Plate Heat Exchanger

Abstract

The present application provides a plate heat exchanger, comprising a first plate and a second plate, each plate having a plurality of corrugated structures arranged at intervals in the main heat exchange area, and the plate having a plurality of crests and a plurality of troughs in the main heat exchange area; the corrugated structure having at least two straight sections and a curved section; the corrugated structure comprising a first connecting wall and two side walls; the two side walls comprising a first side wall and a second side wall; at least one of the second side walls forms a concave portion concave in the direction of the corner of the herringbone corrugation in at least part of the curved section, and the slope of the second side wall corresponding to the concave portion is smaller than the slope of other positions of the second side wall; and / or at least one of the first side walls forms a convex portion protruding in the direction of the corner of the herringbone corrugation in at least part of the curved section, and the slope of the first side wall corresponding to the convex portion is smaller than the slope of other positions of the first side wall. The present application is conducive to improving the heat exchange performance of the plate heat exchanger.

Description

Technical Field

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

[0002] The plate heat exchanger is a highly efficient and compact heat exchanger widely used in refrigeration and air conditioning, new energy vehicles and other industries. In the related art, the plates of the plate heat exchanger are provided with a herringbone wave pattern. When adjacent plates are welded, the sharp corners of the herringbone wave pattern of the plate are usually the weak link of fluid flow. The fluid has poor fluidity at the sharp corners, which easily causes the fluid to be unevenly distributed on the plate. This unevenness reduces the effective heat exchange area of ​​the plate, that is, the plate surface utilization rate is low. This affects the heat exchange performance of the plate heat exchanger. Summary of the invention

[0003] The present application provides a plate heat exchanger, comprising a plurality of plates, wherein the plurality of plates comprise a plurality of first plates and a plurality of second plates, wherein the plurality of first plates and the plurality of second plates are alternately arranged to form two non-connected fluid flow channels, wherein each plate comprises a first heat exchange surface and a second heat exchange surface opposite to each other, wherein the first heat exchange surface of the first plate is opposite to the second heat exchange surface of the second plate, and the second heat exchange surface of the first plate is opposite to the first heat exchange surface of the second plate; wherein each plate is provided with a main heat exchange area, wherein the plate is provided with a plurality of corrugated structures arranged at intervals along the length direction of the plate, wherein the plate has a plurality of crests and a plurality of troughs in the main heat exchange area, wherein the plurality of crests and the plurality of troughs are alternately arranged, and two adjacent troughs have the same or different depths relative to the crests located therebetween;

[0004] The corrugated structure has at least two straight sections and one curved section in the width direction of the plate; the curved section is connected between two adjacent straight sections, and the extension directions of the two adjacent straight sections intersect, so that the two adjacent straight sections and the curved section located therebetween are matched to form a herringbone corrugation, and the curved section forms the corner of the herringbone corrugation;

[0005] The corrugated structure comprises a first connecting wall and two side walls, at least a portion of the first connecting wall forms the wave crest, and the plate surface between adjacent corrugated structures forms the wave trough; the two side walls are respectively connected to both sides of the first connecting wall to achieve connection between the wave crest and the wave troughs on both sides thereof; in the direction of the corner of the herringbone corrugation, the two side walls comprise a first side wall forming the front edge of the herringbone corrugation, and a second side wall forming the rear edge of the herringbone corrugation;

[0006] Wherein, at least one of the second side walls forms a recessed portion in at least a portion of the curved section, which is recessed in the direction of the corner of the herringbone corrugation, and relative to the plane where the crest is located, the slope of the second side wall corresponding to the recessed portion is smaller than the slope of other positions of the second side wall, and the depression corresponding to the recess on one side of the first heat exchange surface and the second heat exchange surface of the plate forms a part of the fluid channel for the flow of the first fluid; and / or, at least one of the first side walls forms a convex portion in at least a portion of the curved section, which is protruding in the direction of the corner of the herringbone corrugation, and relative to the plane where the crest is located, the slope of the first side wall corresponding to the convex portion is smaller than the slope of other positions of the first side wall, and the depression corresponding to the convex portion on the other side of the first heat exchange surface and the second heat exchange surface of the plate forms a part of the fluid channel for the flow of the second fluid.

[0007] The present application improves the channel structure formed by the plates of the plate heat exchanger. The concave portion is conducive to expanding the flow cross-section of the first fluid at the herringbone wave corner, and the convex portion is conducive to expanding the flow cross-section of the second fluid at the herringbone wave corner. The relatively large fluid flow cross-section reduces the influence of the welding points of the bending section on the fluid fluidity, improves the fluidity of the fluid in the middle part of the herringbone corrugated pattern, and further improves the uniformity of the distribution of the fluid on the plates of the plate heat exchanger, thereby improving the heat exchange performance of the plate heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 A schematic diagram of the structure of the plate heat exchanger provided for this application;

[0009] Figure 2 A schematic diagram of the structure of the first plate provided in this application;

[0010] Figure 3 For this application Figure 2 An enlarged schematic diagram of the structure of the first heat exchange surface of the first plate;

[0011] Figure 4 For this application Figure 2 An enlarged schematic diagram of a single corrugated structure of the first plate;

[0012] Figure 5 For this application Figure 2 A partial cross-sectional schematic diagram of a plurality of straight sections continuous in the length direction of the first plate;

[0013] Figure 6 A schematic diagram of an assembly structure of a first plate and a second plate provided in the present application;

[0014] Figure 7 A schematic diagram of another assembly structure of a first plate and a second plate provided in the present application;

[0015] Figure 8A schematic cross-sectional view of a plurality of continuous straight sections in the length direction of a first plate with an asymmetric corrugated structure provided by the present application;

[0016] Fig. 9 A schematic cross-sectional view of a plurality of continuous straight sections in the length direction of a second plate with an asymmetric corrugated structure provided by the present application;

[0017] Fig.10 A schematic diagram of the assembly structure of a first plate and a second plate with an asymmetric corrugated structure provided in the present application. DETAILED DESCRIPTION

[0018] In the related art, when two plates of a plate heat exchanger are stacked together, there is generally a large welding point at the sharp corner of the herringbone wave pattern, which results in less fluid flow at the sharp corner, or even no fluid passing through to form a flow dead zone, resulting in uneven distribution of fluid flow on the plate, reducing the heat exchange performance of the plate heat exchanger. The plate heat exchanger provided by the present application improves the channel structure formed by the corrugated structure on the plate, which is conducive to reducing the distribution difficulty of the fluid when it flows near the curved section of the corrugated structure, improving the uniformity of the fluid flow on the plate, and thus improving the heat exchange performance of the plate heat exchanger.

[0019] like Figures 1 to 10 As shown, an embodiment of the present application provides a plate heat exchanger 10, including a plurality of plates 100, the plurality of plates 100 including a plurality of first plates 101 and a plurality of second plates 102, the plurality of first plates 101 and the plurality of second plates 102 are alternately arranged to form two non-connected fluid flow channels, each plate 100 includes a first heat exchange surface 1001 and a second heat exchange surface 1002 relative to each other, the first heat exchange surface 1001 of the first plate 101 is opposite to the second heat exchange surface 1002 of the second plate 102, and the second heat exchange surface 1002 of the first plate 101 is opposite to the first heat exchange surface 1001 of the second plate 102.

[0020] Of course, the plate heat exchanger 10 product may also include external pipes 11 corresponding to the two fluids. The external pipes 11 corresponding to the two fluids may be located on the same side or different sides in the thickness direction of the plate heat exchanger 10. Figure 1 In the figure, the external pipes 11 are shown as being located on different sides of the plate heat exchanger 10. The number of the external pipes 11 may be four, two of which serve as inlet and outlet pipes of the first fluid, and the other two serve as inlet and outlet pipes of the second fluid.

[0021] Each plate 100 has a main heat exchange zone 1, refer to Figure 2The structure of the first plate 101 is schematically shown. In the main heat exchange zone 1, the plate 101 is provided with a plurality of corrugated structures 2 arranged at intervals along the length direction of the plate. The plate 101 has a plurality of crests 21 and a plurality of troughs 22 in the main heat exchange zone 1. The plurality of crests 21 and the plurality of troughs 22 are alternately arranged, and two adjacent troughs 22 have the same or different depths relative to the crest 21 located therebetween.

[0022] The corrugated structures 2 are arranged on the plate 101 at a certain distance from each other, and the intervals between the multiple corrugated structures 2 can be equal or unequal.

[0023] refer to Figure 2 , Figure 4 Each corrugated structure 2 has at least two straight sections 23 and one curved section 24 in the width direction of the plate 100. The curved section 24 is connected between two adjacent straight sections 23, and the extension directions of the two adjacent straight sections 23 intersect, so that the two adjacent straight sections 23 and the curved section 24 located therebetween are matched to form a herringbone corrugation, and the curved section 24 forms the corner of the herringbone corrugation.

[0024] refer to Figure 3 In the enlarged schematic diagram, the corrugated structure 2 includes a first connecting wall 25 and two side walls 26, at least part of the first connecting wall 25 forms a crest 21, and the plate surface between adjacent corrugated structures 2 forms a trough 22. The two side walls 26 are respectively connected to the two sides of the first connecting wall 25 to achieve the connection between the crest 21 and the troughs 22 on both sides thereof. In the direction of the corner of the herringbone corrugation, the two side walls 26 include a first side wall 261 forming the front edge of the herringbone corrugation, and a second side wall 262 forming the rear edge of the herringbone corrugation. The direction of the corner of the herringbone corrugation roughly coincides with the approximate angle bisector of the corner of the herringbone corrugation, and its direction is the direction of the sharp corner of the herringbone corrugation.

[0025] For the two side walls 26, if the corrugated structure 2 is a multiple herringbone wave structure, each side wall 26 can be either the first side wall 261 or the second side wall 262 in the width direction of the plate, and the side wall 26 does not become one of the first side wall 261 and the second side wall 262 alone. The first side wall 261 and the second side wall 262 are local concepts corresponding to the herringbone corrugation. The first side wall 261 and the second side wall 262 are distinguished as the leading edge and the trailing edge of the herringbone corrugation. That is to say, for a side wall 26, if it forms the leading edge of the herringbone corrugation at a certain position, it is the first side wall 261, and if the side wall 26 forms the trailing edge of the herringbone corrugation at another position, it is the second side wall 262.

[0026] Wherein, at least one second side wall 262 forms a recess 263 in the direction of the corner of the herringbone corrugation in at least a part of the curved section 24, and the slope of the second side wall 262 corresponding to the recess 263 is smaller than the slope of other positions of the second side wall 262 relative to the plane where the crest 21 is located, and the recess 263 corresponding to one side of the first heat exchange surface 1001 and the second heat exchange surface 1002 of the plate 100 can form a part of the fluid channel for the first fluid to flow; and / or , at least one of the first side walls 261 forms a convex portion 264 protruding in the direction of the corner of the herringbone corrugation in at least part of the curved section 24, and relative to the plane where the wave crest 21 is located, the slope of the first side wall 261 corresponding to the position of the convex portion 264 is smaller than the slope of other positions of the first side wall 261, and the concave corresponding to the convex portion 264 on the other side of the first heat exchange surface 1001 and the second heat exchange surface 1002 of the plate 100 can form a part of the fluid channel for the flow of the second fluid. The heat exchange surfaces acted on by the concave portion 263 and the convex portion 264 are opposite. The concave portion 263 mainly serves to expand the flow cross section of the first fluid flowing on the plate at the corner position of the herringbone wave, and the convex portion 264 mainly serves to expand the flow cross section of the second fluid flowing on the plate at the corner position of the herringbone wave.

[0027] For fluids with relatively high pressure drop requirements, such as water side fluids, the recess 263 and the convex portion 264 are beneficial to expanding the flow cross-section of the water side fluid at the tip of the herringbone wave, which can effectively reduce the pressure drop of the water side fluid, thereby improving the heat exchange performance of the plate heat exchanger.

[0028] The plate 100 provided in the embodiment of the present application. Since the corrugated sharp corner is set with a relatively gentle slope during the pressing process, the elongation rate of the plate at this position is reduced, and the stamping thinning amount of the plate at the sharp corner is also reduced accordingly, and the strength loss is small, which is conducive to improving the strength of the plate 100. Therefore, the plate heat exchanger 10 is not easy to deform during its use.

[0029] The embodiment provided by the present application is to set a more gentle structure, namely, a convex portion 264 and a concave portion 263, at the side wall position corresponding to the front edge and / or the rear edge of the herringbone wave angle. For the rear edge of the herringbone wave angle, by changing the local slope, the second side wall 262 forming the rear edge is made to transition to the wave crest 21 more gently relative to other positions. For the front edge of the herringbone wave angle, a more gentle structure is set, and by changing the local slope, the first side portion 261 forming the front edge is made to transition to the wave bottom more gently. The structure of the convex portion 264 and the concave portion 263 does not open up the entire corrugated structure 2, nor does it need to form a passage running through the corrugated curved section, which is conducive to reducing the difficulty of processing.

[0030] The first fluid and the second fluid exchange heat through the plate partition wall. In one embodiment, the first fluid is a refrigerant and the second fluid is a coolant. Of course, the first fluid can also be a coolant, in which case the second fluid can also be a refrigerant.

[0031] In one embodiment, the plurality of second side walls 262 of the plate 100 are each formed with a concave portion 263 , and the plurality of first side walls 261 of the plate 100 are each formed with a convex portion 264 .

[0032] refer to Figure 3 The concave portion 263 extends from the intersection of the trough 22 and the second side wall 262 to the crest 21 adjacent to the second side wall 262, and the side of the concave portion 263 opposite to the first side wall 261 of the adjacent corrugated structure 2 transitions from the trough 22 to the crest 21 in a gradually expanding fan-shaped surface, and the side of the concave portion 263 opposite to the first side wall 261 of the adjacent corrugated structure 2 is a slightly curved surface or a plane.

[0033] Correspondingly, the protrusion 264 extends from the intersection of the crest 21 and the first side wall 261 to the trough 22 adjacent to the first side wall 262, and the side surface of the protrusion 264 opposite to the second side wall 262 of the adjacent corrugated structure 2 gradually narrows from the crest 21 to the trough 22, and the side surface of the protrusion 264 opposite to the second side wall 262 of the adjacent corrugated structure 2 is a slightly curved surface or a plane.

[0034] In another embodiment, similarly, the plurality of second side walls 262 of the plate 100 are each formed with a concave portion 263, and the plurality of first side walls 261 of the plate 100 are each formed with a convex portion 264.

[0035] refer to Figure 7 As shown in the figure, the side surface of the concave portion 263 opposite to the first side wall 261 of the adjacent corrugated structure 2 transitions from the trough 22 to the crest 21 with a gradually expanding fan-shaped surface, and the side surface of the concave portion 263 opposite to the first side wall 261 of the adjacent corrugated structure 2 is a micro-curved surface or a flat surface, and the concave portion 263 extends from the waist of the second side wall 262 to the crest 21 adjacent to the second side wall 262, and the height of the intersection of the concave portion 263 and the second side wall 262 from the crest 21 accounts for 40% to 80% of the height of the crest 21 relative to the trough 22.

[0036] The convex portion 264 extends from the intersection of the crest 21 and the first side wall 261 to the trough 22 adjacent to the first side wall 262, and the side surface of the convex portion 264 opposite to the second side wall 262 of the adjacent corrugated structure 2 gradually shrinks from the crest 21 to the trough 22. On the basis that the side surface of the convex portion 264 opposite to the second side wall 262 of the adjacent corrugated structure 2 is a micro-curved surface or a flat surface, the convex portion 264 extends from the waist of the first side wall 261 to the trough 22 adjacent to the first side wall 261, and the height of the intersection of the convex portion 264 and the first side wall 261 from the trough 22 accounts for 40% to 80% of the height of the crest 21 relative to the trough 22.

[0037] refer to Figure 5 , Figure 6 As shown, in one embodiment of the present application, a plate 100 having a symmetrical wave structure is provided. For each plate 100, the depths of two adjacent troughs 22 are substantially equal. Figure 5 It is a cross-sectional schematic diagram at a plurality of continuous straight sections in the length direction of the plate. Each plate 100 also includes a first matching area 3 located on both sides of the main heat exchange area 1 in the length direction. The first matching area 3 includes a first plane portion 31. The first plane portion 31 is connected to the trough 22 at the edge of the main heat exchange area 1, and the trough 22 is flush with the first plane portion 31. The corrugated structure 2 is convex relative to the first plane portion 31 on the first heat exchange surface 1001 of each plate 100, and the corrugated structure 2 forms a groove relative to the first plane portion 31 on the second heat exchange surface 1002 of each plate 100. The crest 21 formed by at least part of the first connecting wall 25 is provided with a plane for welding with adjacent plates 100, and the trough 22 formed on the plate surface between adjacent corrugated structures 2 is provided with a plane for welding with adjacent plates 100.

[0038] For ease of understanding, the first plate 101 is used for illustration. In the first matching area 3 of the first plate 101, two planar corner holes are formed at the two corners of the first planar portion 31, and boss corner holes protruding from the plate surface by a certain height are respectively formed at the other two corners of the first planar portion 31. The direction in which the boss corner hole protrudes from the first planar portion 31 is opposite to the direction in which the flange protrudes from the first planar portion 31. Here, one side of the first plate 101 with the boss corner hole is defined as the first heat exchange surface 1001, and the other side is the second heat exchange surface 1002.

[0039] The corrugated structure 2 is convex at the first heat exchange surface 1001 of each plate 100 relative to the first plane portion 31, and the top of the corrugated structure 2 forms a crest 21. Correspondingly, the corrugated structure 2 forms a groove at the second heat exchange surface 1002 of each plate relative to the first plane portion 31, and the plate surface portion located between two adjacent corrugated structures 2 forms a trough 22. The herringbone corrugated patterns at the corresponding positions of the first plate 101 and the second plate 102 are set in reverse, and further, as Figure 3As shown, there is a gap between the convex portion 264 and the second side wall 262 of the adjacent corrugated structure 2, and the trough 22 of the plate 100 contacts the crest 21 of the adjacent plate to form a welding spot. The intersection of the first connecting wall 25 and the first side wall 261 and the concave portion 263 are separated by the first connecting wall 25, and the crest formed by at least part of the first connecting wall 25 contacts the trough of the adjacent plate 100 to form a welding spot.

[0040] The above-mentioned welding points are helpful to improve the strength and stability of the welding of the two plates, and are helpful to improve the bearing capacity of the corner area of ​​the herringbone corrugation to the fluid flow pressure, thereby helping to improve the product stability of the plate heat exchanger 10.

[0041] refer to Figure 6 A schematic cross-sectional view of a plurality of continuous bending sections in the length direction of the plate, wherein the first fluid flows between the first heat exchange surface 1001 of the first plate 101 and the second heat exchange surface 1002 of the second plate 102. Figure 6In the figure, the upper side of each plate is the side where the first heat exchange surface 1001 is located, and the lower side of each plate is the side where the second heat exchange surface 1002 is located. The solid line with an arrow indicates the approximate flow direction of the fluid. The slope of the second side wall 262 of the corrugated structure 2 of the first plate 101 at the position corresponding to the recess 263 is smaller than that at other positions of the second side wall 262. When the first fluid flows from the trough 22 of the first plate 101 along the second side wall 262 to the crest 21, compared with the second side wall 262' without the recess 263, the recessed area formed by the recess 263 on the side of the first heat exchange surface 1001 of the first plate 101 is beneficial to optimizing and expanding the flow cross-section of the first fluid at the corner position of the herringbone corrugation. The second side wall 262' without the recess 263 is indicated by a dotted line. The first fluid flowing on the side of the second heat exchange surface 1002 of the second plate 102 also needs to flow from the trough 22 of the second plate 102 along the first side wall 261 to the crest 21. The position of the first side wall 261 of the second plate 102 corresponding to the convex portion 264 has a smaller slope than other positions. The convex portion 264 on the side of the second heat exchange surface 1002 of the second plate 102 corresponds to the concave portion which also serves to expand the flow cross section of the first fluid. In this way, the concave portion 263 of the first plate 101 and the convex portion 264 of the second plate 102 can both serve to expand the flow cross section of the first fluid at the corner position of the herringbone wave, thereby facilitating improvement of the fluidity of the first fluid in the middle part of the herringbone corrugated pattern. Of course, in practice, the plate can have only one of the recessed portion 263 of the first plate 101 and the convex portion 264 of the second plate 102. When the recessed portion 263 of the first plate 101 and the convex portion 264 of the second plate 102 exist at the same time, it is beneficial to make the flow cross-section of the first fluid at the corner position of the herringbone wave larger. Similarly, when the recessed portion 263 of the second plate 101 and the convex portion 264 of the first plate 101 exist at the same time, it is beneficial to make the flow cross-section of the second fluid at the corner position of the herringbone wave larger.

[0042] Although the convex portion 264 is a raised structure at the position of the first heat exchange surface 1001 of the first plate 101, it has little restraining effect on the flow direction of the first fluid and is not easy to affect the fluidity of the first fluid. The convex portion 264 is a recessed area at the second heat exchange surface 1002 of the first plate 101, and the recessed area is beneficial to expanding the flow cross-section of the second fluid flowing on one side of the second heat exchange surface 1002. In this way, by compensating the position with less influence on the fluidity of the first fluid to the second fluid, the fluidity of the second fluid at the sharp corner position can be improved.

[0043] The flow of the second fluid is similar. The second fluid flows between the first heat exchange surface 1001 of the second plate 102 and the second heat exchange surface 1002 of the first plate 101. The slope of the second side wall 262 of the corrugated structure 2 of the second plate 102 at the position corresponding to the recess 263 is smaller than that at other positions of the second side wall 262. When the second fluid flows from the trough 22 of the second plate 102 along the second side wall 262 to the crest 21, compared with the second side wall 262' without the recess 263, the second side wall 262' without the recess 263 is indicated by a dotted line. The recessed area formed by the recess 263 on the side of the first heat exchange surface 1001 of the second plate 102 is beneficial to optimizing and expanding the flow cross-section of the second fluid at the corner position of the herringbone corrugation. At the same time, the second fluid flowing on the side of the second heat exchange surface 1002 of the first plate 101 also needs to flow from the trough 22 of the first plate 101 along the first side wall 261 to the crest 21. The position slope of the convex portion 264 corresponding to the first side wall 261 of the first plate 101 is relatively small, and the concave portion 264 corresponding to the convex portion 264 on the side of the second heat exchange surface 1002 also serves to expand the flow cross-section of the second fluid. In this way, the concave portion 263 of the second plate 102 and the convex portion 264 of the first plate 101 can both serve to expand the flow cross-section of the second fluid at the corner position of the herringbone wave, thereby facilitating the improvement of the fluidity of the first fluid in the middle part of the herringbone corrugated pattern.

[0044] Although the convex portion 264 is a raised structure at the position of the first heat exchange surface 1001 of the second plate 102, it has little restraining effect on the flow direction of the second fluid and is not easy to affect the fluidity of the second fluid. The convex portion 264 is a recessed area at the second heat exchange surface 1002 of the second plate 102, and the recessed area is beneficial to expanding the flow cross-section of the first fluid flowing on one side of the second heat exchange surface 1002. In this way, by compensating the position with less influence on the fluidity of the second fluid to the first fluid, the fluidity of the first fluid at the sharp corner position can be improved.

[0045] The relatively large first fluid flow cross-section and the second fluid flow cross-section are conducive to the smooth flow of the first fluid and the second fluid, reducing the influence of the welding points of the bending section on the fluid fluidity, improving the fluid fluidity in the middle part of the herringbone corrugated pattern, and further improving the uniformity of the distribution of the fluid on the plates of the plate heat exchanger, thereby improving the heat exchange performance of the plate heat exchanger.

[0046] In order to reduce the manufacturing cost, the first plate 101 and the second plate 102 may be plates of the same shape and structure, and the first plate 101 is rotated 180° relative to the second plate 102 .

[0047] In another embodiment of the present application, a plate 100 having an asymmetric corrugated structure is provided. For the asymmetric corrugated structure, refer to Figures 8 to 10The plurality of troughs 22 include a plurality of first troughs 221 and a plurality of second troughs 222. The depth of the first troughs 221 is greater than the depth of the second troughs 222. The first troughs 221 and the second troughs 222 are alternately arranged. The wave crest 21 is provided with a plane or a micro-curved surface for welding with an adjacent plate 100, and the first troughs 221 are provided with a plane or a micro-curved surface for welding with an adjacent plate 100.

[0048] Figure 8 It is a cross-sectional schematic diagram of a plurality of straight sections continuous in the length direction of the first plate 101. The first plate 101 includes a second matching area 4 located on both sides of the main heat exchange area 1 in the length direction of the first plate 101. The second matching area 4 includes a second plane portion 41. The second plane portion 41 is connected to the first trough 221 at the edge of the main heat exchange area 1 of the first plate 101, and the first trough 221 of the main heat exchange area 1 of the first plate 101 is flush with the second plane portion 41. Along the thickness direction of the first plate 101, the peak 21 and the second trough 222 are both higher than the second plane portion 41 on the first heat exchange surface 1001 of the first plate 101. The first trough 221 and the second trough 222 form an M-shaped structure relative to the second plane portion 41.

[0049] Fig. 9 It is a cross-sectional schematic diagram of a plurality of straight sections continuous in the length direction of the second plate 102. The second plate 102 includes a third matching area 5 located on both sides of the main heat exchange area 1 in the length direction of the second plate 102. The third matching area 5 includes a third plane portion 51. The third plane portion 51 is connected to the first connecting wall 25 at the edge of the main heat exchange area 1 of the second plate 102, so that the crest 21 of the second plate 102 is flush with the third plane portion 51. The first wave valley 221 and the second wave valley 222 are raised relative to the third plane portion 51 on the first heat exchange surface 1001 of the second plate 102. The first wave valley 221 and the second wave valley 222 are both higher than the first heat exchange surface 1001 of the second plate 102, and the first wave valley 221 and the second wave valley 222 form a W-shaped structure relative to the third plane portion 51.

[0050] The crest 21 of the first heat exchange surface 1001 of the first plate 101 contacts the crest 21 of the second heat exchange surface 1002 of the adjacent second plate 102 to form a welding spot, and the first trough 221 of the second heat exchange surface 1002 of the first plate 102 contacts the first trough 221 of the first heat exchange surface 1001 of the adjacent second plate 102 to form a welding spot.

[0051] In order to reduce the difficulty of processing the recessed portion 263 and the protruding portion 264 on the asymmetric plate type, the protruding portion 264 is formed on the first side wall 261 adjacent to the first wave valley 221, and the first side wall 261 adjacent to the second wave valley 222 is not formed with the protruding portion 24. Similarly, the recessed portion 263 is formed on the second side wall 262 adjacent to the first wave valley 221, and the second side wall 262 adjacent to the second wave valley 222 is not formed with the recessed portion 263.

[0052] The principle of the advantages of the concave portion 263 and the convex portion 264 on the fluidity of the asymmetric plate-type circulating fluid is similar to that of the symmetric plate-type, and will not be elaborated herein.

[0053] Furthermore, in the above-mentioned schematic diagrams provided in the present application, the number of curved sections 24 of each corrugated structure 2 is greater than or equal to 2. That is, in the width direction of the plate 100, at least a portion of the corrugated structures 2 in the plurality of corrugated structures 2 forms a structure with multiple herringbone corrugated patterns. Of course, the plate 100 of the plate heat exchanger provided in the present application is suitable for a single herringbone wave corrugated structure having one curved section 24 and two straight sections 23, or a V-shaped corrugated structure; it is also suitable for a multiple herringbone wave corrugated structure having more curved sections 24 and more straight sections 23, such as a W-shaped or double herringbone wave corrugated structure having 3 curved sections 24 and 4 straight sections 23. In particular, for multiple herringbone waves, since the wave tip angle of the herringbone wave structure occupies a certain proportion in the width direction of the plate, the present application is of great help in improving the performance of such products.

[0054] This application can effectively improve the uniformity of fluid flow on the plate and significantly reduce fluid flow resistance, thereby effectively improving product performance.

[0055] The plate heat exchanger provided in the present application is introduced in detail above. Specific examples are used in this article to illustrate the principle and implementation of the present invention. The description of the above embodiments is only used to help understand the core idea of ​​the present invention. It should be pointed out that for ordinary technicians in this technical field, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the scope of protection of the claims of the present invention.

Claims

1. A plate heat exchanger (10), comprising a plurality of plates (100), wherein the plurality of plates (100) comprises a plurality of first plates (101) and a plurality of second plates (102), wherein the plurality of first plates (101) and the plurality of second plates (102) are alternately arranged to form two types of fluid flow channels that are not connected, and each plate (100) comprises a first heat exchange surface (1001) and a second heat exchange surface (1002) that are opposite to each other, wherein the first heat exchange surface (1001) of the first plate (101) and the second heat exchange surface (1002) of the second plate (102) are opposite to each other. (1002), the second heat exchange surface (1002) of the first plate (101) is opposite to the first heat exchange surface (1001) of the second plate (102); each plate (100) is provided with a main heat exchange area (1), in which the plate (100) is provided with a plurality of corrugated structures (2) arranged at intervals along the length direction of the plate, and the plate (100) has a plurality of wave crests (21) and a plurality of wave troughs (22) in the main heat exchange area (1), and the plurality of wave crests (21) and the plurality of wave troughs (22) are arranged alternately; The corrugated structure (2) has at least two straight sections (23) and one curved section (24) in the width direction of the plate; the curved section (24) is connected between two adjacent straight sections (23), and the extension directions of the two adjacent straight sections (23) intersect, so that the two adjacent straight sections (23) and the curved section (24) located therebetween are matched to form a herringbone corrugation, and the curved section (24) forms a corner of the herringbone corrugation; The corrugated structure (2) comprises a first connecting wall (25) and two side walls (26); at least a portion of the first connecting wall (25) forms the wave crest (21), and the plate surface between adjacent corrugated structures (2) forms the wave trough (22); the two side walls (26) are respectively connected to two sides of the first connecting wall (25) to achieve connection between the wave crest (21) and the wave troughs (22) on both sides thereof; in the direction of the corner of the herringbone corrugation, the two side walls (26) comprise a first side wall (261) forming the front edge of the herringbone corrugation and a second side wall (262) forming the rear edge of the herringbone corrugation; in, At least one of the second side walls (262) forms a recess (263) in at least a portion of the curved section (24) that is recessed in the direction of the corner of the herringbone corrugation, and the slope of the second side wall (262) corresponding to the recess (263) is smaller than the slope of other positions of the second side wall (262) relative to the plane where the wave crest is located, and the recess (263) corresponding to one side of the first heat exchange surface (1001) and the second heat exchange surface (1002) of the plate (100) forms a part of a fluid channel for the first fluid to flow; and / or, At least one of the first side walls (261) forms a convex portion (264) protruding in the direction of the corner of the herringbone corrugation in at least a part of the area of ​​the curved section (24), and the slope of the first side wall (261) corresponding to the convex portion (264) relative to the plane where the wave crest is located is smaller than the slope of other positions of the first side wall (261), and the concave corresponding to the convex portion (264) on the other side of the first heat exchange surface (1001) and the second heat exchange surface (1002) of the plate (100) forms a part of a fluid channel for the flow of the second fluid.

2. The plate heat exchanger (10) according to claim 1, characterized in that: The plurality of second side walls (262) of the plate (100) are all formed with the concave portion (263), and the plurality of first side walls (261) of the plate (100) are all formed with the convex portion (264); The side surface of the concave portion (263) opposite to the first side wall (261) of the adjacent corrugated structure (2) transitions from the wave valley (22) to the wave peak (21) in a gradually expanding fan-shaped surface, and the side surface of the concave portion (263) opposite to the first side wall (261) of the adjacent corrugated structure (2) is a slightly curved surface or a flat surface; The side surface of the convex portion (264) opposite to the second side wall (262) of the adjacent corrugated structure (2) transitions from the wave crest (21) to the wave trough (22) in a gradually shrinking fan-shaped surface, and the side surface of the convex portion (264) opposite to the second side wall (262) of the adjacent corrugated structure (2) is a slightly curved surface or a flat surface.

3. The plate heat exchanger (10) according to claim 2, characterized in that: The concave portion (263) extends from the intersection of the trough (22) and the second side wall (262) to the crest (21) adjacent to the second side wall (262); or, the concave portion (263) extends from the waist of the second side wall (262) to the crest (21) adjacent to the second side wall (262), and the height of the intersection of the concave portion (263) and the second side wall (262) from the crest (21) accounts for 40% to 80% of the height of the crest (21) relative to the trough (22); The convex portion (264) extends from the intersection of the wave crest (21) and the first side wall (261) to the wave valley (22) adjacent to the first side wall (261); or, the convex portion (264) extends from the waist of the first side wall (261) to the wave valley (22) adjacent to the first side wall (261), and the height of the intersection of the convex portion (264) and the first side wall (261) from the wave valley (22) accounts for 40% to 80% of the height of the wave crest (21) relative to the wave valley (22).

4. The plate heat exchanger (10) according to claim 2 or 3, characterized in that: For each plate (100), the depths of two adjacent troughs (22) are substantially equal. Each plate (100) further comprises a first matching area (3) located on both sides of the main heat exchange area (1) in the length direction of the plate. The first matching area (3) comprises a first plane portion (31). The first plane portion (31) is connected to the trough (22) at the edge of the main heat exchange area (1), and the trough (22) is flush with the first plane portion (31). The corrugated structure (2) is raised on the first heat exchange surface (1001) of each plate (100) relative to the first plane portion (31); and the corrugated structure (2) forms a groove on the second heat exchange surface (1002) of each plate (100) relative to the first plane portion (31).

5. The plate heat exchanger (10) according to claim 4, characterized in that: The convex portion (264) is spaced from the second side wall (262) of the adjacent corrugated structure (2), and the trough (22) of the plate (100) contacts the crest (21) of the adjacent plate (100) to form a welding point.

6. The plate heat exchanger (10) according to claim 5, characterized in that: The intersection of the first connecting wall (25) and the first side wall (261) is spaced from the recess (263), and a wave crest (21) formed at least partially by the first connecting wall (25) contacts a wave trough (22) of an adjacent plate (100) to form a welding point.

7. The plate heat exchanger (10) according to claim 6, characterized in that: The first plate (101) and the second plate (102) are plates of the same shape and structure, and the first plate (101) is arranged to be rotated 180 degrees relative to the second plate (102).

8. The plate heat exchanger (10) according to claim 2 or 3, characterized in that: For each plate (100), the plurality of troughs (22) include a plurality of first troughs (221) and a plurality of second troughs (222); the depth of the first troughs (221) is greater than the depth of the second troughs (222); the first troughs (221) and the second troughs (222) are arranged alternately; the wave crest (21) is provided with a plane or a micro-curved surface for welding with an adjacent plate (100); and the first trough (221) is provided with a plane or a micro-curved surface for welding with an adjacent plate (100); The first plate (101) comprises a second matching area (4) located on both sides of the main heat exchange area (1) in the length direction, the second matching area (4) comprises a second plane portion (41), the second plane portion (41) is connected to a first wave valley (221) at the edge of the main heat exchange area (1) of the first plate (101), and the first wave valley (221) of the main heat exchange area (1) of the first plate (101) is flush with the second plane portion (41); along the thickness direction of the first plate (101), the wave crest (21) and the second wave valley (222) are both higher than the second plane portion (41) on the first heat exchange surface (1001) of the first plate (101); The second plate (102) comprises a third matching area (5) located on both sides of the main heat exchange area (1) in the length direction, the third matching area (5) comprising a third plane portion (51), the third plane portion (51) being connected to a first connecting wall (25) at the edge of the main heat exchange area (1) of the second plate (102), so that the wave crest (21) of the second plate (102) is flush with the third plane portion (51); the first wave trough (221) and the second wave trough (222) are protruding relative to the third plane portion (51) on the first heat exchange surface (1001) of the second plate (102); The wave crest (21) of the first heat exchange surface (1001) of the first plate (101) contacts the wave crest (21) of the second heat exchange surface (1002) of the adjacent second plate (102) to form a welding point, and the first wave trough (221) of the second heat exchange surface (1002) of the first plate (101) contacts the first wave trough (221) of the first heat exchange surface (1001) of the adjacent second plate (102) to form a welding point.

9. The plate heat exchanger according to claim 8, characterized in that: The convex portion (264) is formed on the first side wall (261) adjacent to the first wave valley (221), and the first side wall (261) adjacent to the second wave valley (222) is not formed with the convex portion (264); the concave portion (263) is formed on the second side wall (262) adjacent to the first wave valley (221), and the second side wall (262) adjacent to the second wave valley (222) is not formed with the concave portion (263).

10. The plate heat exchanger according to claim 1, characterized in that: In the width direction of the plate, the number of curved sections (24) of at least a portion of the corrugated structures (2) among the plurality of corrugated structures (2) is greater than or equal to 2, and the at least a portion of the corrugated structures (2) forms a multiple herringbone corrugated pattern in the width direction of the plate.

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