CN112414178A

CN112414178A - Plate heat exchanger and heat exchange plate thereof

Info

Publication number: CN112414178A
Application number: CN202010131835.6A
Authority: CN
Inventors: 李华; 郑希茹; 其他发明人请求不公开姓名
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2020-02-29
Filing date: 2020-02-29
Publication date: 2021-02-26

Abstract

The application provides a plate heat exchanger and a heat exchange plate thereof, wherein the heat exchange plate comprises an inlet area surrounding a refrigerant inlet, an outlet area surrounding a refrigerant outlet, a first main heat exchange area connected with the inlet area, and a second main heat exchange area connected with the outlet area; the heat exchanger is characterized in that a plurality of first salient points are arranged in the first main heat exchange area, a plurality of second salient points are arranged in the second main heat exchange area, the size of the first salient points along the width direction of the plate is larger than that of the second salient points along the width direction of the plate, and the size of the first salient points along the width direction of the plate is larger than that of the first salient points along the length direction of the plate. So set up, strengthened the heat transfer in first main heat transfer region, be favorable to the refrigerant to realize the evaporation trigger effect, improved plate heat exchanger and heat transfer performance of heat transfer slab thereof.

Description

Plate heat exchanger and heat exchange plate thereof

Technical Field

The application relates to a plate heat exchanger and a heat exchange plate sheet thereof, and belongs to the technical field of heat exchange.

Background

The plate heat exchanger is a well-known high-efficiency and compact heat exchanger, can be used for heat exchange between two media (such as secondary refrigerant and refrigerant), and is widely applied to industries such as refrigeration air conditioners, new energy automobiles and the like. The plate heat exchanger in the related art forms mutually-spaced flow channels for two fluids to flow through a plurality of stacked heat exchange plates, and a plurality of raised point-shaped structures are arranged in heat exchange areas of the plates to strengthen heat exchange in the heat exchange process of the two fluids so as to improve the heat exchange performance of the plate heat exchanger.

There is still room for improvement in the related art to further optimize the heat exchange effectiveness of the plates.

Disclosure of Invention

An object of this application is to provide a better plate heat exchanger of heat transfer performance and heat transfer slab thereof.

In a first aspect, the present application relates to a heat exchange plate for a plate heat exchanger, comprising a refrigerant inlet, a refrigerant outlet, an inlet region surrounding the refrigerant inlet, an outlet region surrounding the refrigerant outlet, and a communication region connected between the inlet region and the outlet region, wherein the heat exchange plate forms a flow channel in the communication region for refrigerant to flow from the inlet region to the outlet region;

the communication area comprises a first main heat exchange area and a second main heat exchange area; said first primary heat exchange area being closer to said inlet area than said second primary heat exchange area; said second main heat exchange zone being closer to said outlet region than said first main heat exchange zone; the first main heat exchange area is provided with a plurality of first salient points arranged at intervals, and the second main heat exchange area is provided with a plurality of second salient points arranged at intervals; the plurality of first salient points and the plurality of second salient points are distributed in a plurality of rows along the length direction of the heat exchange plate;

the size of the first salient points along the width direction of the heat exchange plate is larger than or equal to the size of the second salient points along the width direction of the heat exchange plate; and the size of the first salient points along the width direction of the heat exchange plate is larger than that of the first salient points along the length direction of the heat exchange plate.

In the technical scheme provided by the application, the size of the first salient point of the first main heat exchange area along the width direction of the heat exchange plate is larger than that of the first salient point along the length direction of the heat exchange plate, so that the refrigerant is favorable for obtaining better fluid disturbance and plate surface distribution effect when the specific gravity of the liquid phase is higher, thereby being beneficial to strengthening the heat exchange performance of the first main heat exchange area, reducing the liquid phase specific gravity along with the increase of the gas phase specific gravity and the decrease of the liquid phase specific gravity of the refrigerant in the heat exchange process, ensuring that the size of the first salient points along the width direction of the heat exchange plate is larger than that of the second salient points along the width direction of the heat exchange plate, ensuring that the second main heat exchange area is beneficial to providing relatively lower flow pressure drop for the refrigerant than that of the first main heat exchange area, therefore, the refrigerant with a large gas phase can flow out quickly, so that the heat exchange effect of the heat exchange plate is improved and the heat exchange efficiency of the plate heat exchanger is optimized based on the characteristic of gas-liquid two-phase flow of the refrigerant.

In a second aspect, the technical solution adopted by 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 in the communication area for refrigerant to flow from the inlet area to the outlet area;

the size of the first salient points along the width direction of the heat exchange plate is equal to the size of the second salient points along the width direction of the heat exchange plate; the size of the first salient points along the width direction of the heat exchange plate is larger than that of the first salient points along the length direction of the heat exchange plate; the ratio of the sum of the area of the first salient points in the first main heat exchange area to the area of the first main heat exchange area is larger than the ratio of the sum of the area of the second salient points in the second main heat exchange area to the area of the first main heat exchange area.

In the technical scheme provided by the application, the size of the first salient points of the first main heat exchange area along the width direction of the heat exchange plate is larger than that of the first salient points along the length direction of the heat exchange plate, so that better fluid disturbance and plate surface distribution effect of a refrigerant at higher liquid phase specific gravity are obtained, the heat exchange performance of the first main heat exchange area is enhanced, the liquid phase specific gravity is reduced along with the increase of gas phase specific gravity of the refrigerant in the heat exchange process, the size of the second salient points along the width direction of the heat exchange plate is equal to that of the first salient points along the width direction of the heat exchange plate, the ratio of the sum of the area occupied by the second salient points in the second main heat exchange area to the area of the second main heat exchange area is larger than the ratio of the sum of the area of the first salient points in the first main heat exchange area to the area of the first main heat exchange area, and the second main heat exchange area with small distribution density of the salient points is favorable for providing relatively lower, therefore, the refrigerant with a large gas phase can flow out quickly, so that the heat exchange effect of the heat exchange plate is improved and the heat exchange efficiency of the plate heat exchanger is optimized based on the characteristic of gas-liquid two-phase flow of the refrigerant.

Drawings

Fig. 1 is a schematic perspective view of a heat exchanger plate of a plate heat exchanger according to the present application in one embodiment.

Fig. 2 is a perspective view of fig. 1 from another angle.

Fig. 3 is a top view of fig. 1, indicating the different heat exchange areas and the exemplary refrigerant flow directions.

Fig. 4 is a front view of fig. 1.

Fig. 5 is a left side view of fig. 1.

Fig. 6 is an enlarged view of a portion of the inlet area of fig. 3.

FIG. 7 is an enlarged fragmentary view of the first primary heat exchange area of FIG. 3.

Fig. 8 is a partially enlarged view of the first transition region of fig. 3.

Fig. 9 is a partial enlarged view of the turn region in fig. 3.

Fig. 10 is an enlarged view of a portion of the second transition region of fig. 3.

FIG. 11 is an enlarged fragmentary view of the second primary heat exchange area of FIG. 3.

Fig. 12 is an enlarged view of a portion of the exit region of fig. 3.

Fig. 13 is a top view of the first bump of fig. 7 in another embodiment.

Fig. 14 is a top view of a heat exchanger plate of the plate heat exchanger of fig. 3 in another embodiment, in which the different heat exchange areas and the exemplary direction of refrigerant flow are indicated.

Detailed Description

The present application relates to a plate heat exchanger (not shown) including a plurality of heat exchange plates 100 stacked, wherein a first flow channel and a second flow channel are formed between adjacent heat exchange plates 100, the first flow channel is used for a coolant (for example, a cooling liquid) to flow through, and the second flow channel is used for a refrigerant to flow through, so as to realize heat exchange between the two media. Since the basic structure and the working principle of the plate heat exchanger are well known to those skilled in the art, detailed descriptions of the embodiments of the present application are omitted.

Referring to fig. 1 to 13, one 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 region 1 surrounding the refrigerant inlet 11, an outlet region 2 surrounding the refrigerant outlet 21, and a communication region 3 connected between the inlet region 1 and the outlet region 2, the communication region 3 is located between the inlet region 1 and the outlet region 2 in a main flow direction of refrigerant flow, and the heat exchange plate 100 forms a flow channel in the communication region 3 for refrigerant to flow from the inlet region 1 to the outlet region 2.

The communication zone 3 comprises a first main heat exchange zone 4 adjacent to said inlet zone 1 and communicating with said inlet zone 1, a second main heat exchange zone 5 adjacent to said outlet zone 2 and communicating with said outlet zone 2, and a transition zone 6 connected between said first main heat exchange zone 4 and said second main heat exchange zone 5.

Referring to fig. 3, in one embodiment of the present application, the flow channels of the heat exchange plate 100 are U-shaped, that is, the refrigerant flows between the refrigerant inlet 11 and the refrigerant outlet 21 in a U-shaped flow manner, and the transition region 6 includes a first transition region 7 connected to the first main heat exchange region 4 and located downstream of the first main heat exchange region 4 in the main refrigerant flow direction, a second transition region 8 connected to the second main heat exchange region 2 and located upstream of the second main heat exchange region 2 in the main refrigerant flow direction, and a turning region 9 connected between the first transition region 7 and the second transition region 8. Referring to fig. 8 and 10, the length L7 of the first transition area 7 in the length direction L-L of the heat exchanger plate 100 is greater than the length L8 of the second transition area 8 in the length direction L-L of the heat exchanger plate 100.

Referring to fig. 6, the heat exchange plate 100 is provided with a plurality of spaced inlet flow guide protrusions 12 distributed in a direction surrounding the refrigerant inlet 11 in the inlet region 1, so as to enhance distribution of refrigerant flow and improve uniformity and stability of fluid flow at the inlet. Referring to fig. 12, the heat exchange plate 100 is provided with a plurality of outlet guide protrusions 22 distributed around the direction of the refrigerant outlet 21 in the outlet region 2, so as to enhance the distribution of refrigerant circulation and improve the uniformity and stability of fluid flow at the outlet. It should be noted that, referring to fig. 6 and 12, in the embodiment illustrated in the present application, the inlet guide protrusions 12 are uniformly distributed on the major arc C1 around the periphery of the refrigerant inlet 11; the inducer protuberances 22 are evenly distributed on the major arc C2 around the periphery of the refrigerant outlet 21.

In the illustrated embodiment of the present application, please refer to fig. 7 and 11, the first main heat exchanging area 4 is provided with a plurality of first protruding points 41 arranged at intervals, and the second main heat exchanging area 5 is provided with a plurality of second protruding points 51 arranged at intervals. The first hump 41 forms a point wave at the first primary heat exchanging area 4. The second hump 51 forms a point wave at the second primary heat exchanging area 5.

Referring to fig. 1 and 3, in the embodiment shown in the present application, the heat exchange plate 100 is substantially in a round rectangle shape, and includes a top wall 101, a width frame 102 extending along a width direction W-W of the heat exchange plate 100, a length frame 103 extending along a length direction L-L of the heat exchange plate 100, and a partition portion 105, where the width frame 102 and the length frame 103 are bent along an edge of the top wall 101 to form a flange, and an extending direction of the partition portion 105 is the same as the length direction L-L of the heat exchange plate 100. In the illustrated embodiment of the present application, the first protruding point 41 and the second protruding point 51 both protrude upward from the plane of the top wall 101, and the partition 105 protrudes downward from the plane of the top wall 101. The heat exchanger plate 100 comprises a first side (e.g. the upper side in fig. 3) and a second side (e.g. the lower side in fig. 3) separated by the extension direction of the partition 105. The refrigerant inlet 11, the inlet region 1 and the first main heat exchange zone 4 are located on the first side and the refrigerant outlet 21, the outlet region 2 and the second main heat exchange zone 5 are located on the second side.

Referring to fig. 7, in the embodiment illustrated in the present application, a dimension L1 of the first salient point 41 along the width direction W-W of the heat exchanger plate 100 is greater than a dimension L2 of the first salient point 41 along a center line C-C of the length direction L-L of the heat exchanger plate 100. So configured, the distribution effect of the refrigerant near the inlet area can be improved by the relatively large dimension L1 of the first salient point 41 in the width direction W-W of the heat exchanger plate 100; in addition, a heat exchange enhancement measure is taken for the area with the lowest side dryness of the whole refrigerant, so that the local evaporation effect of the liquid phase in the first main heat exchange area 4 is enhanced, and an evaporation trigger effect (lifting onset) is realized. In some embodiments, more than 60% of the first primary heat exchanging area 4 is covered by the first overhang 41. Referring to fig. 7, in an embodiment of the present application, the first bump 41 is a bump with an oval cross section. The direction of the long axis extension line of the ellipse of the first salient point 41 is the same as the width direction W-W of the heat exchange plate 100, and the direction of the short axis extension line of the ellipse of the first salient point 41 is the same as the length direction L-L of the heat exchange plate 100. Of course, in other embodiments, as shown in fig. 13, the first bump 41 may also have a crescent shape. It is understood that in other embodiments, the shape of the first bump 41 may also be a diamond shape, a cashew shape, or a combination of at least two of the foregoing shapes. Referring to fig. 13, when the first convex point 41 has a crescent or a waist shape, the recess 411 of the first convex point 41 is disposed toward the refrigerant inlet 11.

Referring to fig. 7, in one embodiment of the present application, the first protrusions 41 are arranged in a plurality of rows along the length direction L-L of the heat exchanger plate 100, and the first protrusions 41 are arranged in a plurality of columns along the width direction W-W of the heat exchanger plate 100; the first salient points 41 on two adjacent columns are staggered along the length direction L-L of the heat exchange plate 100.

Referring to fig. 11, in the embodiment illustrated in the present application, the second convex points 51 are convex points with an oval cross section, wherein a dimension L3 of the second convex points 51 along a length direction L-L of the heat exchanger plate 100 is larger than a dimension L4 of the second convex points 51 along a center line D-D of a width direction W-W of the heat exchanger plate 100. The direction of the long axis extension line of the ellipse of the second salient point 51 is the same as the length direction L-L of the heat exchange plate 100, and the direction of the short axis extension line of the ellipse of the second salient point 51 is the same as the width direction W-W of the heat exchange plate 100. By the arrangement, the longitudinally arranged ellipse is adopted, and the high-dryness area (evaporation-out point) and the superheat area are facilitated to realize enhanced heat exchange by proper pressure drop and channel structures.

The transition region 6 is provided with a plurality of spaced third protrusions 70 to reduce pressure drop and provide a suitable channel structure for fluid to turn. Referring to fig. 8 and 10, in an embodiment of the present application, the third bumps 70 are bumps with a right circular cross section, and include a plurality of first circular bumps 71 spaced apart from each other in the first transition region 7 and a plurality of second circular bumps 81 spaced apart from each other in the second transition region 8. The first round salient point 71 and the second round salient point 81 are both protruded upwards from the plane of the top wall 101. The first rounded hump 71 forms a point wave at the first transition region 7 and the second rounded hump 81 forms a point wave at the second transition region 8. The first circular salient points 71 are arranged in a plurality of rows along the length direction L-L of the heat exchange plate 100, the first circular salient points 71 are arranged in a plurality of rows along the width direction W-W of the heat exchange plate 100, and the first circular salient points 71 on two adjacent rows are arranged in a staggered manner along the length direction L-L of the heat exchange plate 100. The second round protrusions 81 are arranged in a plurality of rows along the length direction L-L of the heat exchanger plate 100, the second round protrusions 81 are arranged in a plurality of rows along the width direction W-W of the heat exchanger plate 100, and the second round protrusions 81 located on two adjacent rows are arranged in a staggered manner along the length direction L-L of the heat exchanger plate 100.

Under the condition that the dimension L1 of the first bump 41 in the width direction W-W of the heat exchanger plate 100 is larger than the dimension L4 of the second bump 51 in the width direction W-W of the heat exchanger plate 100, the first bump 41 simultaneously satisfies that the dimension L1 of the first bump 41 in the width direction W-W of the heat exchanger plate 100 is larger than the dimension L2 of the first bump 41 in the length direction L-L of the heat exchanger plate 100.

Because the size of the first salient points 41 of the first main heat exchange area 4 along the width direction W-W of the heat exchange plate is larger than the size of the first salient points 41 along the length direction L-L 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 effect when the specific gravity of the liquid phase is higher, thereby being beneficial for strengthening the heat exchange performance of the first main heat exchange area 4, as the specific gravity of the gas phase of the refrigerant is increased and the specific gravity of the liquid phase of the refrigerant is reduced in the heat exchange process, the size of the first salient points 41 along the width direction W-W of the heat exchange plate 100 is larger than the size of the second salient points 51 along the width direction W-W of the heat exchange plate 100, the second main heat exchange area 5 is beneficial for providing relatively lower flow pressure drop for the refrigerant than the first main heat, therefore, the characteristic of gas-liquid two-phase flow of the refrigerant is used, the heat exchange effect of the heat exchange plate is improved, and the heat exchange efficiency of the plate heat exchanger is optimized.

The ratio of the sum of the area of each first bump 41 in the first main heat exchange area 4 to the area of the first main heat exchange area 4 is greater than the ratio of the sum of the area of each second bump 51 in the second main heat exchange area 5 to the area of the second main heat exchange area 5. The first plurality of protrusions 41 having a relatively large sum of areas in the first primary heat exchange area 4 can provide a relatively large flow resistance, so that the flow path of the refrigerant is relatively meandering, which is a good means for enhancing heat exchange.

In some embodiments, the ratio of the dimension L1 of the first salient point 41 along the width direction W-W of the heat exchanger plate 100 to the dimension L2 along the length direction L-L of the heat exchanger plate 100 is recorded as a first ratio; the ratio of the dimension L4 of the second salient point 51 in the width direction W-W of the heat exchanger plate 100 to the dimension L3 in the length direction L-L of the heat exchanger plate 100 is denoted as a second ratio, and the first ratio is larger than the second ratio.

The dimension L1 of the first salient point 41 along the width direction W-W of the heat exchanger plate 100 is greater than or equal to the dimension L31 of the third salient point 70 along the width direction W-W of the heat exchanger plate 100, and the dimension L31 of the third salient point 70 along the width direction W-W of the heat exchanger plate 100 is greater than or equal to the dimension L4 of the second salient point 51 along the width direction W-W of the heat exchanger plate 100; that is, when the dimension L1 of the first bump 41 in the width direction W-W of the heat exchanger plate 100 is equal to the dimension L31 of said third bump 70 in the width direction W-W of the heat exchanger plate 100, the dimension L31 of the third bump 70 in the width direction W-W of the heat exchanger plate 100 is larger than the dimension L4 of said second bump 51 in the width direction W-W of the heat exchanger plate 100. When the dimension L1 of the first overhang 41 in the width direction W-W of the heat exchanger plate 100 is larger than the dimension L31 of said third overhang 70 in the width direction W-W of the heat exchanger plate 100, the dimension L31 of the third overhang 70 in the width direction W-W of the heat exchanger plate 100 may be equal to or larger than the dimension L4 of said second overhang 51 in the width direction W-W of the heat exchanger plate 100.

The ratio of the dimension L31 of the third bump 70 along the width direction W-W of the heat exchanger plate 100 to the dimension L32 along the length direction L-L of the heat exchanger plate 100 is denoted as a third ratio, the first ratio is larger than the third ratio, and the third ratio is larger than the second ratio.

The first ratio, the third ratio and the second ratio are sequentially decreased in a descending manner, so that the tortuous degree of the flow path of the fluid in the three areas is gradually reduced, which is related to the trend that the gas phase specific gravity of the refrigerant is increased and the liquid phase specific gravity of the refrigerant is reduced in the flowing process, and therefore the refrigerant matched with the gas-liquid two-phase flow can achieve better heat exchange efficiency.

The channel structure of the second main heat exchange area 5 is beneficial to providing a relatively lower flow pressure drop for the refrigerant than that of the first main heat exchange area 4, so that the refrigerant with a relatively large gas phase can flow out quickly, the residence time of the refrigerant with relatively weak heat exchange capacity on the plate is reduced, and the influence on the heat exchange performance of the plate is reduced, so that the heat exchange effect of the heat exchange plate 100 is beneficial to being improved and the heat exchange performance of the plate heat exchanger is optimized based on the characteristic of gas-liquid two-phase flow of the refrigerant.

In some embodiments, the dimension L1 of the first overhang 41 in the width direction W-W of the heat exchanger plate 100 is equal to the dimension L4 of the second overhang 51 in the width direction W-W of the heat exchanger plate 100; and the dimension L1 of the first salient point 41 along the width direction W-W of the heat exchanger plate 100 is greater than the dimension L2 of the first salient point 41 along the length direction L-L of the heat exchanger plate 100; the ratio of the sum of the area of each first protrusion 41 in the first primary heat exchange area 4 to the area of the first primary heat exchange area 4 is greater than the ratio of the sum of the area of each second protrusion 51 in the second primary heat exchange area 5 to the area of the second primary heat exchange area 5.

The first bumps 41 and the second bumps 51 may be bump structures with completely opposite shapes and sizes, but the distance between two adjacent first bumps 41 in the same row is smaller than that between two adjacent second bumps 51 in the same row. So that the density distribution of the first bump 41 is larger than that of the second bump 51 in the respective heat transfer regions. The first bulges 41 and the second bulges 51 may also have unequal shapes and sizes, and although the first bulges 41 and the second bulges 51 have the same size in the width direction W-W of the heat exchanger plate 100, the size of the first bulges 41 in the length direction L-L of the heat exchanger plate 100 may be smaller than the size of the second bulges 51 in the length direction L-L of the heat exchanger plate 100. The number of rows of the first protrusions 41 is larger than the number of rows of the second protrusions 51 in the length direction L-L of the heat exchanger plate 100 in the heat exchanger zone of the same area.

The purpose of doing so is also be favorable to reducing the distribution density of the convex point structure in the second main heat transfer region 5 for second main heat transfer region 5 is favorable to providing the flow pressure drop for the refrigerant that is relatively low than first main heat transfer region 4, thereby makes the gaseous phase account for the refrigerant that is bigger can flow out fast, thereby does benefit to reducing the dwell time of the refrigerant that the heat transfer ability is relatively weak at the slab, reduces the influence to slab heat transfer performance.

Referring to fig. 7 and 8, in order to enhance heat exchange, the ratio of the length L5 of the first main heat exchange area 4 along the length direction L-L of the heat exchange plate 100 to the length L7 of the first transition area 7 along the length direction L-L of the heat exchange plate 100 is X, and X is greater than or equal to 5:5 and less than or equal to 8: 2. In some specific embodiments, X ═ 6: 4.

Referring to fig. 3, a refrigerant inlet 11 and a refrigerant outlet 21 are located on the same side (right side in fig. 3) of the heat exchange plate 100 in the length direction L-L, and the refrigerant inlet 11 and the refrigerant outlet 21 are arranged in line along the width direction W-W of the heat exchange plate 100. The heat exchange plates 100 comprise a secondary refrigerant inlet 91 and a secondary refrigerant outlet 92 which are located in the turning region 9, the secondary refrigerant inlet 91 and the secondary refrigerant outlet 92 are located on the same side (on the left side in fig. 3) of the length direction L-L of the heat exchange plate 100, and the secondary refrigerant inlet 91 and the secondary refrigerant outlet 92 are arranged in alignment along the width direction W-W of the heat exchange plate 100. The coolant outlet 92 is located at the first side and the coolant inlet 91 is located at the second side. Of course, in other embodiments, the refrigerant inlet 11 and the refrigerant outlet 21 may be diagonally disposed. Referring to fig. 3, a first flow-through section S1 with the smallest flow area is disposed between the coolant inlet 91 and the width frame 102 of the heat exchange plate 100, a second flow-through section S2 with the smallest flow area is disposed between the coolant inlet 91 and the second transition region 8, a third flow-through section S3 with the smallest flow area is disposed between the coolant outlet 21 and the width frame 102 of the heat exchange plate 100, a fourth flow-through section S4 with the smallest flow area is disposed between the coolant outlet 21 and the first transition region 7, a ratio of a cross-sectional area of the first flow-through section S1 to a cross-sectional area of the second flow-through section S2 is Y, where Y is greater than or equal to 1:1 and less than or equal to 1: 3; the ratio of the sectional area of the third flow-through section S3 to the sectional area of the fourth flow-through section S4 is Z, and Z is greater than or equal to 1:1 and less than or equal to 1: 3. So set up, through the flow distribution that increases the outer turn, let gaseous state refrigerant smuggle liquid state refrigerant can turn round more smoothly, prevent the gas-liquid separation phenomenon.

The first transition region 7 is connected with the first main heat exchange region 4, and the first transition region 7 is positioned at the first side; the second transition zone 8 is connected to the second main heat exchange zone 5 and the second transition zone 8 is located at the second side, and the turning zone 9 extends from the first side to the second side.

In addition, as shown in fig. 3, 7 and 11, the heat exchange plate 100 includes a plurality of bypass preventing protrusions 104 extending from the inner edge of the length frame 103 to the first main heat exchange area 4 and the second main heat exchange area 5, so as to prevent the refrigerant from flowing in a straight line along the length frame 103 without 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.

Referring to fig. 14, in another embodiment of the present application, the flow channel of the heat exchanger plate 100 is I-shaped, the first main heat exchange area 4, the transition area 6, and the second main heat exchange area 5 are sequentially arranged along the length direction L-L of the heat exchanger plate 100, and the three areas may extend from the length edge of one side of the heat exchanger plate 100 to the length edge of the other side of the heat exchanger plate 100, so that the three areas are aligned. The refrigerant inlet 11 and the refrigerant outlet 21 are located on the same side of the heat exchange plate 100 in the width direction W-W, and the refrigerant inlet 11 and the refrigerant outlet 21 are arranged in alignment along the length direction L-L of the heat exchange plate 100; the heat exchange plate 100 comprises a secondary refrigerant outlet 92 positioned below the refrigerant inlet 11 and a secondary refrigerant inlet 91 positioned below the refrigerant outlet 21, and accordingly, the secondary refrigerant inlet 91 and the secondary refrigerant outlet 92 are arranged in alignment along the length direction L-L of the heat exchange plate 100. The plurality of first bumps 41 located in the first main heat exchanging region 4, the plurality of second bumps 51 located in the second main heat exchanging region 5, and the third bump 70 located in the transition region 6 are the same as those in the embodiments shown in fig. 1 to 13, and are not described herein again.

The above embodiments are only used for illustrating the present application and not for limiting the technical solutions described in the present application, and the present application should be understood based on the descriptions of directions such as "left", "right", "upper", "lower", etc. for those skilled in the art, and although the present application has been described in detail in the present application with reference to the above embodiments, those skilled in the art should understand that those skilled in the art can still make modifications or equivalent substitutions on the present application, and all technical solutions and modifications thereof that do not depart from the spirit and scope of the present application should be covered in the claims of the present application.

Claims

1. A heat exchanger 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 refrigerant to flow from the inlet area (1) to the outlet area (2); the method is characterized in that:

the communication area (3) comprises a first main heat exchange area (4) and a second main heat exchange area (5); said first primary heat exchange area (4) being closer to said inlet area (1) than said second primary heat exchange area (5); -said second main heat transfer zone (5) is closer to said outlet region (2) than said first main heat transfer zone (4); the first main heat exchange area (4) is provided with a plurality of first salient points (41) arranged at intervals, and the second main heat exchange area (5) is provided with a plurality of second salient points (51) arranged at intervals; the plurality of first salient points (41) and the plurality of second salient points (51) are distributed in a plurality of rows along the length direction (L-L) of the heat exchange plate (100);

the dimension (L1) of the first salient point (41) along the width direction (W-W) of the heat exchanger plate (100) is larger than the dimension (L4) of the second salient point (51) along the width direction (W-W) of the heat exchanger plate (100); and the dimension (L1) of the first salient point (41) along the width direction (W-W) of the heat exchanger plate (100) is larger than the dimension (L2) of the first salient point (41) along the length direction (L-L) of the heat exchanger plate (100).

2. A heat exchanger plate (100) according to claim 1, wherein the ratio of the sum of the area of the first portholes (41) in the first main heat exchanging area (4) to the area of the first main heat exchanging area (4) is larger than the ratio of the sum of the area of the second portholes (51) in the second main heat exchanging area (5) to the area of the second main heat exchanging area (5).

3. A heat exchanger plate (100) according to claim 1 or 2, wherein: the communication zone (3) further comprises a transition zone (6) connected between the first main heat exchange zone (4) and the second main heat exchange zone (5); the transition region (6) is provided with a plurality of third salient points (70) which are arranged at intervals; the dimension (L1) of the first salient point (41) along the width direction (W-W) of the heat exchanger plate (100) is greater than or equal to the dimension (L31) of the third salient point (70) along the width direction (W-W) of the heat exchanger plate (100), and the dimension (L31) of the third salient point (70) along the width direction (W-W) of the heat exchanger plate (100) is greater than or equal to the dimension (L4) of the second salient point (51) along the width direction (W-W) of the heat exchanger plate (100);

the ratio of the dimension (L1) of the first salient point (41) along the width direction (W-W) of the heat exchange plate (100) to the dimension (L2) along the length direction (L-L) of the heat exchange plate (100) is recorded as a first ratio; the ratio of the dimension (L4) of the second salient point (51) along the width direction (W-W) of the heat exchange plate (100) to the dimension (L3) along the length direction (L-L) of the heat exchange plate (100) is recorded as a second ratio; the ratio of the dimension (L31) of the third salient point (70) along the width direction (W-W) of the heat exchange plate (100) to the dimension (L32) along the length direction (L-L) of the heat exchange plate (100) is recorded as a third ratio; the first ratio is greater than the third ratio, which is greater than the second ratio.

4. A heat exchanger plate (100) according to claim 3, wherein the heat exchanger plate (100) comprises partitions (105), the partitions (105) extending in the same direction as the length direction (L-L) of the heat exchanger plate (100);

the heat exchanger plate (100) comprises a first side and a second side separated by the extension direction of the partition (105), the refrigerant inlet (11), the inlet region (1) and the first main heat transfer zone (4) being located at the first side; the refrigerant outlet (21), the outlet area (2) and the second main heat transfer area (5) are located on the second side;

the refrigerant inlet (11) and the refrigerant outlet (21) are positioned on the same side of the heat exchange plate (100) in the length direction (L-L); said first main heat transfer zone (4) being connected to said inlet zone (1); the second main heat exchange zone (5) is connected to the outlet zone (2).

5. The heat exchanger plate (100) according to claim 4, wherein the transition zone (6) comprises a first transition zone (7), a second transition zone (8) and a turn zone (9) connected between the first transition zone (7) and the second transition zone (8), the first transition zone (7) being connected to the first main heat exchange zone (4) and the first transition zone (7) being located at the first side; the second transition zone (8) is connected with the second main heat exchange zone (5) and the second transition zone (8) is positioned at the second side, and the turning zone (9) extends from the first side to the second side; the third bumps (70) are respectively distributed in the first transition region (7) and the second transition region (8).

6. The heat exchanger plate (100) according to claim 5, wherein the first elevations (41) and the second elevations (51) are both elevations with an oval cross-section, and the third elevations (70) are elevations with a right circular cross-section;

the direction of the long axis extension line of the ellipse of the first salient point (41) is the same as the width direction (W-W) of the heat exchange plate (100), and the direction of the short axis extension line of the ellipse of the first salient point (41) is the same as the length direction (L-L) of the heat exchange plate (100); the direction of the long axis extension line of the ellipse of the second salient point (51) is the same as the length direction (L-L) of the heat exchange plate (100), and the direction of the short axis extension line of the ellipse of the second salient point (51) is the same as the width direction (W-W) of the heat exchange plate (100).

7. A heat exchanger plate (100) according to claim 5 or 6, wherein: the ratio of the length (L5) of the first main heat exchange area (4) in the length direction (L-L) of the heat exchange plate (100) to the length (L7) of the first transition area (7) in the length direction (L-L) of the heat exchange plate (100) is X, and X is more than or equal to 5:5 and less than or equal to 8: 2.

8. The heat exchanger plate (100) according to claim 7, wherein the heat exchanger plate (100) comprises a coolant inlet (91) and a coolant outlet (92) in the turning region (9); the coolant outlet (92) is located on the first side and the coolant inlet (91) is located on the second side; a first flow-through section (S1) with the smallest flow cross-sectional area is arranged between the secondary refrigerant inlet (91) and the width frame (102) of the heat exchange plate (100) close to the secondary refrigerant inlet (91), a second flow-through section (S2) with the smallest flow cross-sectional area is arranged between the secondary refrigerant inlet (91) and the second transition region (8), a third flow-through section (S3) with the smallest flow cross-sectional area is arranged between the secondary refrigerant outlet (92) and the width frame (102) of the heat exchange plate (100) close to the secondary refrigerant outlet (92), and a fourth flow-through section (S4) with the smallest flow cross-sectional area is arranged between the secondary refrigerant outlet (92) and the first transition region (7), wherein the ratio of the sectional area of the first flow-through section (S1) to the sectional area of the second flow-through section (S2) is Y, and Y is more than or less than 1:1 and less than or equal to 1; the ratio of the sectional area of the third flow-through section (S3) to the sectional area of the fourth flow-through section (S4) is Z, and Z is greater than or equal to 1:1 and less than or equal to 1: 3.

9. A heat exchanger plate (100) according to claim 3, wherein: the refrigerant inlet (11) and the refrigerant outlet (21) are positioned on two sides of the heat exchange plate (100) in the length direction (L-L); wherein the refrigerant inlet (11) and the refrigerant outlet (21) are located on the same side of the heat exchange plate (100) in the width direction (W-W), or the refrigerant inlet (11) and the refrigerant outlet (21) are diagonally arranged; said first main heat transfer zone (4) being connected to said inlet zone (1); the second main heat exchange zone (5) is connected to the outlet zone (2).

10. A heat exchanger plate (100) according to any of claims 1 to 9, wherein: the heat exchanger plate (100) comprises a length border (103) extending in a length direction (L-L) of the heat exchanger plate (100) and an anti-bypass protrusion (104) extending from an inner edge of the length border (103) towards the first main heat exchange area (4) and the second main heat exchange area (5).

11. A heat exchanger plate (100) according to claim 1 or 2, wherein: the heat exchange plate (100) is provided with a plurality of inlet flow guide bulges (12) which are spaced from each other in the inlet area (1), and the inlet flow guide bulges (12) are distributed along the direction surrounding the refrigerant inlet (11); and the heat exchange plate (100) is provided with a plurality of outlet guide bulges (22) in the outlet area (2), and the outlet guide bulges (12) are distributed along the direction surrounding the refrigerant outlet (21).

12. A heat exchanger 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 refrigerant to flow from the inlet area (1) to the outlet area (2); the method is characterized in that:

the dimension (L1) of the first salient point (41) along the width direction (W-W) of the heat exchanger plate (100) is equal to the dimension (L4) of the second salient point (51) along the width direction (W-W) of the heat exchanger plate (100); and the dimension (L1) of the first salient point (41) along the width direction (W-W) of the heat exchanger plate (100) is larger than the dimension (L2) of the first salient point (41) along the length direction (L-L) of the heat exchanger plate (100); the ratio of the sum of the area occupied by each first salient point (41) in the first main heat exchange area (4) to the area of the first main heat exchange area (4) is larger than the ratio of the sum of the area occupied by each second salient point (51) in the second main heat exchange area (5) to the area of the second main heat exchange area (5).

13. A plate heat exchanger, characterized in that it comprises a plurality of heat exchange plates (100) according to any one of claims 1 to 12, and a plurality of said heat exchange plates (100) are stacked to form a first flow channel and a second flow channel which are spaced from each other, wherein the first flow channel is used for the circulation of a secondary refrigerant, and the second flow channel is used for the circulation of a refrigerant.