Plate sheet of plate heat exchanger and plate heat exchanger

Abstract

The invention provides a sheet bar. The size of the sheet bar in the length direction is smaller than or equal to 300 mm. The plate sheet is provided with a main heat exchange area, and is provided with a flat plate part and a plurality of corrugated structures which are positioned in the main heat exchange area; the plurality of corrugated structures are arranged at intervals and protrude relative to the flat plate part; the front side and the back side of each plate correspondingly form a circulation channel for a refrigerant to flow and a circulation channel for a secondary refrigerant to flow in the main heat exchange area of the plate, the channel volumes of the two circulation channels are different, the side, where the circulation channel with the smaller volume of the plate is located, of the plate is used for circulation of the refrigerant, and the side, where the circulation channel with the larger volume of the plate is located, of the circulation channel is used for circulation of the secondary refrigerant. The corrugated structure is provided with at least one extension section; the extension section is obliquely arranged relative to the length direction of the sheet bar, and an included angle beta formed between the extension direction of the extension section and the length direction of the sheet bar is greater than or equal to 65 degrees and less than 90 degrees. The plate heat exchanger applying the plate sheet is good in overall heat exchange performance under the condition of small-size plate sheets, and fluid pressure drop is considered at the same time.

Description

Technical Field

[0001] This application relates to the field of heat exchange technology, and more particularly to a plate heat exchanger plate and a plate heat exchanger. Background Technology

[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 of plate heat exchangers. In small-sized plate heat exchanger products, how to balance heat exchange efficiency and fluid pressure drop is a major challenge. Summary of the Invention

[0003] On one hand, this application provides a plate for a plate heat exchanger, the plate having a main heat exchange zone, the plate having a flat plate portion located in the main heat exchange zone and multiple corrugated structures; along the length of the plate, the multiple corrugated structures are arranged at intervals and each of the multiple corrugated structures protrudes from the flat plate portion on the same side of the plate; on the front and back sides of the plate, flow channels for refrigerant flow and flow channels for secondary refrigerant flow are respectively formed in the main heat exchange zone, and the channel volumes of the two flow channels are different, the side with the smaller flow channel volume is used for refrigerant flow, and the side with the larger flow channel volume is used for secondary refrigerant flow;

[0004] The plate has a length dimension of less than or equal to 300 mm; the corrugated structure has at least one extension segment; the extension segment is inclined relative to the length direction of the plate, and the angle β formed by the extension direction of the extension segment and the length direction of the plate satisfies 65°≤β<90°.

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

[0006] In plates with a length dimension of 300 mm or less, the refrigerant flow channels and coolant flow channels formed on the front and back sides of the plate have different volumes. The refrigerant flows in the smaller, more compact flow channels to achieve a smaller refrigerant charge and to improve the heat transfer coefficient of the refrigerant-side fluid, thus achieving better heat transfer performance. The extension section is inclined relative to the length of the plate with an angle β of 65°≤β<90°. For the refrigerant side, where the channel structure is relatively compact, the refrigerant flows more easily along the channel corresponding to the extension direction of the extension section. Consequently, the flow resistance of the refrigerant along the length of the plate increases. Therefore, the relatively large angle β is beneficial to meeting the technical requirements of high pressure drop on the refrigerant side, enabling the refrigerant side to achieve better heat exchange enhancement. At the same time, the refrigerant flows in a larger volume, i.e., a more spacious flow channel. The relatively spacious refrigerant flow channel is beneficial to achieving the technical requirements of low pressure drop on the refrigerant side. Through the above arrangement, it is beneficial for plate heat exchangers using this type of plate to meet the requirements of small size while taking into account heat exchange efficiency and fluid pressure drop. Attached Figure Description

[0007] Figure 1 This is a schematic diagram of the structure of a plate heat exchanger according to an embodiment of this application;

[0008] Figure 2 This is a schematic diagram of the structure of a plate in one embodiment of this application;

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

[0010] Figure 4 yes Figure 2 An enlarged schematic diagram of the front part of the schematic plate;

[0011] Figure 5 yes Figure 2 A magnified schematic diagram of the reverse side of the schematic plate;

[0012] Figure 6 yes Figure 4 A schematic cross-sectional view of the plate along the AA direction;

[0013] Figure 7 This is a schematic diagram of a cross-sectional effect of the plate heat exchanger after the two plates are assembled according to the embodiments of this application;

[0014] Figure 8 This is a schematic diagram of another cross-sectional effect of the plate heat exchanger after the two plates are assembled according to the embodiments of this application;

[0015] Figure 9This is a schematic diagram of another cross-sectional effect of the plate heat exchanger after the two plates are assembled according to the embodiments of this application;

[0016] Figure 10 This is a schematic diagram of another plate structure in an embodiment of this application;

[0017] Figure 11 This is a schematic diagram of another type of plate structure in the embodiments of this application. Detailed Implementation

[0018] In residential air conditioning systems, plate heat exchangers are typically large in size, for example, with plate lengths exceeding 500 mm. Based on the inventor's research experience in the residential air conditioning field, to achieve heat exchange, the pressure drop on the refrigerant side is usually between 10 kPa and 30 kPa. Due to the large size of the products, and considering the long distance between the two corner holes of the refrigerant inlet and outlet on the plates—a key factor affecting heat exchange—the pressure drop gradient for heat exchange in plate heat exchangers is relatively low. Therefore, under the constraint of relatively low pressure drop parameters, large-size plate heat exchangers do not require extremely compact channel structures to meet pressure drop requirements.

[0019] In the field of small-sized plate heat exchangers, such as automotive air conditioning, the compact size of automotive products necessitates smaller overall dimensions for these plate heat exchangers. For example, the length of the plates is typically 300mm or less. Achieving good heat exchange on such small plates requires significant investment. Based on the inventor's research experience, the refrigerant-side pressure drop of condensers in the automotive industry is usually 100kPa-300kPa, which is 10 times or more than that of plate heat exchangers used in the residential air conditioning industry. Simultaneously, the flow channel length is only 50% or less of that of plate heat exchangers used in the residential air conditioning industry, resulting in a pressure drop gradient requirement that is 20 times or more. Therefore, directly adopting the design principles of plate heat exchangers used in the residential air conditioning industry is insufficient to address the technical requirements for enhanced heat exchange in other applications using small-sized plate heat exchangers.

[0020] The plate heat exchanger of this application employs a highly compact refrigerant channel structure with good channel-to-channel flow characteristics, as well as a relatively spacious refrigerant-side channel structure, thereby contributing to a better overall heat exchange performance. The method of this application will now be described in detail.

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

[0022] For the plate heat exchanger 10 product, it may also include external connecting pipes 11 corresponding to the inlet and outlet of two fluids, namely refrigerant and secondary refrigerant. The external connecting 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 plate heat exchanger 10, there are 4 external pipes 11, which are shown on the same side of the plate heat exchanger 10. Two of them are used as refrigerant inlet and outlet pipes, and the other two are used as heat transfer fluid inlet and outlet pipes.

[0023] The following is a detailed description of the plate structure using one of the plates 101 of the plate heat exchanger 10.

[0024] like Figure 2 and Figure 3 As shown, the plate heat exchanger 10 provided in this application has plates 101, each including a front side 1001 and a back side 1002. The edges of the plates 101 have flanges 20. The side where the flange 20 is folded is defined as the back side 1002 of the plate, and conversely, the other side is the front side 1001 of the plate. Figure 2 and Figure 3 In the middle, the flange 20 is folded towards the invisible reverse side, and the visible side of the plate 101 is its front 1001, and the invisible side is its reverse 1002.

[0025] Plate 101 has a length LL of less than or equal to 300 mm. Plate 101 has a main heat exchange zone 21. The main heat exchange zone 21 can be located in the middle of plate 101. Along the length LL of plate 101, the plate also has corner hole zones 22 located on both sides of the main heat exchange zone 21. The corner hole zones 22 have through holes near the four corners of plate 101, allowing fluid to flow in and out. The inlet and outlet for each fluid are located on both sides of the length of plate 101. Figure 2 The plate has four through holes at the corners, two of which (221, 222) can form the inlet and outlet of the refrigerant, while the other two corner holes (223, 224) form the inlet and outlet of the secondary refrigerant.

[0026] Plate 101 has a flat plate portion 210 located in the main heat exchange zone 21 and a plurality of corrugated structures 211. Along the length direction LL of the plate, the plurality of corrugated structures 211 are spaced apart from each other, and each of the corrugated structures 211 protrudes from the flat plate portion 210 on one side of the front surface 1001 of the plate 101. (Reference) Figure 4 The enlarged view of a portion of the front side 1001 of the plate 101 shown shows a first groove 14 formed between two adjacent corrugated structures 211. (Refer to...) Figure 5The enlarged view of a portion of the reverse side 1002 of the plate 101 shown shows that each corrugated structure 211 forms a second groove 24 on the reverse side 1002 of the plate 101.

[0027] On both sides of the plate 101, flow channels for refrigerant flow and secondary refrigerant flow are respectively formed in the main heat exchange zone 21. The first groove 14 forms at least a portion of the flow channel for refrigerant flow, and the second groove 24 forms at least a portion of the flow channel for secondary refrigerant flow. These two flow channels have different volumes; the side of the plate 101 with the smaller volume of the flow channel is used for refrigerant flow. Figure 2 The front side 1001 of the middle plate 101; the side of the plate 101 with the larger flow channel is used for the flow of refrigerant, i.e. Figure 2 On the reverse side 1002 of the middle plate 101. Corrugated structures 211 are arranged at a certain distance from each other on the main heat exchange zone 21 of the plate 101. The spacing between multiple corrugated structures 211 can be equal or unequal.

[0028] The corrugated structure 211 has at least one extension 31. The extension 31 is inclined relative to the length direction LL of the plate 101, and references... Figure 2 As shown, the angle β formed by the extension direction of the extension segment 31 and the length direction LL of the plate 101 satisfies 65°≤β<90°. The extension segment 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 31, which may extend from one edge of the plate to the other edge. When two adjacent plates 101 are assembled, the extensions 31 of the two plates 101 are inclined to both sides in the width direction of the plate, and both satisfy 65°≤β<90°. The angles at which the extensions 31 of the two plates 101 are inclined relative to the length direction LL of the plate 101 may be the same or different. For example, the angle β of the extension 31 of one plate 101 relative to the length direction of the plate 101 is 70°, and the angle β of the extension 31 of the other plate 101 relative to the length direction of the plate 101 is 75°.

[0030] In other embodiments, refer to Figure 3 The number of extension segments 31 of the corrugated structure 211 is greater than or equal to 2. Figure 3The corrugated structure 211 is illustrated by having four extension segments 31. Two adjacent extension segments 31 are inclined to either side of the width direction WW of the plate relative to the length direction LL of the plate. The angle β formed by the extension direction of each extension segment 31 and the length direction LL of the plate 101 satisfies 65° ≤ β < 90°. The angle β formed by the extension direction of two adjacent extension segments 31 and the length direction LL of the plate 101 can be the same or different. The angle between the extension directions of two adjacent extension segments 31 is 2β, meaning the angle between the extension directions of two adjacent extension segments 31 is greater than or equal to 130° and less than 180°. For example, for two adjacent extensions 31 of the corrugated structure 211, the included angle of the extension directions of the two adjacent extensions 31 is 150°, one extension 31 has an included angle β of 70° with respect to the length direction of the plate 101, the other extension 31 has an included angle β of 80° with respect to the length direction of the plate 101, or both extensions 31 have included angles β of 75° with respect to the length direction of the plate 101.

[0031] The corrugated structure 211 also includes a connecting segment 32 connecting the ends of two adjacent extension segments 31 in the extending direction, so that the corrugated structure 211 extends in a continuous form from one edge of the plate width direction WW to the other edge. This corrugated structure 211 can be called a herringbone wave. Figure 2 The herringbone wave has a double degree. Adjacent plates 101 are assembled by having the herringbone corrugated sharp corners facing each other at local locations, which has the technical characteristics of high turbulence and good heat transfer effect.

[0032] The flow pattern of the fluid in the plate 101 with its herringbone structure is decomposed into furrow flow along the channel and longitudinal flow approximately between the inlet and outlet of the plate. When 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°, on the side of the plate 101 where the refrigerant flows, based on the premise of a smaller channel volume, it is beneficial to reduce the refrigerant charge and to allow the refrigerant to achieve a better flow pattern along the first groove 14. The refrigerant can be better distributed in the width direction WW of the plate 101. The flow resistance of the refrigerant along the length direction LL of the plate is relatively large, which is beneficial to meet the larger flow pressure drop index, resulting in a higher fluid heat transfer coefficient and relatively better plate heat transfer performance and efficiency.

[0033] Under the condition of limited plate width 101, a relatively large β angle is also conducive 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 conducive to reducing the deflection effect of refrigerant along the channel at the herringbone tip position, ensuring the refrigerant channel movement trend, which is conducive to improving the flow pressure drop of refrigerant and achieving the purpose of enhancing heat transfer.

[0034] As for the opposite side 1002 of the plate 101 where the refrigerant flows, since the channel volume of the refrigerant itself is large, the relatively large β angle has little effect on the channel direction of the refrigerant in the relatively spacious flow channel. The position of the V-shaped apex is also less sensitive to the pressure drop of the fluid, which is conducive to the refrigerant flowing with 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. The first recessed portion 41 is recessed from the top surface of the corrugated structure 211 and extends along the extension direction of the corrugated structure 211. 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 plate portion 210 relative to the top surface of the corrugated structure 211.

[0036] Figure 6 for Figure 4 The diagram shows a cross-sectional view of the plate 101 along the AA direction, which is approximately perpendicular to the extension section 31. Along the AA direction, the plate 101 has a channel structure with alternating deep and shallow grooves. Multiple plates 101 assembled together form a... Figure 7 A schematic cross-sectional effect.

[0037] Figure 7 The diagram illustrates the assembly of a first plate 101 and a second plate 101'. The corrugated structure 41 of the first plate 101 protrudes relative to the flat plate 210 towards the side where the front surface 1001 of the plate 101 is located, while the corrugated structure 41' of the second plate 101' protrudes relative to its flat plate 210' towards the side where the back surface 1002 of the plate 101' is located. After assembly, Figure 5 The larger flow space with dashed lines indicates the flow area on the refrigerant side, while the smaller flow space without dashed lines indicates the flow area on the refrigerant side. Figure 7 The corrugated structure 41' of the second plate 101' can also be made so that the cross-sections of the flow channels of the first plate 101 and the second plate 101' are mirror-symmetrical by setting the first recess 41'. Of course, the second plate 101' can also be a plate with other structures, such as the same channel volume on both sides of the second plate 101'. As long as one of the two adjacent plates satisfies that the channel volumes on both sides of its front and back are different, it is acceptable.

[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 is beneficial to meeting the requirement of small plate size, so that the assembled plate 101 forms a more compact refrigerant flow channel structure.

[0039] In some embodiments, the depth D2 of the flat plate portion 210 relative to the top surface of the corrugated structure 211 satisfies 0.7mm≤D2≤1mm, and the angle β formed by the extension direction of the extension section 31 and the length direction LL of the plate 101 satisfies 70°≤β≤80°. This is beneficial for meeting the high pressure drop requirements on the refrigerant side, and the overall heat exchange effect of the plate is better.

[0040] The corrugated structure 211 includes two sub-sections 42 located on both sides of the first recess 41. The distance between the center lines extending in the direction of the two sub-sections 42 adjacent to the first recess 41 is denoted as L1. The depth of the bottom of the first recess 41 relative to the top surface of the corrugated structure 211 is denoted as D1. The distance between the center lines extending in the direction of the two sub-sections 42 adjacent to the flat plate 210 is denoted as L2. The depth of the flat plate 210 relative to the top surface of the corrugated structure 211 is denoted as D2, where D1 / L1≥1 / 6 and D2 / L2≥1 / 5. For the deeper first groove 14, the depth D2 of the flat plate 210 relative to the top surface of the corrugated structure 211 is relatively deep. In this region with a relatively deep stamping depth, the heat transfer area along the stamping depth direction of the first groove 14 is relatively large. The depth of D2 is at least 1 / 5 of the length of L2, which helps to make the refrigerant flow as close as possible to the plate wall. This is beneficial to improving the mixing effect of the gaseous and liquid working fluids and optimizing the heat transfer performance. For the shallower first recess 41, in this area with a shallower stamping depth, it is necessary to ensure a certain fluidity. Therefore, the depth of D1 must be at least 1 / 6 of the length of 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. For the refrigerant side, along the AA direction, the distance between the center lines of the two plate sub-sections of the plate portion 210 separated by the corrugated structure 211 extending in the direction of extension 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, and it is necessary to ensure the connection strength between adjacent plates forming the refrigerant flow space. Otherwise, under a certain fluid pressure, an excessively large distance L3 can easily cause plate deformation.

[0042] In the corrugated structure 211, the extension 31 located between adjacent connecting sections 32 has a dimension C1 in the width direction WW of the plate greater than or equal to 12.5 mm. Under certain plate width conditions, by constraining the dimension C1 of the complete extension 31 connected between adjacent connecting sections 32 in the width direction WW of the plate, the number of herringbone waves can be reduced. The sharp corners of the herringbone waves force the fluid to achieve a baffle effect, resulting in a better mixing effect. However, this advantage is not obvious at a large β angle. At this time, the compact channel structure and the large β angle are conducive to enhanced heat transfer on the refrigerant side. Figure 2 The plate 101 shown has a double herringbone wave pattern. An extension segment 31 connecting two adjacent connecting segments 32 is considered a complete extension segment. Under ideal conditions with a plate width of 50mm, a maximum of four complete extension segments 31 can be arranged. Of course, the number of complete extension segments corresponding to the plate 101 can be less than or equal to four. For example, the corrugated structure 211 of the plate 101 can have only one extension segment 31, in which case it does not constitute a herringbone wave pattern.

[0043] refer to Figure 10 The diagram shows the structure of the plate 101. The plate 101 may also have two extension segments 31 and a connecting segment 32 located between the two extension segments 31. One side of the extension segment 31 is connected to the edge of the plate, and the other side is connected to the connecting segment 32. Under ideal conditions with a plate width of 30mm, a maximum of two complete extension segments 31 can be arranged to form a single herringbone wave.

[0044] refer to Figure 11 The diagram shows the structure of the plate 101. An extension segment 31 connecting two adjacent connecting segments 32 is considered a complete extension segment. The plate 101 may also have two complete extension segments 31 and two incomplete extension segments 31. Corresponding to the complete extension segments 31, as shown... Figure 11 For the second and third sequence extensions 31 located near the middle position along the width direction WW of the plate, their dimension C1 along the width direction WW satisfies greater than or equal to 12.5 mm; for the extensions 31 in the incomplete form, such as Figure 11 For the extensions 31 that are connected to the edges of the plate, the dimension C2 of the extensions WW along the width direction of the plate is less than or equal to C1. The weight of the herringbone wave of the plate 101 is estimated to be 1.8 times herringbone wave.

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

[0046] The number of first recesses 41 in the corrugated structure 211 ranges from one to three, and when the number of first recesses 41 exceeds one, adjacent first recesses are spaced apart. For example... Figure 8 The corrugated structure 211 shown has two first recesses 41, which are spaced apart from each other.

[0047] In some other embodiments, the first recess 41 may not be provided, see reference. Figure 9 On one side of the main heat exchange zone 21 of the plate 101, the top surface of the corrugated structure 211 forms a first region M1 for contact with other plates. On the other side of the main heat exchange zone 21 of the plate 101, the flat plate portion 210 forms a second region M2 for contact with other plates. The areas of the first region M1 and the second region M2 are not equal. Specifically, refer to... Figure 9 As shown, at least a portion of the top surface of the corrugated structure 211 is a planar area for contact with other plates. In this case, the corrugated structure 211 does not have a first recess 41. The area of ​​the first region M1 is not equal to the area of ​​the second region M2, which can also realize an asymmetrical channel structure, 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 plates with a length constraint of 300 mm or less, the refrigerant flow channels and coolant flow channels formed on the front and back of the plate have different volumes. The refrigerant flows in the smaller, more compact flow channels to achieve a smaller refrigerant charge and better heat exchange performance. The extension section is inclined relative to the length of the plate with an angle β of 65°≤β<90°. For the refrigerant side with a more compact channel structure, the refrigerant flows more easily in the channel corresponding to the extension direction of the extension section. Consequently, the flow resistance of the refrigerant along the length of the plate increases. The relatively larger β angle is beneficial to meeting the technical requirements of high pressure drop on the refrigerant side, enabling the refrigerant side to achieve better enhanced heat exchange. At the same time, the coolant flows in the larger, more spacious flow channels. The relatively spacious coolant flow channels are beneficial to meeting the technical requirements of low pressure drop on the coolant side, which is conducive to improving the heat exchange effect of small-sized plate heat exchangers as a whole.

[0049] The above embodiments are only used to illustrate this application and are not intended to limit the technical solutions described in this application. The understanding of this specification should be based on those skilled in the art. For example, directional descriptions such as "upper" and "lower" are used. Although this specification has described this application in detail with reference to the above embodiments, those skilled in the art should understand that they can still make modifications or equivalent substitutions to this application. All technical solutions and improvements that do not depart from the spirit and scope of this application should be covered within the scope of the claims of this application.

Claims

1. A plate heat exchanger (10) used in an automotive air conditioning thermal management system, the plate heat exchanger (10) comprising plates (101), a plurality of the plates (101) being stacked along the thickness direction (DD) of the plate heat exchanger (10), the plates (101) having a main heat exchange zone (21), the plates (101) having a flat plate portion (210) located in the main heat exchange zone (21) and a plurality of corrugated structures (211); along the plate (101) 1) Along the length direction (LL), a plurality of the corrugated structures (211) are arranged at intervals and the plurality of the corrugated structures (211) protrude from the flat plate (210) on the same side of the plate (101); on the front and back sides of the plate (101), flow channels for refrigerant flow and flow channels for secondary refrigerant flow are respectively formed in the main heat exchange area (21), the side with the smaller flow channel is used for refrigerant flow and the side with the larger flow channel is used for secondary refrigerant flow; The plate (101) has a length (LL) dimension of less than or equal to 300 mm; the corrugated structure (211) has at least one extension (31); the extension (31) is inclined relative to the length (LL) of the plate (101), and the angle β formed by the extension direction of the extension (31) and the length (LL) of the plate (101) satisfies 65°≤β<90°.

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

3. The plate heat exchanger according to claim 2, characterized in that, The corrugated structure (211) is provided with a first recess (41), which is recessed from the top surface of the corrugated structure (211). The first recess (41) extends along the extension direction of the corrugated structure (211), and the depth of the bottom of the first recess (41) relative to the top surface of the corrugated structure (211) is less than the depth of the flat plate portion (210) relative to the top surface of the corrugated structure (211).

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

5. The plate heat exchanger according to claim 4, characterized in that, The depth D2 of the flat plate (210) relative to the top surface of the corrugated structure (211) satisfies 0.7mm≤D2≤1mm; 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°.

6. The plate heat exchanger according to claim 3, characterized in that, The corrugated structure (211) includes two sub-sections (42) located on both sides of the first recess (41); the distance between the center lines of the two sub-sections (42) adjacent to the first recess (41) in the extension direction is denoted as L1, the depth of the bottom of the first recess (41) relative to the top surface of the corrugated structure (211) is denoted as D1, and the distance between the center lines of the two sub-sections (42) adjacent to the flat plate (210) in the extension direction is denoted as L2, wherein D1 / L1≥1 / 6, D2 / L2≥1 / 5.

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

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

9. The plate heat exchanger according to claim 3, characterized in that, The number of the first recesses (41) in each corrugated structure (211) ranges from 1 to 3, and when the number of the first recesses (41) exceeds 1, the adjacent first recesses (41) are spaced apart.

10. A plate heat exchanger, characterized in that, The plate (101) is provided with a main heat exchange zone (21). The plate (101) has corner hole areas (22) located on both sides of the main heat exchange zone (21). The plate (101) has a flat plate portion (210) located in the main heat exchange zone (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 and all the corrugated structures (211) protrude from the flat plate portion (210) on the same side of the plate (101). On the front and back sides of the plate (101), flow channels for refrigerant flow and flow channels for secondary refrigerant flow are respectively formed in the main heat exchange zone (21). The side with the smaller flow channel of the plate is used for refrigerant flow, and the side with the larger flow channel of the plate is used for secondary refrigerant flow. The plate (101) has a length (LL) dimension of less than or equal to 300 mm; the corrugated structure (211) has at least one extension (31); the extension (31) is inclined relative to the length (LL) of the plate (101), and the angle β formed by the extension direction of the extension (31) and the length (LL) of the plate (101) satisfies 65°≤β<90°.

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