Heat exchange plate and heat exchanger

Abstract

The utility model provides a heat exchange plate and a heat exchanger. The heat exchange plate comprises a plate body, the two sides, in the length direction, of the plate body are each provided with a flow guide area, the middle of the plate body is provided with a heat exchange area, corner holes are formed in the ends of the plate body, herringbone corrugations in the width direction are arranged in the heat exchange area, and a flow guide channel connecting the corner holes and the heat exchange area is arranged in each flow guide area; the flow guide area comprises a first flow guide area and a second flow guide area which are connected, the first flow guide area is close to the corner hole, the edge, connected with the second flow guide area, of the first flow guide area is a first straight line, the edge, close to the heat exchange area, of the second flow guide area is a first arc line and a second arc line which are alternately arranged, the first arc line protrudes towards the heat exchange area, and the second arc line protrudes towards the first flow guide area. And the first arc lines correspond to inflection points of the herringbone ripples one by one. The heat exchange plate and the heat exchanger are simple in structure, convenient to manufacture, uniform in fluid distribution, good in heat transfer effect, high in stability and long in service life.

Description

Technical Field

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

[0002] Detachable plate heat exchangers play an important role in petrochemical, shipbuilding, machinery, HVAC and many other industrial productions due to their flexible process combination, simple manufacturing process, small floor area, compact structure, high heat transfer, easy disassembly and cleaning and many other advantages. With the development of industrial technology, heat exchanger products with high efficiency, energy saving and environmental protection are more and more favored by users. For detachable plate heat exchangers, the insufficient heat exchange performance caused by uneven flow distribution has always been the core problem to be solved by heat exchanger manufacturers. The uneven fluid distribution of the heat exchanger not only affects the heat exchange performance and causes waste of operating energy, but also causes local scaling, blockage, and even local overheating, affecting the life of the product.

[0003] The heat exchanger includes a plurality of stacked heat exchange plates. The heat exchange plate includes a diversion area at both ends and a heat exchange area in the middle. The diversion area is connected with corner holes for fluid inlet and outlet. The existing heat exchange plates mostly have a straight-line design at the boundary between the diversion area and the heat exchange area. Therefore, the distances from different positions of the corner holes to the heat exchange area are not equal, resulting in insufficient flow in the heat exchange area far from the corner holes, forming a relatively large stagnant area and affecting the heat exchange performance. At the same time, the straight boundary often causes insufficient rigidity of the heat exchange plate, and it is easy to bend and deform during manufacturing and operation, affecting the accuracy and life. Therefore, there is an urgent need for a heat exchange plate that can improve the heat transfer effect and structural stability. Summary of the Utility Model

[0004] In view of this, the purpose of this application is to propose a heat exchange plate and a heat exchanger to solve the related problems mentioned in the background art.

[0005] In the first aspect of this application, a heat exchange plate is provided, including a plate body. On both sides of the plate body along the length direction, there is a diversion area respectively, a heat exchange area is arranged in the middle, and corner holes are arranged at the ends. Herringbone corrugations are arranged in the heat exchange area. The herringbone corrugations include at least two rows of inflection points along the width direction. A diversion channel connecting the corner holes and the heat exchange area is arranged in each diversion area; the diversion area includes a connected first diversion area and a second diversion area. The first diversion area is arranged close to the corner holes, and the second diversion area is arranged close to the heat exchange area. The edge where the first diversion area and the second diversion area are connected is a first straight line arranged along the width direction. The edge of the second diversion area close to the heat exchange area is a first arc and a second arc arranged alternately along the width direction. The first arc protrudes towards the heat exchange area, and the second arc protrudes towards the first diversion area. The first arc is arranged in one-to-one correspondence with the inflection points of the herringbone corrugations.

[0006] Further, at least three of the first arcs are included at the edge of the second diversion area close to the heat exchange area. The distance between the vertex of the first arc at both ends of the first straight line and the first straight line is a first distance, and the first distance is positively correlated with the width of the plate body.

[0007] Further, the distance between the vertex of the first arc in the middle of the first straight line and the first straight line is a second distance, the ratio of the first distance to the second distance is a first ratio, and the first ratio is positively correlated with the width of the plate body.

[0008] Further, the first ratio is 0.5 to 1.5.

[0009] Further, the tangent point of the first arc and the second arc is a first tangent point. The distance between the first tangent point and the vertex of the adjacent first arc in the width direction is a third distance, and the distance between the vertices of two adjacent first arcs in the width direction is a fourth distance. The third distance is less than or equal to 1 / 3 of the fourth distance.

[0010] Further, the edge of the heat exchange area in the length direction is a second straight line. The distance between the vertex of the first arc at both ends of the first straight line and the adjacent second straight line is a fifth distance, and the fifth distance is less than the fourth distance.

[0011] Further, the first arcs at both ends of the first straight line intersect with the first straight line.

[0012] Further, the intersection point of the first arc at both ends of the first straight line and the first straight line is a first intersection point, and the first intersection point is arranged with a gap from the second straight line.

[0013] Further, the number of rows of the inflection points of the chevron corrugations in the width direction is odd.

[0014] In the second aspect of the present application, a heat exchanger is provided, which includes a plurality of stacked heat exchange plates as described in the first aspect above, and a sealing gasket is provided between adjacent heat exchange plates.

[0015] As can be seen from the above, for the heat exchange plate and the heat exchanger provided by the present application, the heat exchange plate includes a plate body. On both sides of the plate body along the length direction, there is a diversion area respectively, a heat exchange area is provided in the middle, a corner hole is provided at the end, herringbone corrugations are provided in the heat exchange area, and the herringbone corrugations include at least two rows of inflection points along the width direction. A diversion channel connecting the corner hole and the heat exchange area is provided in each diversion area; the diversion area includes a connected first diversion area and a second diversion area. The first diversion area is arranged close to the corner hole, and the second diversion area is arranged close to the heat exchange area. The edge where the first diversion area and the second diversion area are connected is a first straight line arranged along the width direction. The edge of the second diversion area close to the heat exchange area is a first arc and a second arc arranged alternately along the width direction. The first arc protrudes towards the heat exchange area, and the second arc protrudes towards the first diversion area. In this way, the dividing line between the diversion area and the heat exchange area is wavy, which can effectively improve the rigidity of the plate body, is beneficial to bearing pressure during manufacturing and use, and prolongs the service life of the product; the first arc corresponds to the inflection point of the herringbone corrugation one by one. In this way, in the second diversion area, the number of diversion channels connecting the area corresponding to the first arc close to the corner hole and the corresponding heat exchange area is reduced, that is, the fluid flow rate flowing to the heat exchange area close to the corner hole is reduced; in the second diversion area, the number of diversion channels connecting the area corresponding to the first arc far from the corner hole and the corresponding heat exchange area is increased, that is, the fluid flow rate flowing to the heat exchange area far from the corner hole is increased; for the middle area of the second diversion area, the flow rate will not be significantly changed, so as to evenly distribute the flow rate of the entire heat exchange area, improve the heat transfer performance of the product, and eliminate the problem of fouling in the stagnant area; between adjacent inflection points of the herringbone corrugation, because the second arc protruding towards the first diversion area is provided, the herringbone corrugation in this area extends towards the diversion area, increasing the effective heat transfer area of the heat exchange area, and further improving the heat transfer performance; the heat exchange plate and the heat exchanger have simple structures, are convenient to manufacture, have uniform fluid distribution, good heat transfer effects, strong stability, and long service lives. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the technical solutions in the present application or related technologies, the following will briefly introduce the drawings required for use in the description of the embodiments or related technologies. Obviously, the drawings in the following description are only the embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0017] Figure 1 It is a schematic structural diagram of a heat exchange plate in an embodiment of the present application;

[0018] Figure 2 For Figure 1 a partial enlarged structural diagram of the heat exchange plate in;

[0019] Figure 3 It is a partial structural diagram of another heat exchange plate in an embodiment of the present application;

[0020] Figure 4 is Figure 3 the schematic cross-sectional view of the heat exchange plate at A-A in

[0021] Figure 5 is Figure 3 the schematic cross-sectional view of the heat exchange plate at B-B in

[0022] Figure 6 is Figure 3 the schematic cross-sectional view of the heat exchange plate at C-C in

[0023] Reference numerals: 1, plate body; 2, flow guiding area; 2-1, flow guiding channel; 3, heat exchange area; 3-1, herringbone corrugation; 3-2, second straight line; 4, corner hole; 5, first flow guiding area; 5-1, first straight line; 6, second flow guiding area; 6-1, first arc; 6-2, second arc. Detailed implementation manners

[0024] To make the objectives, technical solutions and advantages of this application clearer and more understandable, the following further elaborates on this application in detail with reference to specific embodiments and the attached drawings.

[0025] It should be noted that unless otherwise defined, the technical terms or scientific terms used in the embodiments of this application should have the ordinary meanings understood by those with ordinary skills in the field to which this application belongs. The "first", "second" and similar terms used in the embodiments of this application do not denote any order, quantity or importance, but are only used to distinguish different components. Words such as "including" or "comprising" mean that the elements or objects appearing before this word cover the elements or objects listed after this word and their equivalents, without excluding other elements or objects. The terms such as "connected" or "coupled" are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. The terms such as "upper", "lower", "left" and "right" are only used to represent relative positional relationships, and when the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0026] Detachable plate heat exchangers play an important role in petrochemical, shipbuilding, machinery, HVAC and many other industrial productions due to their flexible process combinations, simple manufacturing processes, small floor areas, compact structures, and many advantages such as high heat transfer and easy disassembly and cleaning. With the development of industrial technology, heat exchanger products with high efficiency, energy conservation and environmental protection are increasingly favored by users. For detachable plate heat exchangers, the insufficient heat transfer performance caused by uneven flow distribution has always been the core problem that heat exchanger manufacturers need to solve. The uneven fluid distribution in heat exchangers not only affects the heat transfer performance, resulting in waste of operating energy, but also causes local fouling, blockage, and even local overheating, affecting the lifespan of the product.

[0027] The heat exchanger includes a plurality of stacked heat exchange plates. The heat exchange plates include a flow guiding area at both ends and a heat exchange area in the middle. The flow guiding area is connected with corner holes for fluid inlet and outlet. In the existing heat exchange plates, the dividing line between the flow guiding area and the heat exchange area is mostly designed as a straight line. Therefore, the distances from different positions of the corner holes to the heat exchange area are unequal, resulting in insufficient flow rate in the heat exchange area far from the corner holes, forming a relatively large stagnant area and affecting the heat exchange performance. At the same time, the straight dividing line often causes insufficient rigidity of the heat exchange plate, and it is easy to generate bending deformation during manufacturing and operation, affecting accuracy and service life. Therefore, there is an urgent need for a heat exchange plate that can improve heat transfer effect and structural stability.

[0028] In some technologies, a transition area is provided between the flow guiding area and the heat exchange area of the plate. In the transition area, full-height transition protrusions and transition depression corrugations with gradually changing angles are provided to adjust the uniformity of the fluid flowing from the corner holes into the heat exchange area. The transition area is convex towards the heat exchange area in an arc shape, increasing the opening length of the transition area flowing into the heat exchange area. However, the corrugation spacing in the transition area is denser than that in the flow guiding area, increasing the overall resistance of the plate and being unfavorable for energy conservation. At the same time, although it is convex towards the heat exchange area in an arc shape, increasing the inlet of the flow guiding area flowing into the heat exchange area, it cannot more effectively improve the fluid in the stagnant area far from the corner holes.

[0029] The following will be described in detail the technical solutions of the present application through specific embodiments in combination with Figures 1 to 6 to elaborate.

[0030] In some embodiments of the present application, a heat exchange plate is provided. As Figure 1 and Figure 2 shown, it includes a plate body 1. On both sides of the plate body 1 along the length direction, a flow guiding area 2 is respectively provided. In the middle, a heat exchange area 3 is provided. At the end, a corner hole 4 is provided. In the heat exchange area 3, herringbone corrugations 3-1 are provided. The herringbone corrugations 3-1 include at least two rows of inflection points along the width direction. In each flow guiding area 2, a flow guiding channel 2-1 connecting the corner hole 4 and the heat exchange area 3 is provided; the flow guiding area 2 includes a connected first flow guiding area 5 and a second flow guiding area 6. The first flow guiding area 5 is arranged close to the corner hole 4, and the second flow guiding area 6 is arranged close to the heat exchange area 3. The edge where the first flow guiding area 5 is connected to the second flow guiding area 6 is a first straight line 5-1 arranged along the width direction. The edge of the second flow guiding area 6 close to the heat exchange area 3 is a first arc 6-1 and a second arc 6-2 arranged alternately along the width direction. The first arc 6-1 is convex towards the heat exchange area 3, and the second arc 6-2 is convex towards the first flow guiding area 5. The first arc 6-1 is arranged in one-to-one correspondence with the inflection points of the herringbone corrugations 3-1.

[0031] The heat exchange plate includes a plate body 1. As Figure 1As shown, the plate body 1 is, for example, a rectangular plate. In the figure, the L direction is the length direction of the plate body 1, and the W direction is the width direction of the plate body 1. On both sides of the plate body 1 along the length direction, there is a flow guiding area 2 respectively, whose shape is similar to a sector. In the middle of the plate body 1, there is a heat exchange area 3, whose shape is similar to a rectangle. At the end of the plate body 1, there is a corner hole 4.

[0032] As Figure 1 shown, at the corners of the plate body 1, there are four corner holes 4 for the fluid to flow in and out. The fluid can flow in from one of the upper corner holes 4 and flow out from one of the lower corner holes 4, and the specific situation is not limited. In the heat exchange area 3, there are herringbone corrugations 3-1 for disturbing the fluid. In the figure, point a is the inflection point of the herringbone corrugation 3-1, and a1, a2, and a3 are the extension lines of the inflection point. The herringbone corrugation 3-1 has at least two rows of inflection points along the width direction. In each flow guiding area 2, there is a flow guiding channel 2-1 connecting the corner hole 4 and the heat exchange area 3; As Figure 4 and Figure 5 shown, it is a cross-sectional schematic diagram of the flow guiding channel 2-1. As Figure 6 shown is the cross-sectional schematic diagram of the herringbone corrugation 3-1. It can be seen that the flow channel depth of the herringbone corrugation 3-1 is twice that of the flow channel depth of the flow guiding channel 2-1.

[0033] The flow guiding area 2 includes a connected first flow guiding area 5 and a second flow guiding area 6. The first flow guiding area 5 is arranged close to the corner hole 4, and its shape is similar to a triangle. The second flow guiding area 6 is arranged close to the heat exchange area 3 and is a wavy pattern; The edge where the first flow guiding area 5 is connected to the second flow guiding area 6 is a first straight line 5-1 arranged along the width direction, that is Figure 1 shown by the dotted line in the figure. The edge of the second flow guiding area 6 close to the heat exchange area 3 is a first arc 6-1 and a second arc 6-2 arranged alternately along the width direction. The first arc 6-1 protrudes towards the heat exchange area 3, and the second arc 6-2 protrudes towards the first flow guiding area 5. In this way, the boundary between the flow guiding area 2 and the heat exchange area 3 is wavy, which can effectively improve the rigidity of the plate body 1, is beneficial to the pressure bearing during manufacturing and use, and prolongs the service life of the product.

[0034] As Figure 2 shown, in the figure, the extension lines a1, a2, and a3 of the inflection point divide the heat exchange area 3 into four small areas A1, A2, A3, and A4. It is difficult for the fluid between each small area to flow to each other. The first arc 6-1 is arranged in one-to-one correspondence with the inflection point of each row of herringbone corrugations 3-1. In this way, in the second flow guiding area 6, the number of flow guiding channels 2-1 corresponding to the area where the first arc 6-1 close to the corner hole 4 is connected to the corresponding heat exchange area 3 is reduced. As Figure 2 shown in the figure, for the area A1 between the uppermost extension line of the inflection point and the upper edge of the heat exchange area 3, some of the flow guiding channels 2-1 are connected to the extension line a1 of this inflection point. Therefore, the number of flow guiding channels 2-1 connected to this area A1 is reduced, and the fluid flow rate flowing towards the heat exchange area 3 close to the corner hole 4 is also reduced.

[0035] In the second diversion area 6, the number of diversion channels 2-1 corresponding to the area where the first arc 6-1 away from the corner hole 4 communicates with the corresponding heat exchange area 3 increases. For example, Figure 2 in the area A4 between the extension line of the lowest inflection point in [reference] and the lower edge of the heat exchange area 3, some diversion channels 2-1 in other areas are connected to the extension line a3 of this inflection point. Therefore, the number of diversion channels 2-1 communicating with the area A4 increases, and the fluid flow rate flowing towards the heat exchange area 3 away from the corner hole 4 also increases.

[0036] For the middle part of the second diversion area 6, such as Figure 2 the areas A2 and A3 between adjacent extension lines of inflection points in [reference], the number of diversion channels 2-1 will not increase or decrease significantly, and the flow rate will not change significantly either. Thus, the flow distribution in the entire heat exchange area 3 can be made uniform, the heat transfer performance of the product can be improved, and the problem of fouling in the stagnant area can be eliminated.

[0037] Between adjacent inflection points of the herringbone corrugations 3-1, a second arc 6-2 convex towards the first diversion area 5 is provided, so that the herringbone corrugations 3-1 in this area extend towards the diversion area 2, increasing the effective heat transfer area of the heat exchange area 3, and thus improving the heat transfer performance.

[0038] In the combined flow channels of the plate, for the heat exchange area 3, the flow channels formed by two plates usually take the extension line of the inflection point of the herringbone corrugations 3-1 as the boundary. It is difficult for the fluid between the boundaries to flow crosswise after entering the heat exchange area 3 from the diversion area 2. For the area of the extension line of the inflection point of the herringbone corrugations 3-1, because it is the cut-off position of the inclined corrugation flow, the turbulent disturbance is not intense. Therefore, the heat transfer performance in these areas is relatively slightly poor; while in the intermediate area between adjacent extension lines of inflection points, whether it is the upper plate surface flow channel or the lower plate surface flow channel, when the fluid in the diversion area 2 enters the herringbone corrugations 3-1 in the heat exchange area 3, a part will flow along the inclined corrugation in the downstream direction, and another part will cross over the inclined corrugation and enter the other plate surface. However, the fluid on both the upper and lower plate surfaces will pass through the intermediate area, and the flow velocity in the intermediate area is balanced. Therefore, compared with the area of the inflection point, the resistance in the intermediate area is low, and the heat transfer effect is better. In view of this difference, a second arc 6-2 convex towards the diversion area 2 is set to increase the effective heat transfer area of the heat exchange area 3, slightly increase its resistance, make the resistance of the whole plate more balanced, the flow more uniform, and the performance better.

[0039] By setting multi-segment arcs in both positive and negative directions, the number of inlets from the diversion area 2 flowing into the heat exchange area 3 is effectively increased, making the resistance of the overall plate smaller and the product more energy-efficient. In addition, setting multi-segment arcs can effectively improve the rigidity of the plate body 1, especially the rigidity of the boundary area between the heat exchange area 3 and the diversion area 2. Usually, as Figure 6 shown, the corrugation density in the heat exchange area 3 is large, the spacing is small, and the support contact points are very dense, while as Figure 4 and Figure 5As shown, the corrugation pitch in the flow guiding area 2 is large and the contacts are very sparse. Therefore, the flow guiding area 2 is the weak area for the plate to bear pressure. This design can effectively improve the rigidity of this weak area, which is beneficial for manufacturing. At the same time, it can effectively improve the deformation generated during operation and extend the service life.

[0040] This heat exchange plate has a simple structure, is easy to manufacture, has uniform fluid distribution, good heat transfer effect, strong stability, and a long service life.

[0041] In some embodiments, as Figure 2 shown, the edge of the second flow guiding area 6 close to the heat exchange area 3 includes at least three of the first arcs 6-1. The distance between the vertices of the first arcs 6-1 at both ends of the first straight line 5-1 and the first straight line 5-1 is the first distance, and the first distance is positively correlated with the width of the plate body 1.

[0042] As Figure 2 shown, the number of rows of the inflection points of the herringbone corrugations 3-1 in the width direction is three rows, and the vertex of the first arc 6-1 is b; the distance between the vertices of the first arcs 6-1 at both ends of the first straight line 5-1 and the first straight line 5-1 is the first distance, that is, L1. When the width of the plate body 1 is relatively wide, the flow path difference of the fluid flowing from the corner hole 4 to different positions in the heat exchange area 3 is relatively large. By setting a wider first distance, on the one hand, it extends the length of the flow guiding area 2 in the area far from the corner hole 4 and shortens the length of the heat exchange area 3 in this area, which is beneficial for reducing the resistance at a long distance and making the fluid distribution more uniform. On the other hand, the larger L1 is, as Figure 2 shown, the number of flow guiding channels 2-1 flowing from the flow guiding area 2 in the middle to the extension line a3 of the lowest inflection point is more and the flow rate is more sufficient. In the area close to the corner hole 4, the number of flow guiding channels 2-1 flowing from the flow guiding area 2 to the area A1 between the extension line of the uppermost inflection point and the upper edge of the heat exchange area 3 is less and the flow rate also decreases accordingly. Since the distance from the corner hole 4 to the heat exchange area 3 is the shortest in this area, it can just reduce its excessive flow rate.

[0043] In some embodiments, as Figure 2 shown, the distance between the vertex of the first arc 6-1 in the middle of the first straight line 5-1 and the first straight line 5-1 is the second distance, and the ratio of the first distance to the second distance is the first ratio, and the first ratio is positively correlated with the width of the plate body.

[0044] As Figure 2 shown, the distance between the vertex of the first arc 6-1 in the middle of the first straight line 5-1 and the first straight line 5-1 is the second distance, that is, L2. In the middle area in the width direction of the plate, the resistance is usually relatively small and the flow rate is relatively sufficient. In the area farther from the corner hole 4, the resistance is larger.

[0045] For a relatively wide plate width, such as when the width of the plate body 1 is greater than 600 mm, considering that the resistance of the fluid in the area A4 far from the corner hole 4 is relatively large and the overall fluid distribution is extremely uneven, the first spacing can be set to be greater than the second spacing, that is, the first ratio is larger, so that the number of diversion channels 2-1 entering the long-distance is more than that of the diversion channels 2-1 entering the medium-distance, and the fluid resistance is smaller, thereby making the fluid distribution more uniform.

[0046] For a relatively narrow plate width, such as when the width of the plate body 1 is less than 400 mm, considering that the unevenness of the fluid distribution in the area A4 far from the corner hole 4 is relatively not obvious, but the difference in the fluid flow rate between the upper half plate surface (A1 + A2) and the lower half plate surface (A3 + A4) of the plate body 1 is more obvious. The first spacing can be set to be less than the second spacing, that is, the first ratio is smaller, so that the number of diversion channels connected to the extension line a2 of the inflection point is more than that of a3, the overall flow rate entering the lower half plate surface is increased, and the fluid distribution on the two half plate surfaces is more uniform; at the same time, the heat transfer area in the area A4 far from the corner hole 4 is larger, and the heat exchange effect is better.

[0047] In some embodiments, the first ratio is from 0.5 to 1.5.

[0048] When the width of the plate body 1 is greater than 600 mm, the first ratio is from 1.0 to 1.5, such as 1.1, 1.2, 1.3, 1.4 or 1.5, etc., so that the first spacing is larger, the number of diversion channels 2-1 in the area far from the corner hole 4 is more, the fluid flow is more uniform, and it is convenient to manufacture; when the width of the plate body 1 is less than 400 mm, the first ratio is from 0.5 to 1.0, such as 0.5, 0.6, 0.7, 0.8 or 0.9, etc., so that the second spacing is larger, the fluid distribution on the two half plate surfaces is more uniform, the heat transfer performance is good, and it is convenient to manufacture.

[0049] In some embodiments, as Figure 2 shown, the tangent point of the first arc 6-1 and the second arc 6-2 is the first tangent point, the spacing between the first tangent point and the vertex of the adjacent first arc 6-1 in the width direction is the third spacing, and the spacing between the vertices of two adjacent first arcs 6-1 in the width direction is the fourth spacing. The third spacing is less than or equal to 1 / 3 of the fourth spacing.

[0050] As Figure 2As shown in the figure, the tangent point of the first arc 6-1 and the second arc 6-2 in the figure is the first tangent point c; the distance between the first tangent point and the vertex b of the adjacent first arc 6-1 in the width direction is the third distance, that is, L3; the distance between the vertices b of two adjacent first arcs 6-1 in the width direction is the fourth distance, that is, L4; set L3≤1 / 3L4, so that the vertex of the first arc 6-1 can be more convex toward the heat exchange area 3, and in the second diversion area 6 far from the corner hole 4, the number of diversion channels 2-1 connecting to the heat exchange area 3 can be more, while in the second diversion area 6 close to the corner hole 4, the number of diversion channels 2-1 connecting to the heat exchange area 3 can be less, which is more conducive to flow distribution and uniform heat exchange effect.

[0051] In some embodiments, as Figure 2 shown, the edge of the heat exchange area 3 in the length direction is the second straight line 3-2, and the distance between the vertex of the first arc 6-1 at both ends of the first straight line 5-1 and the adjacent second straight line 3-2 is the fifth distance, and the fifth distance is less than the fourth distance.

[0052] As Figure 2 shown, a sealing groove and an edge wrap are provided on the outer periphery of the heat exchange area 3, the corner hole 4 and the diversion area 2, and the upper and lower edges of the heat exchange area 3 are the second straight line 3-2; the distance between the vertex b of the first arc 6-1 at both ends of the first straight line 5-1 and the adjacent second straight line 3-2 is the fifth distance, that is, L5; the distance between the vertices b of two adjacent first arcs 6-1 in the width direction is the fourth distance, that is, L4; set L5<L4, and its main purpose is to reduce the distance from the extension line of the inflection point to the edge of the sealing groove, so that the vertex b of the first arc 6-1 convex toward the heat exchange area 3 is closer to the sealing groove. Then, in the heat exchange area 3 far from the corner hole 4, the percentage increase in the number of diversion channels 2-1 in this area compared to the number of diversion channels 2-1 in this area when the second diversion area 6 is not provided is greater, so that the flow distribution effect is greater, and the problem of uneven flow distribution caused by the flow resistance deviation caused by the distance of the corner hole 4 can be more effectively improved.

[0053] In some embodiments, as Figure 2 and Figure 3 shown, the first arc 6-1 at both ends of the first straight line 5-1 intersects with the first straight line 5-1.

[0054] As Figure 2 and Figure 3 shown, the first arc 6-1 at both ends of the first straight line 5-1 intersects with the first straight line 5-1, and the intersection point is the first intersection point d. Such a setting avoids the intersection of the first arc 6-1 and the second straight line 3-2, which will cause some diversion channels 2-1 in the diversion area 2 to be connected to the sealing groove, the flow channel to be blocked, and a flow dead zone to be formed, reducing the heat exchange effect.

[0055] In some embodiments, asFigure 2 As shown, the intersection points of the first arc 6-1 at both ends of the first straight line 5-1 and the first straight line 5-1 are the first intersection points, and the first intersection points are arranged at a gap from the second straight line 3-2.

[0056] As Figure 3 shown, the first intersection point d is arranged at the intersection position of the first straight line 5-1 and the second straight line 3-2. Since the manufacturing mold of the plate body 1 is usually formed by splicing multiple die core blocks, such an arrangement will cause the die core boundary to cross the concave-convex corrugations of the edge wrap, making it difficult to manufacture and affecting the service life of the mold.

[0057] As Figure 2 shown, the first intersection point d is only arranged on the first straight line 5-1 and is arranged at a gap from the second straight line 3-2. In this way, the die core will not cross the concave-convex corrugations during manufacturing, which is more convenient for manufacturing and protecting the service life of the mold. The distance between the first intersection point d and the adjacent second straight line 3-2 can be less than or equal to 1 / 4 of the fifth distance to ensure the rigidity of the plate body 1.

[0058] In some embodiments, the number of inflection point rows of the herringbone corrugations 3-1 in the width direction is odd, so that the structural stability of the plate body 1 is stronger and it is also convenient for assembly.

[0059] In some embodiments of the present application, a heat exchanger is provided, which includes a plurality of stacked heat exchange plates as described in any of the above embodiments, and a sealing gasket is provided between adjacent heat exchange plates.

[0060] This heat exchanger has the beneficial effects of the corresponding embodiments of the foregoing heat exchange plates, which will not be elaborated herein.

[0061] Those of ordinary skill in the art should understand that: the discussion of any of the above embodiments is only exemplary and is not intended to imply that the scope of the present application (including the claims) is limited to these examples; under the idea of the present application, the technical features between the above embodiments or different embodiments can also be combined, the steps can be implemented in any order, and there are many other variations in different aspects of the embodiments of the present application as described above, and they are not provided in detail for the sake of brevity.

[0062] In addition, in the case of elaborating details to describe the exemplary embodiments of the present application, it is obvious to those skilled in the art that the present application embodiments can be implemented without these details or with changes in these details. Therefore, these descriptions should be considered illustrative rather than restrictive.

[0063] Although the present application has been described in combination with the embodiments of the present application, according to the foregoing description, many substitutions, modifications and variations of these embodiments will be obvious to those of ordinary skill in the art.

[0064] Embodiments of the present application are intended to cover all such substitutions, modifications, and variations that fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the embodiments of the present application shall be included within the protection scope of the present application.

Claims

1. A heat exchange plate, characterized in that, It includes a plate body. On both sides of the plate body along the length direction, there is a diversion area respectively. In the middle, there is a heat exchange area. At the end, there is a corner hole. In the heat exchange area, there are herringbone corrugations. The herringbone corrugations include at least two rows of inflection points along the width direction. In each diversion area, there is a diversion channel connecting the corner hole and the heat exchange area; The diversion area includes a connected first diversion area and a second diversion area. The first diversion area is arranged close to the corner hole. The second diversion area is arranged close to the heat exchange area. The edge where the first diversion area and the second diversion area meet is a first straight line arranged along the width direction. The edge of the second diversion area close to the heat exchange area is a first arc and a second arc arranged alternately along the width direction. The first arc bulges towards the heat exchange area. The second arc bulges towards the first diversion area. The first arc corresponds to the inflection point of the herringbone corrugation one by one.

2. The heat exchange plate according to claim 1, wherein, The edge of the second diversion area close to the heat exchange area includes at least three of the first arcs. The distance between the vertex of the first arc at both ends of the first straight line and the first straight line is a first distance. The first distance is positively correlated with the width of the plate body.

3. The heat exchange plate according to claim 2, wherein, The distance between the vertex of the first arc in the middle of the first straight line and the first straight line is a second distance. The ratio of the first distance to the second distance is a first ratio. The first ratio is positively correlated with the width of the plate body.

4. The heat exchange plate according to claim 3, wherein, The first ratio is from 0.5 to 1.

5.

5. The heat exchange plate according to claim 1, wherein, The tangent point of the first arc and the second arc is a first tangent point. The distance between the first tangent point and the vertex of the adjacent first arc along the width direction is a third distance. The distance between the vertices of two adjacent first arcs along the width direction is a fourth distance. The third distance is less than or equal to 1 / 3 of the fourth distance.

6. The heat exchange plate according to claim 5, characterized in that, The edge of the heat exchange area along the length direction is a second straight line. The distance between the vertex of the first arc at both ends of the first straight line and the adjacent second straight line is a fifth distance. The fifth distance is less than the fourth distance.

7. The heat exchange plate according to claim 6, wherein, The first arcs at both ends of the first straight line intersect with the first straight line.

8. The heat exchange plate according to claim 7, wherein The intersection point of the first arcs at both ends of the first straight line and the first straight line is a first intersection point. The first intersection point is arranged with a gap from the second straight line.

9. The heat exchange plate according to claim 1, wherein, The number of rows of the inflection points of the herringbone corrugations along the width direction is odd.

10. A heat exchanger, characterized in that, It includes a plurality of stacked heat exchange plates as described in any one of claims 1-9. A sealing gasket is arranged between adjacent heat exchange plates.

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