Plate heat exchanger

Abstract

A heat exchange plate comprises a plate face, the plate face comprises a distribution part and a heat exchange part, the distribution part comprises a first fluid distribution area and a second fluid distribution area which are located at the two ends of the plate face in the length direction respectively, and the heat exchange part is located between the first fluid distribution area and the second fluid distribution area. The heat exchange unit comprises a first heat exchange area and a second heat exchange area; the boundary part L1 is located between the first heat exchange area and the second heat exchange area, and one end of the boundary part L1 is located on the edge of one side of the heat exchange unit in the length direction; the other end of the boundary part L1 is positioned at the adjacent part of the heat exchange unit and the distribution part; the first heat exchange area extends from one side to the other side in the width direction of the heat exchange unit, both the first heat exchange area and the second heat exchange area are provided with inclined ripples, and the inclined ripples of the second heat exchange area and the inclined ripples of the first heat exchange area are different in inclined direction. According to the heat exchange plates of the plate heat exchanger, through the structural design, fluid pressure loss is reduced, and the overall heat exchange performance is improved.

Description

[0001] This application claims priority to Chinese Patent Application No. 202411044151.7, filed on July 31, 2024, entitled "Heat Exchange Plates and Plate Heat Exchangers", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This invention relates to the fields of refrigeration, air conditioning, and heat pumps, and particularly to a plate heat exchanger. Background Technology

[0003] In plate heat exchangers, the heat exchange plates typically employ a corrugated structure to balance the plate's heat transfer capacity and the fluid's pressure loss, achieving better heat exchange performance. Background technology uses single-layer herringbone corrugations on larger plates. While single-layer herringbone corrugations on larger plates offer advantages in fluid distribution and lower pressure loss, they result in poorer heat exchange. Double herringbone corrugations can achieve better heat exchange performance, but they increase fluid pressure loss. Summary of the Invention

[0004] Therefore, it is necessary to provide a plate heat exchanger with good overall heat exchange performance to address the above problems.

[0005] To achieve the above technical objectives, the present invention adopts the following technical solution:

[0006] A plate heat exchanger includes heat exchange plates, each plate having a corrugated surface. The plate surface includes a distribution section and a heat exchange section. The distribution section includes a first fluid distribution area and a second fluid distribution area located at both ends along the length of the plate surface. The heat exchange section is located between the first fluid distribution area and the second fluid distribution area. The heat exchange section includes a heat exchange unit extending from one side to the other along the width of the plate surface. The heat exchange unit includes a first heat exchange zone and a second heat exchange zone. A boundary L1 is defined, located between the first heat exchange zone and the second heat exchange zone. One end of the boundary L1 is located at one edge along the length of the heat exchange unit, and the other end of the boundary L1 is located at the adjacent portion between the heat exchange unit and the distribution section. The first heat exchange zone extends from one side to the other along the width of the heat exchange unit. Both the first and second heat exchange zones have inclined corrugations, and the inclined corrugations of the second heat exchange zone have a different inclination direction than those of the first heat exchange zone.

[0007] The plate heat exchanger of the present invention adopts an inclined corrugated structure in the heat exchange section. In the same heat exchange unit of the heat exchange section, a first heat exchange zone and a second heat exchange zone with inclined corrugations having different flow directions are arranged. When the fluid flows to the boundary between the first heat exchange zone and the second heat exchange zone, it is blocked by the corrugations with the other flow direction, thereby generating turbulence, improving the heat exchange capacity of the plate, and improving the overall heat exchange performance of the plate heat exchanger. Attached Figure Description

[0008] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings will be briefly described below. The drawings are merely illustrative of some embodiments of the present invention and are not intended to limit the invention to all embodiments. In the drawings:

[0009] Figure 1 This is a schematic diagram of the heat exchange plates in one embodiment of the present invention;

[0010] Figure 2 for Figure 1 A magnified view of a portion of the heat exchange plate at position A.

[0011] Figure 3 for Figure 1 A schematic diagram of the heat exchange unit in the embodiment;

[0012] Figure 4 for Figure 2 A magnified view of a portion of position B in the middle;

[0013] Figure 5 This is a schematic diagram of the heat exchange section in another embodiment of the present invention;

[0014] Figure 6 for Figure 5 Schematic diagram of the heat exchange unit;

[0015] Figure 7 This is a schematic diagram of the heat exchange plates in another embodiment of the present invention;

[0016] Figure 8 for Figure 7 Schematic diagram of the heat exchange section;

[0017] Figure 9 for Figure 7 A magnified view of the area at position I in the middle;

[0018] Figure 10 for Figure 7 Another enlarged view of the middle I position;

[0019] Figure 11 This is a schematic diagram of the first heat exchange plate and the second heat exchange plate in one embodiment of the present invention;

[0020] Figure 12 for Figure 11 Another schematic diagram of the first and second heat exchange plates;

[0021] Figure 13 This is a schematic diagram of the second heat exchange plate in the present invention;

[0022] Figure 14 This is a cross-sectional schematic diagram of a heat exchanger plate assembly in another embodiment of the present invention;

[0023] Figure 15 for Figure 14 A magnified view of the area at position E in the middle;

[0024] Figure 16 for Figure 15 A magnified view of the area at position H in the middle;

[0025] Figure 17 This is an exploded schematic diagram of a heat exchanger in one embodiment of the present invention.

[0026] In the picture:

[0027] 1. Plate surface; 10. Distribution section; 11. First fluid distribution zone; 12. Second fluid distribution zone; 101. Flow guiding zone; 102. Baffle zone; 20. Heat exchange section; 200. Heat exchange unit; 201. First heat exchange zone; 202. Second heat exchange zone; 203. Third heat exchange zone; 30. Main heat exchange zone; 40. Auxiliary heat exchange zone; 50. Port hole; 51. Input port hole; 52. Output port hole; 60. Distribution hole; 70. Groove section; 71. Annular section; 72. Extension section; 2. Heat exchange plate assembly; 21. First heat exchange plate; 211. First distribution section; 212. First heat exchange section; 213. First main heat exchange zone; 214. First auxiliary heat exchange zone; 22. Second heat exchange plate; 221. Second distribution section; 222. Second heat exchange section; 223. Second main heat exchange zone; 224. Second auxiliary heat exchange zone. Detailed Implementation

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. Based on the embodiments of the present invention, all other technical solutions obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] In the accompanying drawings, shapes and dimensions may be enlarged for clarity, and the same reference numerals will be used in all figures to indicate the same or similar parts.

[0030] In the following description, terms such as center, thickness, height, length, front, back, rear, left, right, top, bottom, upper, and lower are defined relative to the structure shown in the accompanying drawings. In particular, "height" corresponds to the dimension from top to bottom, "width" corresponds to the dimension from left to right, and "depth" corresponds to the dimension from front to back. These are relative concepts and may vary depending on their location and usage. Therefore, these or other orientations should not be interpreted as restrictive terms.

[0031] Terms involving attachment, connection, etc., refer to the relationship in which these structures are fixed or restrained by direct connection to each other or by indirect connection through intermediate structures, as well as movable or rigid attachment, unless otherwise clearly stated.

[0032] To achieve the above-mentioned objectives and other advantages of the present invention, the present invention provides the following technical solutions:

[0033] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0034] To achieve the above-mentioned objectives and other advantages of the present invention, the present invention provides the following technical solutions:

[0035] On the one hand, such as Figure 1 , Figure 7 As shown, the present invention provides a heat exchange plate, which includes a corrugated plate surface 1 and flanges arranged around the plate surface 1. The plate surface 1 includes a distribution section 10 and a heat exchange section 20. Specifically, the distribution section 10 includes a first fluid distribution area 11 and a second fluid distribution area 12 located at both ends of the plate surface 1 along its length. The first fluid distribution area 11 and the second fluid distribution area 12 have port holes 50, and the heat exchange section 20 is located between the first fluid distribution area 11 and the second fluid distribution area 12.

[0036] like Figure 2 , Figure 5 As shown, the heat exchange section 20 includes a heat exchange unit 200 that extends from one side of the plate surface 1 in the width direction to the other side. The heat exchange unit 200 includes a first heat exchange zone 201 and a second heat exchange zone 202. A dividing section L1 is defined, located between the first heat exchange zone 201 and the second heat exchange zone 202. One end of the dividing section L1 is located at one edge along the length direction of the heat exchange unit 200; the other end of the dividing section L1 is located at the adjacent portion of the heat exchange unit 200 and the distribution section 10. The first heat exchange zone 201 extends from one side of the width direction of the heat exchange unit 200 to the other side. Both the first heat exchange zone 201 and the second heat exchange zone 202 have inclined corrugations. The inclined corrugations of the second heat exchange zone 202 have different inclined directions than the inclined corrugations of the first heat exchange zone 201 (it should be understood that the different inclined directions in this invention refer to the different directions of fluid flow guided by the corrugations, that is, the difference between the inclined direction of the corrugations pointing from the upper left to the lower right of the plate surface 1 and the inclined direction of the corrugations pointing from the upper right to the lower left of the plate surface 1).

[0037] Through the above structural design, the heat exchange section 20 of the plate 1 is arranged with inclined corrugations. The inclined corrugations have a simple shape, which can effectively reduce the elongation of the plate 1. At the same time, the inclined corrugations without bends can reduce the pressure loss of the fluid along the flow path inside the corrugations. The inclined corrugations of the first heat exchange zone 201 and the second heat exchange zone 202 have different inclination directions. Therefore, when the fluid in one heat exchange zone flows to the boundary L1, it is blocked by the corrugations of the other heat exchange zone, thereby forming turbulence at the boundary L1, increasing the local fluid resistance, and improving the heat exchange performance of the plate.

[0038] In further proposals, such as Figure 2 As shown, the dividing section L1 is arranged along an inclined line, dividing the heat exchange unit 200 into a first heat exchange zone 201 and a second heat exchange zone 202 located at one corner of the heat exchange unit 200, forming a triangle. The dividing section L1 is adapted to the shape of the inclined corrugations, so that when fluid flows to the dividing section L1, it is obstructed by the complete inclined corrugations, forming uniform local resistance. It should be understood that the dividing section L1 in the figure is only schematic and does not necessarily represent the shape and specific location of the dividing section L1 in the actual product. Optionally, the dividing section L1 can also be arranged in an arc or a zigzag shape, and the inclined corrugations within the first heat exchange zone 201 and the second heat exchange zone 202 can be adaptively adjusted to achieve the technical effects of this invention.

[0039] Furthermore, such as Figure 2 As shown, the heat exchange unit 200 also includes a third heat exchange zone 203. A boundary portion L2 is defined, located between the first heat exchange zone 201 and the third heat exchange zone 203. The boundary portions L1 and L2 are arranged parallel to each other (if the boundary portions are not distributed along a straight line, they are symmetrical about the center of the heat exchange unit 200 by rotating 180°). The boundary portion L1 and the edge of the heat exchange unit 200 in the length direction form an acute angle b1, and the boundary portion L2 and the edge of the heat exchange unit 200 in the length direction form an acute angle b2. The acute angles b1 and b2 are equal in angle and have opposite opening directions, so that the second heat exchange zone 202 and the third heat exchange zone 203 are diagonally arranged in the heat exchange unit 200, that is, the opening of the acute angle b1 faces the first fluid distribution zone 11, and the opening of the acute angle b2 faces the second fluid distribution zone 12. The third heat exchange zone 203 has inclined corrugations, and the inclined corrugations of the third heat exchange zone 203 have the same inclination angle and the same inclination direction as the inclined corrugations of the second heat exchange zone 202. Through the above structural design, the flow direction of the inclined corrugations in the second heat exchange zone 202 and the third heat exchange zone 203 is different from that in the first heat exchange zone 201. Therefore, regardless of the flow direction of the fluid in the heat exchange unit 200, turbulence will be generated at either the boundary L1 or the boundary L2, thereby improving the heat exchange performance.

[0040] Furthermore, such as Figure 3 , Figure 6As shown, the heat exchange unit 200 includes a main heat exchange zone 30 with a larger area and an auxiliary heat exchange zone 40 with a smaller area. The area of ​​the main heat exchange zone is defined as M and the area of ​​the auxiliary heat exchange zone is defined as N. The relationship between M and N satisfies N≤M≤4N, that is, the area of ​​the main heat exchange zone 30 accounts for 1 / 2 to 4 / 5 of the area of ​​the heat exchange unit 200, ensuring that the heat exchange unit 200 has enough area for heat exchange.

[0041] The areas of the first heat exchange zone 201 are defined as S1, the second heat exchange zone 202 as S2, and the third heat exchange zone 203 as S3. When S1 > S2 + S3, the first heat exchange zone 201 serves as the main heat exchange zone 30. When S1 < S2 + S3, the second and third heat exchange zones 202 and 203 serve as the main heat exchange zones 30. The main heat exchange zone 30 undertakes the primary heat exchange function, while the auxiliary heat exchange zone 40, in addition to performing some heat exchange functions, also guides the fluid and increases turbulence.

[0042] When corrugations are pressed onto the plate at different angles, they can be categorized into large-angle corrugations with larger tilt angles and small-angle corrugations with smaller tilt angles. Large-angle corrugations increase fluid resistance and enhance heat transfer, while small-angle corrugations reduce fluid resistance and weaken heat transfer. Choosing a suitable corrugation tilt angle is beneficial for balancing fluid resistance and heat exchange efficiency. Let a1 be the obtuse angle formed by the tilted corrugations of the main heat exchange zone 30 and the width-direction edge of the plate surface 1. In this invention, a1 satisfies 120°≤a1≤150°. Let a2 be the obtuse angle formed by the oblique corrugations of the auxiliary heat exchange zone 40 and the width-direction edge of the heat exchange unit 200. Then, 120°≤a2≤a1. In this invention, the preferred angles a1 and a2 are 130 degrees.

[0043] In further proposals, such as Figure 1 , Figure 7 As shown, the heat exchange section 20 includes at least two heat exchange units 200, which are arranged along the length of the plate surface 1. Adjacent heat exchange units 200 are mirror-symmetrical about the width of the plate surface 1. Changing the fluid flow direction can increase the convective heat transfer intensity of the plate and improve the heat transfer performance. The second heat exchange zone 202, located on both sides of the heat exchange section 20 along its length, is adjacent to the distribution section 10 and guides the fluid in the distribution section 10 to the first heat exchange zone 201.

[0044] In further proposals, such as Figure 2 , Figure 4As shown, the distribution section 10 has a herringbone corrugation, and the first fluid distribution area 11 and the second fluid distribution area 12 each have at least two port holes 50, with the herringbone corrugation surrounding the port holes 50. The herringbone corrugation located in the same fluid distribution area includes a flow-guiding area 101 and flow-deflecting areas 102 located on both sides of the flow-guiding area 101. The flow-deflecting area 102 includes a first side and a second side. The first side is located at the edge along the length direction of the plate surface 1, and the second side connects to the edge along the width direction of the heat exchange section 20. It should be noted that the flow-deflecting area 102 in the figure is only a schematic representation and does not limit the specific shape and range of the flow-deflecting area 102 in the actual product. If the angle of the herringbone corrugation of the flow-guiding area 101 is defined as a3, and the angle between the extension lines of the corrugations on both sides of the flow-deflecting area 102 is defined as a4, then a4 ≤ a3. The included angle α4 of the corrugations in the baffle zone 102 is smaller than the angle α3 of the herringbone corrugations in the guide zone 101. This changes the fluid flow direction, guiding the fluid from both sides of the guide zone 101 in the width direction of the plate surface 1 towards the heat exchange section 20, which is beneficial for uniform fluid distribution. Compared to the herringbone corrugations of the guide zone 101, the included angle α4 of the baffle zone 102 is smaller, which can increase the number of weld points at the location of the baffle zone 102, thereby strengthening the connection. In a further embodiment, the inclined corrugations of the second heat exchange zone 202 have a different inclined direction from at least some of the adjacent herringbone corrugations, further changing the fluid flow direction and promoting uniform fluid distribution throughout the heat exchange section 20.

[0045] In further proposals, such as Figure 13 As shown, the corrugations in the distribution section 10 have equal heights, while the corrugations in the heat exchange section 20 are arranged with alternating high and low corrugations, and the height of the high corrugations is equal to that of the corrugations in the distribution section 10. The varying corrugations help to increase turbulence and improve the heat transfer capacity of the plates.

[0046] In further proposals, such as Figure 7 , Figure 9 , Figure 10 , Figure 13As shown, the port hole 50 includes an input port hole 51 and an output port hole 52. The input port hole 51 and the output port hole 52 for the same medium are located in the first fluid distribution area 11 and the second fluid distribution area 12, respectively. A distribution hole 60 is provided on one side of the input port hole 51 for refrigerant. The center of the input port hole 51 for refrigerant is defined as D. The distance between the center D and the edge of the plate surface 1 in the length direction has a minimum value D1, and the distance between the center D and the edge of the plate surface 1 in the width direction has a minimum value D2. The center of the distribution hole 60 is defined as G. The distance between the center G and the edge of the plate surface 1 in the length direction has a minimum value G1, and the distance between the center G and the edge of the plate surface 1 in the width direction has a minimum value G2. Then the relationship between D1 and G1 satisfies G1 > D1, and the relationship between D2 and G2 satisfies D2 > G2. The line connecting the center D and the center G is defined as C. The acute angle formed by the line connecting C and the adjacent edge of the plate surface 1 in the width direction is C1. Then 30° ≤ C1 ≤ 90°.

[0047] The above structural design allows the distribution hole 60 to be located inside the width direction of the plate and pointing to the adjacent width direction edge, which is beneficial for the refrigerant to flow quickly and evenly in the distribution area when it flows in from the distribution hole 60, and then evenly distributed to the entire plate surface 1.

[0048] In further proposals, such as Figure 9 , Figure 13 As shown, a groove-shaped portion 70 is provided around the refrigerant distribution hole 60. The groove-shaped portion 70 includes an annular portion 71 and a protruding portion 72. The bottom wall of the annular portion 71 is provided around the refrigerant inlet port hole 51. The protruding portion 72 extends relative to the side wall of the annular portion 71 towards the edge of the adjacent plate surface 1 in the width direction, and the protruding direction is consistent with the direction of the distribution hole 60. The distribution hole 60 is formed in the bottom wall of the protruding portion 72. Furthermore, the groove-shaped portion 70 is recessed from the welding plane on one side of the plate to the welding plane on the other side of the plate, that is, the recessed depth of the groove-shaped portion 70 is equal to the corrugation depth of the distribution portion 10.

[0049] On the other hand, such as Figures 11 to 17 As shown, the present invention provides a plate heat exchanger having a plurality of heat exchange plate groups 2, each heat exchange plate group 2 consisting of two heat exchange plates having the aforementioned structure, with a single-layer fluid channel formed between the two heat exchange plates.

[0050] Specifically, such as Figure 11 , Figure 12 As shown, each heat exchange plate group 2 includes a first heat exchange plate 21 and a second heat exchange plate 22, which are stacked together. The first and second heat exchange plates have the aforementioned heat exchange plate structure. Specifically, the first heat exchange plate 21 has the following specific structure: Figure 1 As shown, the specific structure of the second heat exchange plate 22 is as follows: Figure 7As shown. The main heat exchange zone 30 in the first heat exchange plate 21 is defined as the first main heat exchange zone 213, and the auxiliary heat exchange zone 40 is defined as the first auxiliary heat exchange zone 214; the main heat exchange zone 30 in the second heat exchange plate 22 is defined as the second main heat exchange zone 223, and the auxiliary heat exchange zone 40 is defined as the second auxiliary heat exchange zone 224; the second main heat exchange zone 223 is opposite to the first main heat exchange zone 213, and the second auxiliary heat exchange zone 224 is opposite to the first auxiliary heat exchange zone 214; the corrugated structures at the relative positions of the first heat exchange plate 21 and the second heat exchange plate 22 are projected in an alternating manner along the stacking direction of the heat exchange plate assembly 2. That is, when the first heat exchange plate 21 and the second heat exchange plate 22 are stacked, the distribution section 10 is positioned correspondingly, and the herringbone openings face opposite directions; the first heat exchange zone 201, the second heat exchange zone 202, and the third heat exchange zone 203 in the heat exchange section 20 are positioned correspondingly, but the corrugated inclination directions are different.

[0051] Through the above structural design, the heat exchange plates in the heat exchange plate group 2 of the present invention are zoned and correspond to each other when stacked, and the corrugation tilt direction is different. Different plates are easy to distinguish and identify, and it is not easy for them to be reversed or misassembled when multiple layers are stacked.

[0052] In further proposals, such as Figure 1 , Figure 3 , Figure 7 , Figure 8 , Figure 11 , Figure 12 As shown, in the first heat exchange plate 21, the inclined corrugations of the main heat exchange zone 30 form an obtuse angle a1 with the width-direction edge of the plate surface 1, and the inclined corrugations of the auxiliary heat exchange zone 40 form an obtuse angle a2 with the width-direction edge of the heat exchange unit 200; in the second heat exchange plate 22, the inclined corrugations of the main heat exchange zone 30 form an obtuse angle b1 with the width-direction edge of the plate surface 1, and the inclined corrugations of the auxiliary heat exchange zone 40 form an obtuse angle b2 with the width-direction edge of the heat exchange unit 200, satisfying b1 = a1 and b2 = a2. The corrugations at the relative positions of the first heat exchange plate 21 and the second heat exchange plate 22 have different inclination directions but equal inclination angles, which facilitates the formation of regular and uniform heat exchange channels, improves plate heat exchange efficiency, and prevents freezing.

[0053] In a further embodiment, the heat exchange plate assembly 2 can be configured with different corrugation heights for different heat exchange requirements. Specifically, the heat exchange section 20 in the first heat exchange plate 21 is defined as the first heat exchange section 212, and the distribution section 10 is defined as the first distribution section 211; the heat exchange section 20 in the second heat exchange plate 22 is defined as the second heat exchange section 222, and the distribution section 10 is defined as the second distribution section 221. Therefore, when the first and second plates are combined, the following options can be selected (the attached diagram only shows one embodiment):

[0054] (1) The corrugation heights of the first heat exchange section 212 and the first distribution section 211 are equal; the corrugation heights of the second heat exchange section 222 and the second distribution section 221 are equal, and the corrugation heights of the first heat exchange section 212 and the second heat exchange section 222 are equal.

[0055] (2) Figure 13 , Figure 16 As shown, the corrugation heights of the first heat exchange section 212 and the first distribution section 211 are equal; the corrugation height of the second distribution section 221 is equal to that of the first distribution section 211; the corrugations of the second heat exchange section 222 are arranged with alternating high and low corrugations, and the height of the high corrugations is equal to that of the second distribution section 221. Several heat exchange plate assemblies 2 overlap to form asymmetrical channels with unequal internal volumes. The channels with larger volumes are generally water-side channels, and the channels with smaller volumes are generally refrigerant channels, reducing the refrigerant charge, lowering the water-side pressure drop, and improving heat exchange performance.

[0056] (3) The corrugations of the first heat exchange section 212 are arranged with alternating high and low corrugations, and the height of the high corrugations is equal to the height of the corrugations of the first distribution section 211; the corrugations of the second heat exchange section 222 are arranged with alternating high and low corrugations, and the height of the high corrugations is equal to the height of the corrugations of the second distribution section 221. Several heat exchange plate groups 2 overlap to form asymmetrical channels with unequal internal volumes. Both plates are arranged with alternating high and low corrugations, which increases the difference in internal volume between different flow channels, further reduces the refrigerant charge, and reduces the water-side pressure drop.

[0057] In one embodiment, the heat exchanger in this invention is a dual-loop plate heat exchanger, that is, the port holes 50 of the heat exchange plate assembly 2 include two input port holes 51 for the refrigerant and two output port holes 52 for the refrigerant. The input port holes 51 and output port holes 52 for the same medium are located in the first fluid distribution area 11 and the second fluid distribution area 12, respectively. The heat exchange plate assembly 2 has six port holes (F1 / F2 / F3 / F4 / F5 / F6, and the port holes in the following text are labeled accordingly), and four plates are stacked to form three channels, namely one water-side channel and two refrigerant channels, wherein F1 / F2 are the port holes 50 of the water-side channel.

[0058] Specifically, such as Figure 7 , Figure 14 , Figure 17As shown, when the heat exchanger is used as an evaporator, refrigerant flows in from port holes F3 / F5 below the plates and flows out from port holes above the plates, while water flows in from port hole F1 above the plates and flows out from port hole F2 below the plates. When the heat exchanger is used as a condenser, refrigerant flows in from port holes F5 / F6 above the plates and flows out from port holes below the plates, while water flows in from port hole F2 below the plates and flows out from port hole F1 above the plates. When the refrigerant channels use cross-flow, port holes F3 and F6 correspond, and port holes F4 and F6 correspond; when the refrigerant channels use parallel flow, port holes F3 and F5 correspond, and port holes F4 and F6 correspond.

[0059] like Figure 12 , Figure 13 , Figure 16 , Figure 17 As shown, to differentiate the inlets of the two refrigerant channels, the heat exchanger plate assembly 2 in the heat exchanger has two different plate types, A and B. Plate type A does not have a distributor, while plate type B has only one port hole for the refrigerant with a distributor. Specifically, a distribution hole 60 is opened at port hole F3 on plate B, while no distribution hole 60 is opened at port hole F5. The first refrigerant channel R1 enters the interlayer flow channel only through the distribution hole 60 at position F3, and the second refrigerant channel R2 is not connected in this interlayer flow channel. On plate B', no distribution hole 60 is opened at port hole F3, but a distribution hole 60 is opened at port hole F5. The second refrigerant channel R2 enters the interlayer flow channel only through the distribution hole 60 at position F5, and the first refrigerant channel R1 is not connected in this interlayer flow channel. Through the above structural design, when the heat exchange plates in heat exchange plate group 2 are stacked in the order of ABA-B'-ABA-B'..., a dual refrigerant circuit will be formed in sequence: water side channel W-first refrigerant channel R1-water side channel W-second refrigerant channel R2...

[0060] In further proposals, such as Figure 12 , Figure 13 , Figure 17 As shown, in order to facilitate plate processing, grooves 70 are pressed at the positions of the two refrigerant inlet port holes 51 in plate type B and plate type B'. The only difference is that the grooves 70 at the positions of the different port holes 50 are provided with distribution holes 60 to distinguish the inlets of the first refrigerant channel R1 and the second refrigerant channel R2.

[0061] In further proposals, such as Figure 13 , Figure 14 , Figure 15 , Figure 16As shown, the two heat exchange plates in the same heat exchange plate group 2 are asymmetrical. The corrugations on the heat exchange plate of type A are of equal height, while the corrugations on the distribution section 10 of the heat exchange plate of type B are of equal height, but the corrugations on the heat exchange section 20 are of different heights. Through the above structural design, a heat exchange plate group 2 is formed that has a stable connection in the distribution area and different flow channel volumes in the heat exchange area.

[0062] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0063] The embodiments described above are merely examples of several implementations of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention.

Claims

1. A plate heat exchanger, comprising heat exchange plates, the heat exchange plates including a plate surface (1) having a corrugated structure, the plate surface (1) including a distribution section (10) and a heat exchange section (20), the distribution section (10) including a first fluid distribution area (11) and a second fluid distribution area (12) respectively located at both ends of the plate surface (1) along its length, the heat exchange section (20) being located between the first fluid distribution area (11) and the second fluid distribution area (12), characterized in that: The heat exchange section (20) includes a heat exchange unit (200) that extends from one side of the plate surface (1) in the width direction to the other side. The heat exchange unit (200) includes a first heat exchange zone (201) and a second heat exchange zone (202). A dividing section L1 is defined, which is located between the first heat exchange zone (201) and the second heat exchange zone (202). One end of the dividing section L1 is located at the edge of one side of the heat exchange unit (200) in the length direction. The other end of the dividing section L1 is located at the adjacent part of the heat exchange unit (200) and the distribution section (10). The first heat exchange zone (201) extends from one side of the width direction of the heat exchange unit (200) to the other side. Both the first heat exchange zone (201) and the second heat exchange zone (202) have inclined corrugations. The inclined corrugations of the second heat exchange zone (202) have different inclination directions than the inclined corrugations of the first heat exchange zone (201).

2. The plate heat exchanger as described in claim 1, characterized in that, The heat exchange unit (200) further includes a third heat exchange zone (203), defining a dividing part L2. The dividing part L2 is located between the first heat exchange zone (201) and the third heat exchange zone (203). The dividing part L1 and the dividing part L2 are strip-shaped. The dividing part L1 and the edge of the heat exchange unit (200) in the length direction form an acute angle b1, and the dividing part L2 and the edge of the heat exchange unit (200) in the length direction form an acute angle b2, so b1 = b2. The third heat exchange zone (203) has inclined corrugations. The inclined corrugations of the third heat exchange zone (203) have the same inclined angle and the same inclined direction as the inclined corrugations of the second heat exchange zone (202).

3. The plate heat exchanger as described in claim 1 or 2, characterized in that, The heat exchange section (20) includes at least two heat exchange units (200), each heat exchange unit (200) is arranged along the length direction of the plate surface (1), and adjacent heat exchange units (200) are mirror-symmetrical about the width direction of the plate surface (1).

4. The plate heat exchanger as described in claim 2, characterized in that, The heat exchange unit (200) includes a main heat exchange zone (30) and an auxiliary heat exchange zone (40). The area of ​​the main heat exchange zone is defined as M and the area of ​​the auxiliary heat exchange zone is defined as N. The relationship between M and N satisfies N≤M≤4N. The area of ​​the first heat exchange zone (201) is defined as S1, the area of ​​the second heat exchange zone (202) is defined as S2, and the area of ​​the third heat exchange zone (203) is defined as S3. When S1>S2+S3, the first heat exchange zone (201) is the main heat exchange zone (30). When S1<S2+S3, the second heat exchange zone (202) and the third heat exchange zone (203) are the main heat exchange zone (30). The obtuse angle formed by the inclined corrugation of the main heat exchange zone (30) and the width direction edge of the plate surface (1) is defined as a1. Then a1 satisfies 120°≤a1≤150°.

5. The plate heat exchanger as described in claim 4, characterized in that, The inclined corrugations of the auxiliary heat exchange zone (40) form an obtuse angle a2 with the width direction edge of the heat exchange unit (200), so 120°≤a2≤a1.

6. The plate heat exchanger as described in claim 4, characterized in that, Both the first fluid distribution area (11) and the second fluid distribution area (12) include a flow guide area (101) and a flow deflection area (102) located on both sides of the flow guide area (101). The corrugations at the location of the flow guide area (101) and the corrugations at the location of the flow deflection area (102) extend at an angle.

7. The plate heat exchanger as described in claim 4, characterized in that, The distribution section (10) includes a port hole (50), which includes an input port hole (51) and an output port hole (52). The input port hole (51) and the output port hole (52) of the same medium are located in the first fluid distribution area (11) and the second fluid distribution area (12), respectively. A distribution hole (60) is provided on one side of the inlet port hole (51) for refrigerant. The center of the inlet port hole (51) for refrigerant is defined as D. The distance between the center D and the edge of the plate surface (1) in the length direction has a minimum value D1, and the distance between the center D and the edge of the plate surface (1) in the width direction has a minimum value D2. The center of the distribution hole (60) is defined as G. The distance between the center G and the edge of the plate surface (1) in the length direction has a minimum value G1, and the distance between the center G and the edge of the plate surface (1) in the width direction has a minimum value G2. Then the relationship between D1 and G1 satisfies G1 > D1, and the relationship between D2 and G2 satisfies D2 > G2. Let C be the line connecting the center D and the center G, and let C1 be the acute angle formed by the line C and the adjacent edge of the plate (1) in the width direction. Then, 30°≤C1≤90°.

8. The plate heat exchanger as described in any one of claims 1-7, characterized in that, It includes a first heat exchange plate (21) and a second heat exchange plate (22), wherein the first heat exchange plate (21) is the heat exchange plate according to any one of claims 1-7, and the second heat exchange plate (22) is the heat exchange plate according to any one of claims 1-7, wherein the first heat exchange plate (21) and the second heat exchange plate (22) are stacked together; the corrugated structures in the opposite regions of the first heat exchange plate (21) and the second heat exchange plate (22) have equal inclination angles and staggered directions.

9. The plate heat exchanger as described in claim 8, characterized in that, The heat exchange section (20) in the first heat exchange plate (21) is defined as the first heat exchange section (212), and the distribution section (10) is defined as the first distribution section (211); the heat exchange section (20) in the second heat exchange plate (22) is defined as the second heat exchange section (222), and the distribution section (10) is defined as the second distribution section (221); the corrugation heights of the first heat exchange section (212) and the first distribution section (211) are equal; the corrugation heights of the second heat exchange section (222) and the second distribution section (221) are equal, and the corrugation heights of the first heat exchange section (212) and the second heat exchange section (222) are equal.

10. The plate heat exchanger as described in claim 9, characterized in that, The heat exchange section (20) in the first heat exchange plate (21) is defined as the first heat exchange section (212), and the distribution section (10) is defined as the first distribution section (211); the heat exchange section (20) in the second heat exchange plate (22) is defined as the second heat exchange section (222), and the distribution section (10) is defined as the second distribution section (221); the corrugation heights of the first heat exchange section (212) and the first distribution section (211) are equal; the corrugation height of the second distribution section (221) is equal to the corrugation height of the first distribution section (211); the corrugations of the second heat exchange section (222) are arranged with alternating high and low waves, and the height of the high wave is equal to the corrugation height of the second distribution section (221).

11. The plate heat exchanger as described in claim 9, characterized in that, The heat exchange section (20) in the first heat exchange plate (21) is defined as the first heat exchange section (212), and the distribution section (10) is defined as the first distribution section (211); the heat exchange section (20) in the second heat exchange plate (22) is defined as the second heat exchange section (222), and the distribution section (10) is defined as the second distribution section (221); the corrugations of the first heat exchange section (212) are arranged with alternating high and low waves, and the height of the high waves is equal to the height of the corrugations of the first distribution section (211); the corrugations of the second heat exchange section (222) are arranged with alternating high and low waves, and the height of the high waves is equal to the height of the corrugations of the second distribution section (221).

12. The plate heat exchanger as described in any one of claims 10-12, characterized in that, The second heat exchange plate (22) includes two inlet port holes (51) and two outlet port holes (52) for the refrigerant in the port holes (50); the second heat exchange plate (22) also includes a distribution hole (60) and a groove (70), the distribution hole (60) being located beside one of the two inlet port holes (51) for the refrigerant; the groove (70) includes an annular portion (71) and a protruding portion (72), the bottom wall of the annular portion (71) being arranged around the refrigerant inlet port holes (51)(50), the protruding portion (72) protruding relative to the side wall of the annular portion (71), and the distribution hole (60) being located on the bottom wall of the protruding portion (72).

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