 is close to the second plate 25 relative to the connecting portion 8, that is, at least part of the first convex portion 11 is far away from the first substrate 35 of the first plate 15 relative to the connecting portion 8. The setting of the connecting portion 8 can relatively increase the flow resistance of the first sub-plate channel S11, increase the heat exchange area of ​​the first sub-plate channel S11, and improve the heat exchange efficiency. On the other hand, due to the setting of the connecting portion 8, when the refrigerant flows from the first channel 101 into the first inter-plate channel S1, the amount of refrigerant allocated to the first sub-plate channel S11 is relatively small, and the amount of refrigerant allocated to other first inter-plate channels S1 increases.

[0068] Specifically, in the present embodiment, one end of the connecting portion 8 is connected to the first rib 14, and / or the other end of the connecting portion 8 is connected to the first protrusion 11. Of course, in some other embodiments, the connecting portion 8 is located between the first rib 14 and the first protrusion 11, and the two ends of the connecting portion 8 are not connected to the first rib 14 and the first protrusion 11.

[0069] In this embodiment, a plurality of connection parts 8 can be provided, and the plurality of connection parts 8 are arranged at intervals along the length direction of the heat exchanger 100. For better heat exchange effect, connection parts 8 are provided from the inflow area where the refrigerant enters the first inter-sub-plate channel S11 to the area where the refrigerant flows out of the first inter-sub-plate channel S11. Specifically, in this embodiment, the first rib 14 is in a Z-shaped wave shape, and the first rib 14 includes a first part 142 and a second part 143. The first part 142 and the second part 143 are alternately arranged along the length direction of the first rib 14, and the adjacent first part 142 and the second part 143 are connected. In this embodiment, the extension direction F of the first part 142 is parallel or substantially parallel, and the extension direction of the second part 143 is parallel or substantially parallel to the E direction. Such an arrangement can make the shape of the first rib 14 substantially the same as 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. It should be noted that the above-mentioned substantially parallel means that the angle with the F direction and the E direction is 0-10 degrees. For the convenience of manufacturing and simple mold forming, some of the multiple connecting parts 8 are arranged along the F direction, and / or, some of the multiple connecting parts 8 are arranged along the E direction, wherein the connecting part 8 arranged along the F direction has one end connected to the first protrusion 11, and the other end connected to the second part 143 of the first rib 14, wherein the connecting part 8 arranged along the E direction has one end connected to the first protrusion 11, and the other end connected to the first part 142 of the first rib 14. It can be understood that the connecting part 8 connected to the first part 142 and the connecting part 8 connected to the second part 143 are symmetrically arranged, and the intersection line of the first part 142 and the second part 143 is parallel to the width direction of the heat exchanger 100. For the refrigerant side, due to the low viscosity of the refrigerant itself, when the refrigerant flows through the first inter-sub-plate channel S11, the setting of the connecting portion 8 can increase the flow resistance of the refrigerant. It can be understood that multiple connecting portions 8 are set, and some connecting portions 8 are set along the F direction, and some connecting portions 8 are set along the E direction, and the two are set alternately, and at least part of the first rib 14, the connecting portion 8, the first convex portion 11, the first substrate 35, and the second plate 25 define a low flow position, and the connecting portion 8 and part of the second plate 25 define a high flow position. Then, the refrigerant in the first inter-sub-plate channel S11 flows in a wavy path along the height direction of the heat exchanger 100, that is, a flow channel structure of "high flow position-low flow position-high flow position" is formed. Compared with the straight line without the connecting portion 8, the setting of the connecting portion 8 of this scheme can increase the flow resistance when the refrigerant flows, and the setting of the connecting portion 8 can also increase the heat exchange area between the fluids and improve the heat exchange performance.

[0070] 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, comprising a first plate (1) and a 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); The first plate (1) comprises a first rib (14), and the protrusion direction of the first rib (14) is consistent with the protrusion direction of the first protrusion (11); The plurality of first protrusions (11) include a first group of first protrusions (K1) and a second group of first protrusions (K2), wherein a direction perpendicular to an extension direction of the first rib (14) and parallel to an extension direction of the first substrate (35) is defined as a first direction, and along the first direction, the first group of first protrusions (K1) are located on one side of the first rib (14), and the second group of first protrusions (K2) are located on the other side of the first rib (14); The first group of first protrusions (K1) are adjacent to the first rib (14), and the second group of first protrusions (K2) are adjacent to the first rib (14); Along the first direction, the first group of first protrusions (K1) is closer to the first rib (14) than the second group of first protrusions (K2).

2. The heat exchanger according to claim 1, characterized in that: Along a direction parallel to the first substrate (35), one end of the first rib (14) is connected to the first end (51) of the first plate (1), and the other end of the first rib (14) is not connected to the second end (52) of the first plate (1); The heat exchanger comprises a first hole channel (101) and a second hole channel (102); along the first direction, the first hole channel (101) and the second hole channel (102) are located on both sides of the first rib (14); the first hole channel (101) and the second hole channel (102) are both connected to the first inter-plate channel; the first hole channel (101) is used to introduce fluid into the first inter-plate channel; and the second hole channel (102) is used to guide fluid out of the first inter-plate channel; Along the first direction, the first group of first protrusions (K1) and the first channel (101) are located on the same side of the first rib (14), and the second group of first protrusions (K2) and the second channel (102) are located on the same side of the first rib (14).

3. The heat exchanger according to claim 2, characterized in that: Along the first direction, the width of the first group of first protrusions (K1) is greater than the width of the second group of first protrusions (K2).

4. The heat exchanger according to claim 2, characterized in that: The number of the first protrusions in the first group of first protrusions (K1) is more than two, and the first protrusions (11) in the first group of first protrusions (K1) are arranged along the extension direction of the first rib (14).

5. The heat exchanger according to claim 2, characterized in that: The end of the first rib (14) relatively close to the second end (52) of the first plate (1) is defined as an open end (142); along the extension direction of the first rib (14), one end of the second group of first protrusions (K2) extends to the vicinity of the open end (142); the second plate (2) includes a second rib (22); and the other end of the second group of first protrusions (K2) is substantially flush with one end of the second rib (22).

6. The heat exchanger according to claim 5, characterized in that The plurality of first protrusions (11) include a third group of first protrusions (K3); along the first direction, the third group of first protrusions (K3) and the second group of first protrusions (K2) are located on the same side of the first rib (14); the first protrusions (11) in the third group of first protrusions (K3) are all adjacent to the first rib (14); along the extension direction of the first rib (14), the third group of first protrusions (K3) are basically located between the orthographic projection of the second rib (22) on the first plate (1) and the first end (51) of the first plate (1); the distance between the third group of first protrusions (K3) and the first rib (14) is defined as S1; the distance between the first group of first protrusions (K1) and the first rib (14) is defined as S2; S1 is the same as or approximately the same as S2.

7. The heat exchanger according to any one of claims 1 to 6, characterized in that: The first rib (14) extends in a curved shape along the first direction.

8. The heat exchanger according to claim 7, characterized in that The edge of the first protrusion (11) is rhombus-shaped, triangular-shaped or hexagonal-shaped.

9. The heat exchanger according to claim 7, characterized in that: The first rib (14) is sawtooth-shaped, comprising a first portion (142) and a second portion (143), the first portion (142) and the second portion (143) being alternately arranged along the length direction of the first rib (14), adjacent first portions (142) and second portions (143) being connected; and the first portion (142) and the second portion (143) being arranged at an angle.

10. A heat exchanger, comprising a first plate (1) and a second plate (2), wherein the first plate (1) comprises a plurality of first protrusions (11) and a first base plate (35), and the first protrusions (11) protrude relative to the first base plate (35) toward the second plate (2); The first plate (1) comprises a first rib (14), and the protrusion direction of the first rib (14) is consistent with the protrusion direction of the first protrusion (11); The plurality of first protrusions (11) include a first group of first protrusions (K1) and a second group of first protrusions (K2), wherein a direction perpendicular to an extension direction of the first rib (14) and parallel to an extension direction of the first substrate (35) is defined as a first direction, and along the first direction, the first group of first protrusions (K1) are located on one side of the first rib (14), and the second group of first protrusions (K2) are located on the other side of the first rib (14); The first group of first protrusions (K1) are adjacent to the first rib (14), and the second group of first protrusions (K2) are adjacent to the first rib (14); Along the first direction, the width of the gap formed between the first group of first protrusions (K1) and the first rib (14) is smaller than the width of the gap formed between the second group of first protrusions (K2) and the first rib (14).

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