Plate heat exchanger and its heat exchange plates

Abstract

The present application provides a plate heat exchanger and a heat exchange plate thereof, wherein the heat exchange plate comprises an inlet region surrounding a refrigerant inlet, an outlet region surrounding a refrigerant outlet, a first main heat exchange region connected to the inlet region, and a second main heat exchange region connected to the outlet region; a plurality of first convex points are arranged in the first main heat exchange region, a plurality of second convex points are arranged in the second main heat exchange region, the size of the first convex points along the width direction of the plate is greater than the size of the second convex points along the width direction of the plate, and the size of the first convex points along the width direction of the plate is greater than the size of the first convex points along the length direction of the plate. Such an arrangement strengthens the heat exchange of the first main heat exchange region, is conducive to the realization of the evaporation triggering effect of the refrigerant, and improves the heat exchange performance of the plate heat exchanger and its heat exchange plate.

Description

Technical Field

[0001] The present application relates to a plate heat exchanger and a heat exchange plate thereof, and belongs to the technical field of heat exchange. Background Art

[0002] Plate heat exchangers are recognized as efficient and compact heat exchangers that can be used for heat exchange between two media (such as coolant and refrigerant), and have been widely used in refrigeration and air conditioning, new energy vehicles and other industries. The plate heat exchanger in the related art forms mutually spaced flow channels for the flow of two fluids through a number of stacked heat exchange plates, and a number of raised point structures are arranged in the heat exchange area of ​​the plate to enhance the heat exchange process of the two fluids, so as to improve the heat exchange performance of the plate heat exchanger.

[0003] However, there is still room for improvement in the relevant technology to further optimize the heat exchange effect of the plates. Summary of the invention

[0004] The purpose of the present application is to provide a plate heat exchanger and a heat exchange plate thereof with good heat exchange performance.

[0005] In a first aspect, the technical solution adopted in the present application relates to a heat exchange plate of a plate heat exchanger, which comprises a refrigerant inlet, a refrigerant outlet, an inlet area surrounding the refrigerant inlet, an outlet area surrounding the refrigerant outlet, and a communication area connected between the inlet area and the outlet area, wherein the heat exchange plate forms a flow channel for the refrigerant to flow from the inlet area to the outlet area in the communication area;

[0006] The connecting area includes a first main heat exchange area and a second main heat exchange area; the first main heat exchange area is closer to the inlet area than the second main heat exchange area; the second main heat exchange area is closer to the outlet area than the first main heat exchange area; the first main heat exchange area is provided with a plurality of first convex points arranged at intervals, and the second main heat exchange area is provided with a plurality of second convex points arranged at intervals; the plurality of first convex points and the plurality of second convex points are both distributed in multiple rows along the length direction of the heat exchange plate;

[0007] The dimension of the first protrusion along the width direction of the heat exchange plate is greater than or equal to the dimension of the second protrusion along the width direction of the heat exchange plate; and the dimension of the first protrusion along the width direction of the heat exchange plate is greater than the dimension of the first protrusion along the length direction of the heat exchange plate.

[0008] In the technical solution provided in the present application, since the size of the first protrusion of the first main heat exchange area along the width direction of the heat exchange plate is larger than the size of the first protrusion along the length direction of the heat exchange plate, it is beneficial for the refrigerant to obtain better fluid disturbance and plate surface distribution effects when the liquid specific gravity is high, thereby helping to enhance the heat exchange performance of the first main heat exchange area. As the gas specific gravity of the refrigerant increases and the liquid specific gravity decreases during the heat exchange process, the size of the first protrusion along the width direction of the heat exchange plate is larger than the size of the second protrusion along the width direction of the heat exchange plate. The second main heat exchange area is beneficial to providing the refrigerant with a relatively lower flow pressure drop than the first main heat exchange area, thereby allowing the refrigerant with a larger gas phase ratio to flow out quickly. Based on the characteristics of the gas-liquid two-phase flow of the refrigerant, this is beneficial to improving the heat exchange effect of the heat exchange plate and optimizing the heat exchange efficiency of the plate heat exchanger.

[0009] In a second aspect, the technical solution adopted in the present application relates to a heat exchange plate of a plate heat exchanger, which comprises a refrigerant inlet, a refrigerant outlet, an inlet area surrounding the refrigerant inlet, an outlet area surrounding the refrigerant outlet, and a communication area connected between the inlet area and the outlet area, wherein the heat exchange plate forms a flow channel for the refrigerant to flow from the inlet area to the outlet area in the communication area;

[0010] The connecting area includes a first main heat exchange area and a second main heat exchange area; the first main heat exchange area is closer to the inlet area than the second main heat exchange area; the second main heat exchange area is closer to the outlet area than the first main heat exchange area; the first main heat exchange area is provided with a plurality of first convex points arranged at intervals, and the second main heat exchange area is provided with a plurality of second convex points arranged at intervals; the plurality of first convex points and the plurality of second convex points are both distributed in multiple rows along the length direction of the heat exchange plate;

[0011] The dimension of the first protrusion along the width direction of the heat exchange plate is equal to the dimension of the second protrusion along the width direction of the heat exchange plate; and the dimension of the first protrusion along the width direction of the heat exchange plate is greater than the dimension of the first protrusion along the length direction of the heat exchange plate; the ratio of the sum of the areas occupied by each of the first protrusions in the first main heat exchange region to the area of ​​the first main heat exchange region is greater than the ratio of the sum of the areas occupied by each of the second protrusions in the second main heat exchange region to the area of ​​the first main heat exchange region.

[0012] In the technical solution provided in the present application, since the size of the first protrusion of the first main heat exchange area along the width direction of the heat exchange plate is larger than the size of the first protrusion along the length direction of the heat exchange plate, it is beneficial for the refrigerant to obtain better fluid disturbance and plate surface distribution effects when the liquid specific gravity is high, thereby enhancing the heat exchange performance of the first main heat exchange area. As the gas specific gravity of the refrigerant increases and the liquid specific gravity decreases during the heat exchange process, the size of the second protrusion along the width direction of the heat exchange plate is equal to the size of the first protrusion along the width direction of the heat exchange plate, and the ratio of the sum of the area occupied by each second protrusion in the second main heat exchange area to the area of ​​the second main heat exchange area is greater than the ratio of the sum of the area of ​​each first protrusion in the first main heat exchange area to the area of ​​the first main heat exchange area. Therefore, the second main heat exchange area with a smaller protrusion distribution density is beneficial to providing the refrigerant with a relatively lower flow pressure drop than the first main heat exchange area, so that the refrigerant with a larger proportion of gas phase can flow out quickly. In this way, based on the characteristics of the gas-liquid two-phase flow of the refrigerant, it is beneficial to improve the heat exchange effect of the heat exchange plate and optimize the heat exchange efficiency of the plate heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 It is a three-dimensional schematic diagram of a heat exchange plate of a plate heat exchanger of the present application in one embodiment.

[0014] Figure 2 yes Figure 1 A three-dimensional diagram from another angle.

[0015] Figure 3 yes Figure 1 A top view of the heat exchanger is shown with different heat exchange areas and schematic refrigerant flow directions indicated.

[0016] Figure 4 yes Figure 1 main view.

[0017] Figure 5 yes Figure 1 Left view of .

[0018] Figure 6 yes Figure 3 A partial enlarged view of the middle import area.

[0019] Figure 7 yes Figure 3 A partial enlarged view of the first main heat exchange area.

[0020] Figure 8 yes Figure 3 A partial enlarged view of the first transition area.

[0021] Fig. 9 yes Figure 3 A partial enlarged view of the mid-turn area.

[0022] Fig.10yes Figure 3 A partial enlarged view of the second transition area.

[0023] Fig.11 yes Figure 3 A partial enlarged view of the second main heat exchange area.

[0024] Fig.12 yes Figure 3 A partial enlarged view of the middle exit area.

[0025] Fig.13 yes Figure 7 A top view of the first bump in another embodiment.

[0026] Fig.14 yes Figure 3 A top view of a heat exchange plate of a center plate heat exchanger in another embodiment, wherein different heat exchange areas and schematic refrigerant flow directions are indicated. DETAILED DESCRIPTION

[0027] The present application relates to a plate heat exchanger (not shown), which includes a plurality of stacked heat exchange plates 100, wherein adjacent heat exchange plates 100 form mutually spaced first and second flow channels, wherein the first flow channel is used for circulating a coolant (such as a cooling liquid), and the second flow channel is used for circulating a refrigerant, so as to achieve heat exchange between the two media. Since the basic structure and working principle of the plate heat exchanger are already well known to those skilled in the art, they will not be described in detail in the specific implementation of the present application.

[0028] Please refer to Figures 1 to 13 As shown, an embodiment of the present application discloses a heat exchange plate 100 of a plate heat exchanger, which includes a refrigerant inlet 11, a refrigerant outlet 21, an inlet area 1 surrounding the refrigerant inlet 11, an outlet area 2 surrounding the refrigerant outlet 21, and a connecting area 3 connected between the inlet area 1 and the outlet area 2, wherein the connecting area 3 is located between the inlet area 1 and the outlet area 2 along the main flow direction of the refrigerant flow, and the heat exchange plate 100 forms a flow channel for the refrigerant to flow from the inlet area 1 to the outlet area 2 in the connecting area 3.

[0029] The connecting area 3 includes a first main heat exchange area 4 close to the inlet area 1 and connected to the inlet area 1, a second main heat exchange area 5 close to the outlet area 2 and connected to the outlet area 2, and a transition area 6 connected between the first main heat exchange area 4 and the second main heat exchange area 5.

[0030] Please refer to Figure 3As shown, in one embodiment of the present application, the flow channel of the heat exchange plate 100 is U-shaped, that is, the refrigerant flows between the refrigerant inlet 11 and the refrigerant outlet 21 in a U-shaped flow, and the transition area 6 includes a first transition area 7 connected to the first main heat exchange area 4 and located downstream of the first main heat exchange area 4 in the main flow direction of the refrigerant, a second transition area 8 connected to the second main heat exchange area 2 and located upstream of the second main heat exchange area 2 in the main flow direction of the refrigerant, and a turning area 9 connected between the first transition area 7 and the second transition area 8. Please refer to Figure 8 and Fig.10 As shown, a length L7 of the first transition region 7 along the length direction LL of the heat exchange plate 100 is greater than a length L8 of the second transition region 8 along the length direction LL of the heat exchange plate 100 .

[0031] Please refer to Figure 6 As shown, the heat exchange plate 100 is provided with a plurality of inlet guide protrusions 12 spaced apart from each other in the inlet area 1 and distributed in a direction around the refrigerant inlet 11, so as to strengthen the distribution of the refrigerant flow and improve the uniformity and stability of the fluid flow at the inlet. Fig.12 As shown, the heat exchange plate 100 is provided with a plurality of outlet guide protrusions 22 spaced apart from each other in the outlet area 2 and distributed around the refrigerant outlet 21 to strengthen the distribution of the refrigerant flow and improve the uniformity and stability of the fluid flow at the outlet. Figure 6 and Fig.12 As shown, in the embodiment illustrated in the present application, the inlet guide protrusions 12 are evenly distributed on the major arc C1 around the periphery of the refrigerant inlet 11 ; the outlet guide protrusions 22 are evenly distributed on the major arc C2 around the periphery of the refrigerant outlet 21 .

[0032] In the embodiment shown in the present application, please refer to Figure 7 and Fig.11 As shown, the first main heat exchange region 4 is provided with a plurality of first convex points 41 arranged at intervals, and the second main heat exchange region 5 is provided with a plurality of second convex points 51 arranged at intervals. The first convex points 41 form point waves located in the first main heat exchange region 4. The second convex points 51 form point waves located in the second main heat exchange region 5.

[0033] Please refer to Figure 1 and Figure 3As shown, in the embodiment illustrated in the present application, the heat exchange plate 100 is roughly in the shape of a rounded rectangle, which includes a top wall 101, a width frame 102 extending along the width direction WW of the heat exchange plate 100, a length frame 103 extending along the length direction LL of the heat exchange plate 100, and a partition 105, wherein the width frame 102 and the length frame 103 are bent along the edge of the top wall 101 to form a flange, and the extension direction of the partition 105 is the same as the length direction LL of the heat exchange plate 100. In the embodiment illustrated in the present application, the first protrusion 41 and the second protrusion 51 both protrude upward from the plane where the top wall 101 is located, and the partition 105 protrudes downward from the plane where the top wall 101 is located. The heat exchange plate 100 includes a first side (e.g. Figure 3 the upper side) and the second side (e.g. Figure 3 The refrigerant inlet 11, the inlet region 1 and the first main heat exchange region 4 are located on the first side, and the refrigerant outlet 21, the outlet region 2 and the second main heat exchange region 5 are located on the second side.

[0034] Please refer to Figure 7 As shown, in the embodiment illustrated in the present application, the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is larger than the dimension L2 of the first protrusion 41 at the center line CC along the length direction LL of the heat exchange plate 100. In this way, the relatively large dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 can improve the distribution effect of the refrigerant near the inlet area; in addition, enhanced heat exchange measures are taken for the area with the lowest dryness on the entire refrigerant side, thereby enhancing the local evaporation effect of the liquid phase in the first main heat exchange area 4 and realizing the evaporation triggering effect (boiling onset). In some embodiments, more than 60% of the first main heat exchange area 4 is covered by the first protrusion 41. Please refer to Figure 7 As shown, in one embodiment of the present application, the first protrusion 41 is a protrusion with an elliptical cross section. The direction of the long axis extension line of the ellipse of the first protrusion 41 is the same as the width direction WW of the heat exchange plate 100, and the direction of the short axis extension line of the ellipse of the first protrusion 41 is the same as the length direction LL of the heat exchange plate 100. Of course, in other embodiments, please refer to Fig.13 As shown, the shape of the first protrusion 41 may also be a crescent shape. It is understood that in other embodiments, the shape of the first protrusion 41 may also be a diamond shape, a cashew shape, or a combination of at least two of the above shapes. Fig.13As shown, when the shape of the first protrusion 41 is a crescent shape or a cashew shape, the notch 411 of the first protrusion 41 is arranged toward the refrigerant inlet 11 .

[0035] Please refer to Figure 7 As shown, in one embodiment of the present application, the first protrusions 41 are arranged in multiple rows along the length direction LL of the heat exchange plate 100, and the first protrusions 41 are arranged in multiple columns along the width direction WW of the heat exchange plate 100; the first protrusions 41 located in two adjacent columns are staggered along the length direction LL of the heat exchange plate 100.

[0036] Please refer to Fig.11 As shown, in the embodiment illustrated in the present application, the second convex point 51 is a convex point with an elliptical cross section, wherein the dimension L3 of the second convex point 51 along the length direction LL of the heat exchange plate 100 is greater than the dimension L4 of the second convex point 51 at the center line DD along the width direction WW of the heat exchange plate 100. The direction of the long axis extension line of the ellipse of the second convex point 51 is the same as the length direction LL of the heat exchange plate 100, and the direction of the short axis extension line of the ellipse of the second convex point 51 is the same as the width direction WW of the heat exchange plate 100. In this way, the longitudinally arranged ellipse is adopted, and the appropriate pressure drop and channel structure are used to facilitate the enhanced heat exchange in the high dryness zone (evaporation heat exchange dry-out point) and the overheating zone.

[0037] The transition area 6 is provided with a plurality of third protrusions 70 arranged at intervals to appropriately reduce the pressure drop and provide a suitable channel structure for the fluid turning. Figure 8 and Fig.10As shown, in one embodiment of the present application, the third protrusion 70 is a protrusion with a perfect circular cross section, which includes a plurality of first circular protrusions 71 arranged at intervals in the first transition area 7 and a plurality of second circular protrusions 81 arranged at intervals in the second transition area 8. The first circular protrusions 71 and the second circular protrusions 81 both protrude upward from the plane where the top wall 101 is located. The first circular protrusions 71 form a point wave located in the first transition area 7, and the second circular protrusions 81 form a point wave located in the second transition area 8. The first circular protrusions 71 are arranged in multiple rows along the length direction LL of the heat exchange plate 100, and the first circular protrusions 71 are arranged in multiple columns along the width direction WW of the heat exchange plate 100, and the first circular protrusions 71 located in two adjacent columns are arranged alternately along the length direction LL of the heat exchange plate 100. The second circular protrusions 81 are arranged in multiple rows along the length direction LL of the heat exchange plate 100 , and are arranged in multiple columns along the width direction WW of the heat exchange plate 100 . The second circular protrusions 81 located in two adjacent columns are staggered along the length direction LL of the heat exchange plate 100 .

[0038] Under the condition that the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is greater than the dimension L4 of the second protrusion 51 along the width direction WW of the heat exchange plate 100, the first protrusion 41 also satisfies that the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is greater than the dimension L2 of the first protrusion 41 along the length direction LL of the heat exchange plate 100.

[0039] Since the size of the first convex point 41 of the first main heat exchange area 4 along the width direction WW of the heat exchange plate is larger than the size of the first convex point 41 along the length direction LL of the heat exchange plate 100, the flow path of the refrigerant is relatively tortuous, which is beneficial for the refrigerant to obtain better fluid disturbance and plate surface distribution effects when the liquid specific gravity is high, thereby facilitating the enhancement of the heat exchange performance of the first main heat exchange area 4. As the gas specific gravity of the refrigerant increases and the liquid specific gravity decreases during the heat exchange process, the size of the first convex point 41 along the width direction WW of the heat exchange plate 100 is larger than the size of the second convex point 51 along the width direction WW of the heat exchange plate 100. The second main heat exchange area 5 is beneficial for providing the refrigerant with a relatively lower flow pressure drop than the first main heat exchange area 51, thereby allowing the refrigerant with a larger gas phase ratio to flow out quickly. Based on the characteristics of the gas-liquid two-phase flow of the refrigerant, this is beneficial for improving the heat exchange effect of the heat exchange plate and optimizing the heat exchange efficiency of the plate heat exchanger.

[0040] The ratio of the sum of the areas occupied by the first convex points 41 in the first main heat exchange region 4 to the area of ​​the first main heat exchange region 4 is greater than the ratio of the sum of the areas of the second convex points 51 in the second main heat exchange region 5 to the area of ​​the second main heat exchange region 5. Providing a plurality of first convex points 41 with a relatively large sum of areas in the first main heat exchange region 4 can provide a relatively large flow resistance, thereby making the flow path of the refrigerant relatively tortuous, which is a better means of enhancing heat exchange.

[0041] In some embodiments, the ratio of the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 to the dimension L2 along the length direction LL of the heat exchange plate 100 is recorded as a first ratio; the ratio of the dimension L4 of the second protrusion 51 along the width direction WW of the heat exchange plate 100 to the dimension L3 along the length direction LL of the heat exchange plate 100 is recorded as a second ratio, and the first ratio is greater than the second ratio.

[0042] The dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is greater than or equal to the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100, and the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100 is greater than or equal to the dimension L4 of the second protrusion 51 along the width direction WW of the heat exchange plate 100; that is, when the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is equal to the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100, the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100 is greater than the dimension L4 of the second protrusion 51 along the width direction WW of the heat exchange plate 100. When the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is greater than the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100, the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100 may be greater than or equal to the dimension L4 of the second protrusion 51 along the width direction WW of the heat exchange plate 100.

[0043] The ratio of the dimension L31 of the third protrusion 70 along the width direction WW of the heat exchange plate 100 to the dimension L32 along the length direction LL of the heat exchange plate 100 is recorded as a third ratio, the first ratio is greater than the third ratio, and the third ratio is greater than the second ratio.

[0044] The first ratio, the third ratio and the second ratio decrease successively, so that the tortuosity of the flow path of the fluid in the three areas gradually decreases, which is related to the trend that the gas phase density increases and the liquid phase density decreases during the flow of the refrigerant, which is conducive to the refrigerant with gas-liquid two-phase flow to achieve better heat exchange efficiency.

[0045] The channel structure of the second main heat exchange zone 5 is conducive to providing the refrigerant with a relatively lower flow pressure drop than the first main heat exchange zone 4, so that the refrigerant with a relatively large gas phase ratio can flow out quickly, thereby helping to reduce the residence time of the refrigerant with relatively weak heat exchange capacity on the plate and reduce the impact on the heat exchange performance of the plate. Based on the characteristics of the gas-liquid two-phase flow of the refrigerant, this is conducive to improving the heat exchange effect of the heat exchange plate 100 and optimizing the heat exchange performance of the plate heat exchanger.

[0046] In some embodiments, the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is equal to the dimension L4 of the second protrusion 51 along the width direction WW of the heat exchange plate 100; and the dimension L1 of the first protrusion 41 along the width direction WW of the heat exchange plate 100 is greater than the dimension L2 of the first protrusion 41 along the length direction LL of the heat exchange plate 100; the ratio of the sum of the areas occupied by each first protrusion 41 in the first main heat exchange region 4 to the area of ​​the first main heat exchange region 4 is greater than the ratio of the sum of the areas of each second protrusion 51 in the second main heat exchange region 5 to the area of ​​the second main heat exchange region 5.

[0047] The first convex point 41 and the second convex point 51 may be convex point structures with completely opposite shapes and sizes, but the spacing between two adjacent first convex points 41 in the same row is smaller than that between two adjacent second convex points 51 in the same row. Therefore, the density distribution of the first convex points 41 in the corresponding heat exchange area is larger than that of the second convex points 51. The first convex points 41 and the second convex points 51 may also be unequal in shape and size. Although the first convex points 41 and the second convex points 51 have the same size along the width direction WW of the heat exchange plate 100, the size of the first convex point 41 along the length direction LL of the heat exchange plate 100 may be smaller than the size of the second convex point 51 along the length direction LL of the heat exchange plate 100. In the heat exchange area of ​​the same area, the number of rows of the first convex points 41 distributed along the length direction LL of the heat exchange plate 100 is greater than the number of rows of the second convex points 51 distributed.

[0048] The purpose of doing so is also to help reduce the distribution density of the convex point structure in the second main heat exchange area 5, so that the second main heat exchange area 5 is conducive to providing the refrigerant with a relatively lower flow pressure drop than the first main heat exchange area 4, so that the refrigerant with a relatively large proportion of gas phase can flow out quickly, thereby helping to reduce the residence time of the refrigerant with relatively weak heat exchange capacity on the plate and reduce the impact on the heat exchange performance of the plate.

[0049] Please refer to Figure 7 and Figure 8As shown, in order to enhance heat exchange, the ratio of the length L5 of the first main heat exchange region 4 along the length direction LL of the heat exchange plate 100 to the length L7 of the first transition region 7 along the length direction LL of the heat exchange plate 100 is X, 5:5≤X≤8:2. In some specific embodiments, X=6:4.

[0050] Please refer to Figure 3 As shown, the refrigerant inlet 11 and the refrigerant outlet 21 are located on the same side of the length direction LL of the heat exchange plate 100 (eg Figure 3 The refrigerant inlet 11 and the refrigerant outlet 21 are arranged in alignment along the width direction WW of the heat exchange plate 100. The heat exchange plate 100 includes a brine inlet 91 and a brine outlet 92 located in the turning area 9. The brine inlet 91 and the brine outlet 92 are located on the same side of the length direction LL of the heat exchange plate 100 (as shown in FIG. Figure 3 The brine inlet 91 and the brine outlet 92 are arranged in alignment along the width direction WW of the heat exchange plate 100. The brine outlet 92 is located on the first side, and the brine inlet 91 is located on the second side. Of course, in other embodiments, the refrigerant inlet 11 and the refrigerant outlet 21 may also be arranged diagonally. Figure 3 As shown, a first flow cross section S1 with the smallest flow area is provided between the brine inlet 91 and the width frame 102 of the heat exchange plate 100, a second flow cross section S2 with the smallest flow area is provided between the brine inlet 91 and the second transition area 8, a third flow cross section S3 with the smallest flow area is provided between the brine outlet 21 and the width frame 102 of the heat exchange plate 100, and a fourth flow cross section S4 with the smallest flow area is provided between the brine outlet 21 and the first transition area 7, the ratio of the cross-sectional area of ​​the first flow cross section S1 to the cross-sectional area of ​​the second flow cross section S2 is Y, 1:1≤Y≤1:3; the ratio of the cross-sectional area of ​​the third flow cross section S3 to the cross-sectional area of ​​the fourth flow cross section S4 is Z, 1:1≤Z≤1:3. In this way, by increasing the flow distribution of the outer bend, the gaseous refrigerant entrained with the liquid refrigerant can turn more smoothly, preventing the gas-liquid separation phenomenon.

[0051] The first transition area 7 is connected to the first main heat exchange area 4 and is located on the first side; the second transition area 8 is connected to the second main heat exchange area 5 and is located on the second side, and the turning area 9 extends from the first side to the second side.

[0052] In addition, please refer to Figure 3 , Figure 7 and Fig.11As shown, the heat exchange plate 100 includes a plurality of anti-bypass protrusions 104 extending from the inner edge of the length frame 103 toward the first main heat exchange area 4 and the second main heat exchange area 5, thereby preventing the refrigerant from flowing in a straight line along the length frame 103 instead of flowing through the first main heat exchange area 4 and the second main heat exchange area 5 in the middle of the heat exchange plate 100.

[0053] Please refer to Fig.14 As shown, in another embodiment of the present application, the flow channel of the heat exchange plate 100 is I-shaped, and the first main heat exchange area 4, the transition area 6 and the second main heat exchange area 5 are arranged in sequence along the length direction LL of the heat exchange plate 100. The three areas can extend from the length edge of one side of the heat exchange plate 100 to the length edge of the other side, so that the three areas are arranged in alignment. The refrigerant inlet 11 and the refrigerant outlet 21 are located on the same side of the width direction WW of the heat exchange plate 100, and the refrigerant inlet 11 and the refrigerant outlet 21 are arranged in alignment along the length direction LL of the heat exchange plate 100; the heat exchange plate 100 includes a refrigerant outlet 92 located below the refrigerant inlet 11 and a refrigerant inlet 91 located below the refrigerant outlet 21, and accordingly, the refrigerant inlet 91 and the refrigerant outlet 92 are arranged in alignment along the length direction LL of the heat exchange plate 100. The first convex points 41 located in the first main heat exchange region 4, the second convex points 51 located in the second main heat exchange region 5, and the third convex points 70 located in the transition region 6 are all connected to the first convex points 41 located in the first main heat exchange region 4, the second convex points 51 located in the second main heat exchange region 5, and the third convex points 70 located in the transition region 6. Figures 1 to 13 The embodiments shown are the same and will not be described again.

[0054] The above embodiments are only used to illustrate the present application but not to limit the technical solutions described in the present application. The understanding of this specification should be based on the technical personnel in the relevant technical field. For example, for the description of directions such as "left", "right", "up", and "down", although this specification has described the present application in detail with reference to the above embodiments, ordinary technical personnel in the field should understand that technical personnel in the relevant technical field can still modify or make equivalent substitutions to the present application, and all technical solutions and improvements thereof that do not depart from the spirit and scope of the present application should be included in the scope of the claims of the present application.

Claims

1. A heat exchange plate (100) of a plate heat exchanger, comprising a refrigerant inlet (11), a refrigerant outlet (21), an inlet area (1) surrounding the refrigerant inlet (11), an outlet area (2) surrounding the refrigerant outlet (21), and a communication area (3) connected between the inlet area (1) and the outlet area (2); the heat exchange plate (100) forms a flow channel in the communication area (3) for the refrigerant to flow from the inlet area (1) to the outlet area (2); characterized in that: The connecting region (3) comprises a first main heat exchange region (4) and a second main heat exchange region (5); the first main heat exchange region (4) is closer to the inlet region (1) than the second main heat exchange region (5); the second main heat exchange region (5) is closer to the outlet region (2) than the first main heat exchange region (4); the first main heat exchange region (4) is provided with a plurality of first convex points (41) arranged at intervals, and the second main heat exchange region (5) is provided with a plurality of second convex points (51) arranged at intervals; the plurality of first convex points (41) and the plurality of second convex points (51) are both distributed in multiple rows along the length direction (LL) of the heat exchange plate (100); The size (L1) of the first protrusion (41) along the width direction (WW) of the heat exchange plate (100) is greater than the size (L4) of the second protrusion (51) along the width direction (WW) of the heat exchange plate (100); and the size (L1) of the first protrusion (41) along the width direction (WW) of the heat exchange plate (100) is greater than the size (L2) of the first protrusion (41) along the length direction (LL) of the heat exchange plate (100).

2. The heat exchange plate (100) according to claim 1, characterized in that: The ratio of the sum of the areas occupied by the first protrusions (41) in the first main heat exchange region (4) to the area of ​​the first main heat exchange region (4) is greater than the ratio of the sum of the areas occupied by the second protrusions (51) in the second main heat exchange region (5) to the area of ​​the second main heat exchange region (5).

3. The heat exchange plate (100) according to claim 1 or 2, characterized in that: The connecting area (3) further comprises a transition area (6) connected between the first main heat exchange area (4) and the second main heat exchange area (5); the transition area (6) is provided with a plurality of third protrusions (70) arranged at intervals; the size (L1) of the first protrusion (41) along the width direction (WW) of the heat exchange plate (100) is greater than or equal to the size (L31) of the third protrusion (70) along the width direction (WW) of the heat exchange plate (100), and the size (L31) of the third protrusion (70) along the width direction (WW) of the heat exchange plate (100) is greater than or equal to the size (L4) of the second protrusion (51) along the width direction (WW) of the heat exchange plate (100); The ratio of the size (L1) of the first protrusion (41) along the width direction (WW) of the heat exchange plate (100) to the size (L2) along the length direction (LL) of the heat exchange plate (100) is recorded as a first ratio; the ratio of the size (L4) of the second protrusion (51) along the width direction (WW) of the heat exchange plate (100) to the size (L3) along the length direction (LL) of the heat exchange plate (100) is recorded as a second ratio; the ratio of the size (L31) of the third protrusion (70) along the width direction (WW) of the heat exchange plate (100) to the size (L32) along the length direction (LL) of the heat exchange plate (100) is recorded as a third ratio; the first ratio is greater than the third ratio, and the third ratio is greater than the second ratio.

4. The heat exchange plate (100) according to claim 3, characterized in that: The heat exchange plate (100) comprises a partition (105), and an extension direction of the partition (105) is the same as a length direction (LL) of the heat exchange plate (100); The heat exchange plate (100) comprises a first side and a second side separated by an extension direction of the partition (105); the refrigerant inlet (11), the inlet area (1) and the first main heat exchange area (4) are located on the first side; the refrigerant outlet (21), the outlet area (2) and the second main heat exchange area (5) are located on the second side; The refrigerant inlet (11) and the refrigerant outlet (21) are located on the same side of the heat exchange plate (100) in the length direction (LL); the first main heat exchange area (4) is connected to the inlet area (1); and the second main heat exchange area (5) is connected to the outlet area (2).

5. The heat exchange plate (100) according to claim 4, characterized in that: The transition region (6) comprises a first transition region (7), a second transition region (8) and a turning region (9) connected between the first transition region (7) and the second transition region (8); the first transition region (7) is connected to the first main heat exchange region (4) and the first transition region (7) is located on the first side; the second transition region (8) is connected to the second main heat exchange region (5) and the second transition region (8) is located on the second side; the turning region (9) extends from the first side to the second side; the plurality of third convex points (70) are respectively distributed in the first transition region (7) and the second transition region (8).

6. The heat exchange plate (100) according to claim 5, characterized in that: The first convex point (41) and the second convex point (51) are both convex points with elliptical cross-sections, and the third convex point (70) is a convex point with a perfect circular cross-section; The direction of the major axis extension line of the ellipse of the first convex point (41) is the same as the width direction (WW) of the heat exchange plate (100), and the direction of the minor axis extension line of the ellipse of the first convex point (41) is the same as the length direction (LL) of the heat exchange plate (100); the direction of the major axis extension line of the ellipse of the second convex point (51) is the same as the length direction (LL) of the heat exchange plate (100), and the direction of the minor axis extension line of the ellipse of the second convex point (51) is the same as the width direction (WW) of the heat exchange plate (100).

7. The heat exchange plate (100) according to claim 5 or 6, characterized in that: The ratio of the length (L5) of the first main heat exchange region (4) along the length direction (LL) of the heat exchange plate (100) to the length (L7) of the first transition region (7) along the length direction (LL) of the heat exchange plate (100) is X, 5:5≤X≤8:

2.

8. The heat exchange plate (100) according to claim 7, characterized in that: The heat exchange plate (100) comprises a refrigerant inlet (91) and a refrigerant outlet (92) located in the turning area (9); the refrigerant outlet (92) is located on the first side, and the refrigerant inlet (91) is located on the second side; a first flow section (S1) with the smallest flow cross-sectional area is provided between the refrigerant inlet (91) and the width frame (102) of the heat exchange plate (100) to which it is adjacent, a second flow section (S2) with the smallest flow cross-sectional area is provided between the refrigerant inlet (91) and the second transition area (8), and the refrigerant outlet (92) is provided at the first side. A third flow section (S3) with the smallest flow cross-sectional area is provided between (92) and the width frame (102) of the heat exchange plate (100) adjacent to it, and a fourth flow section (S4) with the smallest flow cross-sectional area is provided between the refrigerant outlet (92) and the first transition area (7), wherein the ratio of the cross-sectional area of ​​the first flow section (S1) to the cross-sectional area of ​​the second flow section (S2) is Y, 1:1≤Y≤1:3; and the ratio of the cross-sectional area of ​​the third flow section (S3) to the cross-sectional area of ​​the fourth flow section (S4) is Z, 1:1≤Z≤1:

3.

9. The heat exchange plate (100) according to claim 3, characterized in that: The refrigerant inlet (11) and the refrigerant outlet (21) are located on both sides of the length direction (LL) of the heat exchange plate (100); wherein the refrigerant inlet (11) and the refrigerant outlet (21) are located on the same side of the width direction (WW) of the heat exchange plate (100), or the refrigerant inlet (11) and the refrigerant outlet (21) are arranged diagonally; the first main heat exchange region (4) is connected to the inlet region (1); and the second main heat exchange region (5) is connected to the outlet region (2).

10. The heat exchange plate (100) according to claim 1, characterized in that: The heat exchange plate (100) comprises a length frame (103) extending along a length direction (LL) of the heat exchange plate (100) and an anti-bypass protrusion (104) extending from an inner edge of the length frame (103) toward the first main heat exchange region (4) and the second main heat exchange region (5).

11. The heat exchange plate (100) according to claim 1 or 2, characterized in that: The heat exchange plate (100) is provided with a plurality of inlet flow guide protrusions (12) spaced apart from each other in the inlet region (1), and the plurality of inlet flow guide protrusions (12) are distributed in a direction surrounding the refrigerant inlet (11); and the heat exchange plate (100) is provided with a plurality of outlet flow guide protrusions (22) in the outlet region (2), and the plurality of outlet flow guide protrusions (22) are distributed in a direction surrounding the refrigerant outlet (21).

12. A heat exchange plate (100) of a plate heat exchanger, comprising a refrigerant inlet (11), a refrigerant outlet (21), an inlet area (1) surrounding the refrigerant inlet (11), an outlet area (2) surrounding the refrigerant outlet (21), and a communication area (3) connected between the inlet area (1) and the outlet area (2); the heat exchange plate (100) forms a flow channel in the communication area (3) for the refrigerant to flow from the inlet area (1) to the outlet area (2); characterized in that: The connecting region (3) comprises a first main heat exchange region (4) and a second main heat exchange region (5); the first main heat exchange region (4) is closer to the inlet region (1) than the second main heat exchange region (5); the second main heat exchange region (5) is closer to the outlet region (2) than the first main heat exchange region (4); the first main heat exchange region (4) is provided with a plurality of first convex points (41) arranged at intervals, and the second main heat exchange region (5) is provided with a plurality of second convex points (51) arranged at intervals; the plurality of first convex points (41) and the plurality of second convex points (51) are both distributed in multiple rows along the length direction (LL) of the heat exchange plate (100); The size (L1) of the first protrusion (41) along the width direction (WW) of the heat exchange plate (100) is equal to the size (L4) of the second protrusion (51) along the width direction (WW) of the heat exchange plate (100); and the size (L1) of the first protrusion (41) along the width direction (WW) of the heat exchange plate (100) is greater than the size (L2) of the first protrusion (41) along the length direction (LL) of the heat exchange plate (100); and the ratio of the sum of the areas occupied by each of the first protrusions (41) in the first main heat exchange region (4) to the area of ​​the first main heat exchange region (4) is greater than the ratio of the sum of the areas of each of the second protrusions (51) in the second main heat exchange region (5) to the area of ​​the second main heat exchange region (5).

13. A plate heat exchanger, characterized in that: Comprising a plurality of heat exchange plates (100) as claimed in any one of claims 1 to 12, wherein the plurality of heat exchange plates (100) are stacked to form a first flow channel and a second flow channel spaced apart from each other, wherein the first flow channel is used for circulating a coolant, and the second flow channel is used for circulating a refrigerant.

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