Plates of plate heat exchanger and plate heat exchanger

Abstract

The present application provides a plate having a length dimension of less than or equal to 300 mm. The plate is provided with a main heat exchange region, and comprises a flat portion located in the main heat exchange region and a plurality of corrugated structures. The plurality of corrugated structures are arranged at intervals and protrude relative to the flat portion. Flow channels for refrigerant and coolant flow are formed on both sides of the front and back of the plate at the main heat exchange region, respectively. The two flow channels have different channel volumes, with the side of the plate having the smaller flow channel being used for refrigerant flow, and the side of the plate having the larger flow channel being used for coolant flow. The corrugated structure has at least one extension section. The extension section is arranged obliquely relative to the length direction of the plate, and the angle β formed between the extension direction of the extension section and the length direction of the plate satisfies 65°≤β<90°. A plate heat exchanger using this type of plate has good overall heat exchange performance under the condition of small-sized plates, while also taking into account fluid pressure drop.

Description

Technical Field

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

[0002] In related technologies, plate heat exchangers can generally be used for heat exchange between two fluids. Fluid heat exchange efficiency is an important parameter indicator of plate heat exchangers. In small-sized plate heat exchanger products, how to balance heat exchange efficiency and fluid pressure drop is a major problem for small-sized plate heat exchangers. Summary of the Invention

[0003] On one hand, the present application provides a plate of a plate heat exchanger, wherein the plate is provided with a main heat exchange area, the plate has corner hole areas located on both sides of the main heat exchange area, the plate has a flat portion located in the main heat exchange area and a plurality of corrugated structures; along the length direction of the plate, the plurality of corrugated structures are arranged at intervals from each other and all of the plurality of corrugated structures protrude relative to the flat portion on the same side of the plate; circulation channels for refrigerant flow and for secondary refrigerant flow are formed on both sides of the front and back surfaces of the plate at the main heat exchange area, respectively, and the channel volumes of the two circulation channels are different, the side of the plate where the circulation channel with a smaller volume is located is used for circulating refrigerant, and the side of the plate where the circulation channel with a larger volume is located is used for circulating secondary refrigerant;

[0004] The dimension of the plate in its length direction is less than or equal to 300 mm; the corrugated structure has at least one extension section; the extension section is inclined relative to the length direction of the plate, and the angle β formed by the extension direction of the extension section and the length direction of the plate satisfies 65°≤β<90°; the corrugated structure is provided with a first recessed portion, the first recessed portion is recessed from the top surface of the corrugated structure, the first recessed portion extends along the extension direction of the corrugated structure, the depth of the bottom of the first recessed portion relative to the top surface of the corrugated structure is less than the depth of the flat portion relative to the top surface of the corrugated structure, and the corrugated structure includes two sub-sections located on both sides of the first recessed portion; the distance between the center lines of the two sub-sections adjacent to the first recessed portion in the extension direction is recorded as L1, the depth of the bottom of the first recessed portion relative to the top surface of the corrugated structure is recorded as D1, and the distance between the center lines of the two sub-sections adjacent to the flat portion in the extension direction is recorded as L2, wherein D1 / L1≥1 / 6, and D2 / L2≥1 / 5.

[0005] On the other hand, the present application also provides a plate heat exchanger, which is used in an automobile air-conditioning thermal management system, and includes at least one plate as described above.

[0006] In plates with a length dimension of less than or equal to 300 mm, since the refrigerant circulation channels and the coolant circulation channels formed on the front and back sides of the plates have different volumes, the refrigerant flows in the smaller, i.e. more compact, circulation channels to achieve a smaller refrigerant charge, and is beneficial to improving the heat transfer coefficient of the refrigerant side fluid and achieving better heat exchange performance. The extension section is inclined relative to the length direction of the plate at an angle β satisfying 65°≤β<90°. For the refrigerant side with a more compact channel structure, the refrigerant is more likely to flow along the groove corresponding to the extension direction of the extension section, and the corresponding refrigerant flow resistance along the length direction of the plate increases. Therefore, the relatively large β angle is conducive to meeting the technical requirements of the refrigerant side with high pressure drop, so that the refrigerant side can achieve better enhanced heat exchange purposes. At the same time, the refrigerant flows in the larger volume, that is, the more spacious circulation channel. The relatively spacious refrigerant flow channel is conducive to achieving the technical requirements of low pressure drop on the refrigerant side. Through the above arrangement, it is conducive to making the plate heat exchanger using such plates meet the requirements of small size while taking into account heat exchange efficiency and fluid pressure drop. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Figure 1 This is a schematic structural diagram of a plate heat exchanger involved in an embodiment of the present application;

[0008] Figure 2 This is a schematic structural diagram of a plate in an embodiment of the present application;

[0009] Figure 3 yes Figure 2 A schematic diagram of the three-dimensional structure of the plate from another perspective;

[0010] Figure 4 yes Figure 2 An enlarged schematic diagram of a portion of the structure on the front side of the plate is shown;

[0011] Figure 5 yes Figure 2 An enlarged schematic diagram of a portion of the structure on the reverse side of the illustrated plate;

[0012] Figure 6 yes Figure 4 Schematic diagram of the cross section of the plate along the AA direction;

[0013] Figure 7 This is a schematic diagram of a cross-sectional effect of two plates of a plate heat exchanger involved in an embodiment of the present application after assembly;

[0014] Figure 8 This is another cross-sectional schematic diagram of the two plates of the plate heat exchanger involved in the embodiment of the present application after assembly;

[0015] Figure 9This is another cross-sectional schematic diagram of the two plates of the plate heat exchanger involved in the embodiment of the present application after assembly;

[0016] Figure 10 is a schematic structural diagram of another plate in an embodiment of the present application;

[0017] Figure 11 It is a structural schematic diagram of another plate in the embodiment of the present application. DETAILED DESCRIPTION

[0018] In residential air conditioning systems, plate heat exchangers are typically large, for example, with plates exceeding 500mm in length. Furthermore, based on the inventor's R&D experience, the refrigerant-side pressure drop specification for achieving heat exchange is typically between 10kPa and 30kPa. Due to the large size of the product, the distance between the refrigerant inlet and outlet corners of the plate, a key factor affecting heat exchange, is long, resulting in a relatively low pressure drop gradient for plate heat exchangers. Therefore, under the relatively low pressure drop parameter constraint, large-sized plate heat exchangers do not require an extremely compact channel structure to meet pressure drop requirements.

[0019] In technical fields where small-sized plate heat exchangers are used, such as automotive air conditioning, the overall dimensions of plate heat exchangers are relatively small due to the compactness of automotive products. For example, the length of the plates is less than or equal to 300mm. To achieve good heat exchange performance on such small plates, the inventors' R&D experience shows that the refrigerant-side pressure drop specifications for condensers provided by the automotive industry are typically 100kPa-300kPa, which is 10 times or more that of plate heat exchangers used in the household refrigeration and air conditioning industry. At the same time, the product flow path length is only 50% or less of the corresponding flow path length of plate heat exchangers used in the household refrigeration and air conditioning industry, resulting in a corresponding pressure drop gradient requirement of 20 times or more that used in the refrigeration and air conditioning industry. Therefore, directly citing the design ideas of plate heat exchangers used in the household refrigeration and air conditioning industry will not be able to meet the technical requirements for enhanced heat exchange in other applications of small-sized plate heat exchangers.

[0020] The plate heat exchanger of the present application utilizes a highly compact refrigerant channel structure with a favorable groove flow tendency, as well as a relatively spacious brine side channel structure, thereby facilitating the plate heat exchanger to achieve a better overall heat exchange effect. The method of the present application is described in detail below.

[0021] like Figure 1 As shown, the present application provides a plate heat exchanger 10, which includes a plurality of stacked plates, and the plurality of plates can have at least two different structures and shapes. For example, the plates can be processed and manufactured using two molds or even more sub-molds, and the present application does not impose too many restrictions on this.

[0022] The plate heat exchanger 10 may further include external pipes 11 corresponding to the inlet and outlet of two fluids, namely the refrigerant and the brine. The external pipes 11 corresponding to each fluid may be located on the same side or different sides of the thickness direction DD of the plate heat exchanger 10. Figure 1 In the figure, there are four external pipes 11, which are shown as being located on the same side of the plate heat exchanger 10, two of which serve as inlet and outlet pipes for the refrigerant, and the other two serve as inlet and outlet pipes for the brine.

[0023] The plate structure is specifically described below using one of the plates 101 of the plate heat exchanger 10 .

[0024] like Figure 2 and Figure 3 As shown, the plate 101 of the plate heat exchanger 10 provided in the present application includes a front side 1001 and a back side 1002. The edge of the plate 101 has a flange 20. The side where the flange 20 is folded is defined as the back side 1002 of the plate, and the other side is defined as the front side 1001 of the plate. Figure 2 and Figure 3 In the figure, the flange 20 is folded toward the invisible reverse side. The visible side of the plate 101 is its front side 1001 , and the other invisible side is its reverse side 1002 .

[0025] The plate 101 has a dimension of less than or equal to 300 mm in its lengthwise direction LL. The plate 101 is provided with a main heat exchange area 21. The main heat exchange area 21 can be located in the middle of the plate 101. Along the lengthwise direction LL of the plate 101, the plate also has corner hole areas 22 located on both sides of the main heat exchange area 21. The corner hole areas 22 are provided with through holes penetrating the plate 101 near the four corners of the plate 101. Fluids flow in and out through the through holes. The inlet and outlet of each fluid are located on both sides of the lengthwise direction of the plate 101. Figure 2 The four through holes at the corners of the plate, two of which (221, 222) can form the inlet and outlet of the refrigerant, and the other two (223, 224) can form the inlet and outlet of the coolant.

[0026] The plate 101 has a flat portion 210 located in the main heat exchange area 21 and a plurality of corrugated structures 211. Along the length direction LL of the plate, the plurality of corrugated structures 211 are arranged at intervals from each other and all of the plurality of corrugated structures 211 protrude relative to the flat portion 210 on the front side 1001 of the plate 101. Figure 4 The enlarged view of a portion of the front side 1001 of the plate 101 is shown, and a first groove 14 is formed between two adjacent corrugated structures 211. Figure 5The enlarged view of a portion of the reverse side 1002 of the plate 101 is shown. Each corrugated structure 211 forms a corresponding second groove 24 on the reverse side 1002 of the plate 101 .

[0027] The front and back sides of the plate 101 form corresponding circulation channels for the flow of refrigerant and the flow of secondary coolant at the main heat exchange area 21. The first groove 14 forms at least a part of the circulation channel for the flow of refrigerant, and the second groove 24 forms at least a part of the circulation channel for the flow of secondary coolant. The two circulation channels have different channel volumes. The side of the plate 101 where the circulation channel with the smaller volume is located is used for the circulation of refrigerant, that is, Figure 2 The front side 1001 of the middle plate 101; the side of the plate 101 where the larger flow channel is located is used to circulate the coolant, that is Figure 2 The reverse side 1002 of the middle plate 101. The corrugated structures 211 are arranged at a certain distance from each other on the main heat exchange area 21 of the plate 101, and the spacing between the multiple corrugated structures 211 can be equal or unequal.

[0028] The corrugated structure 211 has at least one extension section 31. The extension section 31 is tilted relative to the length direction LL of the plate 101 and is Figure 2 As shown, the angle β formed between the extension direction of the extension section 31 and the length direction LL of the plate 101 satisfies 65°≤β<90°. The extension section 31 can have a straight extension direction or an arc-shaped extension direction with a small curvature.

[0029] In some embodiments, the corrugated structure 211 may have only one extension section 31, which may extend from one edge of the plate to the other edge. When two adjacent plates 101 are assembled, the extension sections 31 of the two plates 101 are inclined toward both sides of the plate width direction, and both satisfy 65°≤β<90°. The angles of inclination of the extension sections 31 of the two plates 101 relative to the longitudinal direction LL of the plate 101 can be the same or different. For example, the angle β of the extension section 31 of one plate 101 relative to the longitudinal direction of the plate 101 is 70°, and the angle β of the extension section 31 of the other plate 101 relative to the longitudinal direction of the plate 101 is 75°.

[0030] In other embodiments, reference Figure 3 , the number of the extension sections 31 of the corrugated structure 211 is greater than or equal to 2, Figure 3In the illustration, a corrugated structure 211 is shown as having four extensions 31. Two adjacent extensions 31 are inclined toward either side of the plate's width direction WW relative to the plate's length direction LL. The angle β formed between the extension direction of each extension 31 and the plate's length direction LL satisfies 65° ≤ β < 90°. The angle β formed between the extension direction of two adjacent extensions 31 and the plate's length direction LL can be the same or different. The angle between the extension directions of two adjacent extensions 31 is 2β, meaning that the angle between the extension directions of two adjacent extensions 31 is greater than or equal to 130° and less than 180°. For example, for two adjacent extension sections 31 of the corrugated structure 211, the angle fitted in the extension direction of the two adjacent extension sections 31 is 150°, the angle β of one extension section 31 relative to the length direction of the plate 101 is 70°, and the angle β of the other extension section 31 relative to the length direction of the plate 101 is 80°, or the angle β of the two extension sections 31 relative to the length direction of the plate 101 is both 75°.

[0031] The corrugated structure 211 further includes a connecting section 32 connected to the ends of two adjacent extension sections 31 in the extension direction, so that the corrugated structure 211 extends continuously from one edge to the other edge in the width direction WW of the plate. This shape of the corrugated structure 211 can be called a herringbone wave. Figure 2 The multiplicity of the middle herringbone wave is 2. Two adjacent plates 101 are assembled in such a way that the sharp corners of the herringbone corrugations at local positions face each other, which has the technical characteristics of high turbulence and good heat exchange enhancement.

[0032] The flow of fluid through the plate 101 with a herringbone structure is divided into furrow flow along the grooves and longitudinal flow roughly along the inlet and outlet of the plate. When the angle β formed by the extension direction of the extension section 31 and the longitudinal direction LL of the plate 101 satisfies 65°≤β<90°, the refrigerant charge on the front side 1001 of the plate 101, where the refrigerant flows, is reduced, given the smaller channel volume. This also facilitates a better refrigerant flow along the first groove 14, allowing for better distribution of the refrigerant across the width direction WW of the plate 101. The flow resistance of the refrigerant along the longitudinal direction LL of the plate is greater, facilitating a higher pressure drop requirement. This results in a higher fluid heat transfer coefficient and relatively better plate heat exchange performance and efficiency.

[0033] Under the condition of limited width of the plate 101, a relatively large β angle is also beneficial to reducing the number of extension sections 31 and connecting sections 32 of each corrugated structure 211. The relatively small number of connecting sections 32 is beneficial to reducing the deflection effect of the refrigerant along the groove direction at the herringbone wave tip position, ensuring the trend of the refrigerant to move in the groove direction, which is beneficial to increasing the flow pressure drop of the refrigerant and achieving the purpose of enhancing heat exchange.

[0034] As for the opposite side 1002 of the plate 101 for the flow of the refrigerant, since the channel volume of the refrigerant itself is relatively large, in the relatively spacious circulation channel, the relatively large β angle has no obvious effect on the groove operation of the refrigerant side, and the herringbone wave tip angle position is less sensitive to the pressure drop of the fluid operation, which is conducive to the refrigerant flowing at a relatively low flow pressure drop, thereby reducing the pump power consumption of the thermal management system it is used in.

[0035] refer to Figure 4 As shown, the corrugated structure 211 is provided with a first recessed portion 41, which is recessed from the top surface of the corrugated structure 211. The first recessed portion 41 extends along the extension direction of the corrugated structure 211, and the depth D1 of the bottom of the first recessed portion 41 relative to the top surface of the corrugated structure 211 is less than the depth D2 of the flat portion 210 relative to the top surface of the corrugated structure 211.

[0036] Figure 6 for Figure 4 The cross-sectional view of the plate in the AA direction is shown, and the AA direction passes through the extension section 31 approximately perpendicularly. Along the AA direction, the plate 101 has a "one deep and one shallow" groove structure, and multiple plates 101 are assembled to form a groove structure as shown in FIG. Figure 7 Schematic cross-sectional effect.

[0037] Figure 7 In the figure, the first plate 101 and the second plate 101' are assembled. The corrugated structure 41 of the first plate 101 is convex relative to the flat portion 210 toward the side where the front surface 1001 of the plate 101 is located. The corrugated structure 41' of the second plate 101' is convex relative to the flat portion 210' toward the side where the back surface 1002 of the plate 101' is located. After assembly, Figure 5 In the figure, the larger flow space with dotted lines indicates the flow area on the refrigerant side, and the smaller flow space without dotted lines indicates the flow area on the refrigerant side. Figure 7 The corrugated structure 41' of the second plate 101' can also be provided with a first recessed portion 41', so that the cross-sections of the flow channels of the first plate 101 and the second plate 101' are mirror-symmetrical. Of course, the second plate 101' can also have other structures, for example, the channel volumes on the front and back sides of the second plate 101' are the same. As long as one of the two adjacent plates has different channel volumes on its front and back sides, it will be sufficient.

[0038] like Figure 6 As shown, the depth D2 of the flat plate portion 210 relative to the top surface of the corrugated structure 211 satisfies D2≤1.2mm. In the field of automotive air conditioning, a smaller stamping depth D2 helps meet the requirement of small plate volume, so that the assembled plate 101 forms a more compact refrigerant flow channel structure.

[0039] In some embodiments, the depth D2 of the flat portion 210 relative to the top surface of the corrugated structure 211 satisfies 0.7 mm ≤ D2 ≤ 1 mm, and the angle β formed between the extension direction of the extension section 31 and the lengthwise direction LL of the plate 101 satisfies 70° ≤ β ≤ 80°. This helps meet the high pressure drop requirement on the refrigerant side and improves the overall heat exchange performance of the plate.

[0040] The corrugated structure 211 includes two sub-portions 42 located on either side of the first recessed portion 41. The distance between the centerlines of the two sub-portions 42 adjacent to the first recessed portion 41 in the extending direction is denoted as L1. The depth of the bottom of the first recessed portion 41 relative to the top surface of the corrugated structure 211 is denoted as D1. The distance between the centerlines of the two sub-portions 42 adjacent to the flat portion 210 in the extending direction is denoted as L2. The depth of the flat portion 210 relative to the top surface of the corrugated structure 211 is denoted as D2. D1 / L1 ≥ 1 / 6, and D2 / L2 ≥ 1 / 5. For the deeper first grooves 14, the depth D2 of the flat portion 210 relative to the top surface of the corrugated structure 211 is deeper. In this deeper stamping depth region, the heat exchange area along the stamping depth direction of the first groove 14 is larger. A depth D2 of at least 1 / 5 of the length L2 facilitates the refrigerant flow to reflect a flow pattern toward the plate wall as much as possible, thereby improving the mixing effect of the gas-phase and liquid-phase working fluids and optimizing heat exchange performance. As for the shallower first recessed portion 41 , in this area with a shallower stamping depth, it is necessary to ensure a certain fluidity of the fluid, so the depth D1 is at least 1 / 6 of the length L1 .

[0041] In some embodiments, the ratio of the depth of D2 to the depth of D1 can be greater than or equal to 1.5. On the brine side, along the AA direction, the distance between the centerlines of the two flat plate sub-sections of the flat plate portion 210 separated by the corrugated structure 211 in the extending direction is L3. L3 satisfies L3 = L1 + L2, and the ratio of L3 to D1 is less than or equal to 8. The distance L3 cannot be too large to ensure the connection strength between adjacent plates forming the brine flow space. Otherwise, under certain fluid pressure, an excessively large distance L3 can easily cause plate deformation.

[0042] In the corrugated structure 211, the dimension C1 of the extended section 31 between adjacent connecting sections 32 along the plate width direction WW is greater than or equal to 12.5 mm. Under certain plate width conditions, by constraining the dimension C1 of the intact extended section 31 between adjacent connecting sections 32 along the plate width direction WW, the multiplicity of the herringbone waves can be reduced. The sharp angles of the herringbone waves force the fluid to achieve deflection, resulting in better mixing. However, the advantage is less pronounced at larger angles β. In this case, the compact channel structure and larger angle β facilitate enhanced heat exchange on the refrigerant side. Figure 2 The plate 101 shown has a double herringbone pattern, with the extension segment 31 connecting two adjacent connecting segments 32 being considered a complete extension segment. Ideally, a maximum of four complete extension segments 31 are provided for a 50 mm plate width. Of course, the plate 101 may have a total of four or fewer complete extension segments. For example, the corrugated structure 211 of the plate 101 may have only one extension segment 31, in which case a herringbone corrugated pattern is not formed.

[0043] refer to Figure 10 The plate 101 is shown as a schematic structural diagram. The plate 101 may also have two extension sections 31 and a connecting section 32 located between the two extension sections 31. One side of the extension section 31 is connected to the edge of the plate, and the other side is connected to the connecting section 32. Under ideal conditions, a maximum of two complete extension sections 31 are arranged under a plate width of 30 mm, thereby forming a single herringbone wave.

[0044] refer to Figure 11 The structural diagram of the plate 101 is shown in FIG. The extension section 31 connected between two adjacent connecting sections 32 is recorded as a complete extension section. The plate 101 can also have two complete extension sections 31 and two incomplete extension sections 31. For the complete extension section 31, as shown in FIG. Figure 11 For the second and third order extension segments 31 near the middle position along the width direction WW of the plate, the dimension C1 along the width direction WW of the plate is greater than or equal to 12.5 mm; for the incomplete extension segment 31, such as Figure 11 For the extension sections 31 connected to the edges of the plates, the dimension C2 along the width direction WW of the plates is less than or equal to C1. The multiplicity of the herringbone wave of the plate 101 is estimated to be 1.8.

[0045] In other cases, for example, the plate 101 may also have three extension segments 31 and two connecting segments 32 , and the two connecting segments 32 are respectively located between two groups of adjacent extension segments 31 , thereby roughly forming a 1.5-fold herringbone wave, etc.

[0046] The number of the first recessed portions 41 of the corrugated structure 211 ranges from 1 to 3, and when the number of the first recessed portions 41 exceeds 1, adjacent first recessed portions are spaced apart. Figure 8 The corrugated structure 211 shown is provided with two first recessed portions 41 , and the two first recessed portions 41 are spaced apart from each other.

[0047] In some other embodiments, the first recessed portion 41 may not be provided. Figure 9 In the main heat exchange area 21 on one side of the front and back sides of the plate 101, the top surface of the corrugated structure 211 forms a first area M1 for contacting other plates. In the main heat exchange area 21 on the other side of the front and back sides of the plate 101, the flat portion 210 forms a second area M2 for contacting other plates. The area of ​​the first area M1 is not equal to the area of ​​the second area M2. Figure 9 As shown, at least part of the top surface of the corrugated structure 211 is a planar area for contacting other plates. At this time, the corrugated structure 211 is not provided with a first recessed portion 41, and the area of ​​the first area M1 is not equal to the area of ​​the second area M2, so that an asymmetric channel structure can be realized, so that the channel volume on one side of the plate is smaller and the channel volume on the other side is larger.

[0048] In the plate whose length dimension is constrained to be less than or equal to 300mm, due to the different volumes of the refrigerant flow channels and the coolant flow channels formed on the front and back sides of the plate, the refrigerant flows in the smaller, i.e. more compact, flow channels to achieve a smaller refrigerant charge and better heat exchange performance. The extension section is inclined relative to the length direction of the plate at an angle β satisfying 65°≤β<90°. For the refrigerant side with a more compact channel structure, the refrigerant is more likely to flow along the channel corresponding to the extension direction of the extension section, and the corresponding refrigerant flow resistance along the length direction of the plate increases. Therefore, the relatively large β angle is conducive to meeting the technical requirements of the high-pressure drop refrigerant side, so that the refrigerant side can achieve better enhanced heat exchange. At the same time, the coolant flows in the larger, i.e. more spacious flow channels. The relatively spacious coolant flow channels are conducive to taking into account the technical requirements of low pressure drop on the coolant side, and are conducive to improving the heat exchange effect of the small-sized plate heat exchanger as a whole.

[0049] 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. The understanding of this specification should be based on technical personnel in the relevant technical field. For example, directional descriptions such as "up" and "down" are used. Although this specification has described the present application in detail with reference to the above embodiments, ordinary technical personnel in this field should understand that technical personnel in the relevant technical field can still modify or replace the present 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 plate of a plate heat exchanger, wherein the plate (101) is provided with a main heat exchange area (21), the plate (101) has corner hole areas (22) located on both sides of the main heat exchange area (21), the plate (101) has a flat portion (210) located in the main heat exchange area (21) and a plurality of corrugated structures (211); along the length direction (LL) of the plate, the plurality of corrugated structures (211) are arranged at intervals from each other and the plurality of corrugated structures (211) are all protruded relative to the flat portion (210) on the same side of the plate (101); the plate (101) has circulation channels for refrigerant flow and for coolant flow respectively formed on both sides of its main heat exchange area (21), and the channel volumes of the two circulation channels are different, wherein: The side of the plate where the circulation channel with a smaller volume is located is used for circulating refrigerant, and the side of the plate where the circulation channel with a larger volume is located is used for circulating brine; The size of the plate (101) in its length direction (LL) is less than or equal to 300 mm; the corrugated structure (211) has at least one extension section (31); the extension section (31) is arranged obliquely relative to the length direction (LL) of the plate (101), and the angle β formed by the extension direction of the extension section (31) and the length direction (LL) of the plate (101) satisfies 65°≤β<90°; the corrugated structure (211) is provided with a first recessed portion (41), the first recessed portion (41) is recessed from the top surface of the corrugated structure (211), the first recessed portion (41) extends along the extension direction of the corrugated structure (211), and the first recessed portion (41) The depth of the bottom of the first concave portion (41) relative to the top surface of the corrugated structure (211) is less than the depth of the flat portion (210) relative to the top surface of the corrugated structure (211), and the corrugated structure (211) includes two sub-portions (42) located on both sides of the first concave portion (41); the distance between the center lines of the two sub-portions (42) adjacent to the first concave portion (41) in the extension direction is recorded as L1, the depth of the bottom of the first concave portion (41) relative to the top surface of the corrugated structure (211) is recorded as D1, and the distance between the center lines of the two sub-portions (42) adjacent to the flat portion (210) in the extension direction is recorded as L2, wherein D1 / L1≥1 / 6, and D2 / L2≥1 / 5.

2. The plate according to claim 1, characterized in that The number of the extension sections (31) of the corrugated structure (211) is greater than or equal to 2, and two adjacent extension sections (31) are inclined toward both sides of the plate width direction (WW) relative to the length direction (LL) of the plate (101); the corrugated structure (211) further includes a connecting section (32) connected to the ends of the two adjacent extension sections (31) in the extension direction; the corrugated structure (211) extends in a continuous form from one side edge to the other side edge in the plate width direction (WW).

3. The plate according to claim 1, characterized in that The depth of the flat plate portion (210) relative to the top surface of the corrugated structure (211) is recorded as D2, where D2≤1.2 mm.

4. The plate according to claim 3, characterized in that The depth D2 of the flat plate portion (210) relative to the top surface of the corrugated structure (211) satisfies 0.7 mm ≤ D2 ≤ 1 mm; and the angle (β) formed by the extension direction of the extension section (31) and the length direction (LL) of the plate satisfies 70° ≤ β ≤ 80°.

5. The plate according to claim 2, characterized in that In the corrugated structure (211), for the extension section (31) located between adjacent connecting sections (32), its dimension C1 along the width direction (WW) of the plate satisfies C1≥12.5 mm.

6. The plate according to claim 1, characterized in that At the main heat exchange area (21) on one of the front and back sides of the plate (101), the top surface of the corrugated structure (211) forms a first area (M1) for contacting other plates; at the main heat exchange area (21) on the other of the front and back sides of the plate (101), the flat portion (210) forms a second area (M2) for contacting other plates; the area of ​​the first area (M1) is not equal to the area of ​​the second area (M2).

7. The plate according to claim 1, characterized in that The number of the first recessed portions (41) of each corrugated structure (211) ranges from 1 to 3, and when the number of the first recessed portions (41) exceeds 1, adjacent first recessed portions (41) are arranged at intervals.

8. A plate heat exchanger, characterized in that: The plate heat exchanger (10) is applied to an automobile air-conditioning thermal management system, and the plate heat exchanger (10) comprises at least one plate according to any one of claims 1 to 7.

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