CN219037717U

CN219037717U - Plate heat exchanger

Info

Publication number: CN219037717U
Application number: CN202223154541.9U
Authority: CN
Inventors: 张婷; 张凌杰; 张小彬; 周高飞; 张建康
Original assignee: Zhejiang Sanhua Plate Exchange Technology Co ltd
Current assignee: Zhejiang Sanhua Plate Exchange Technology Co ltd
Priority date: 2022-11-25
Filing date: 2022-11-25
Publication date: 2023-05-16
Anticipated expiration: 2032-11-25

Abstract

The application provides a plate heat exchanger, which comprises a plurality of first plates and a plurality of second plates, wherein each of the first plates and the second plates comprises two long sides, one of the two long sides is a first long side, the other long side is a second long side, each of the first plates and the second plates is provided with a first corner hole, and compared with the second long side, the first corner hole is closer to the first long side; the first slab has first slab ripple, and first slab ripple includes the first ripple that is close to first angular aperture, and first ripple has first ripple section, first intermediate ripple section and second ripple section at least partially, and first ripple section extends towards first long limit slope, and second ripple section extends towards second long limit slope, and first ripple section and second ripple section form first contained angle, and first intermediate ripple section has first ripple angle, and the angle of first contained angle is less than the angle of first ripple angle. The application is through first corrugated be close to two long limit ripple sections and all be the structure of buckling, improves plate heat exchanger's intensity.

Description

Plate heat exchanger

Technical Field

The application belongs to the heat exchanger field, and specifically relates to a plate heat exchanger.

Background

The plate heat exchanger has the advantages of compact structure, high heat exchange coefficient, strong reliability, small refrigerant filling amount and the like, and is widely applied to refrigeration and heating systems as an evaporator, a condenser, an economizer and the like.

The herringbone waves are arranged on the plate sheets of the plate heat exchanger, the areas where the corner holes are located are required to bear higher pressure, the herringbone wave shapes on the plate sheets in the related technology are kept consistent, the welding points of the waves of the adjacent plate sheets in the areas where the corner holes are located are fewer, the plate is low in strength and poor in pressure resistance in the corner hole areas, fluid leakage is easy to occur in the application process, and more waves are arranged in the corner hole areas, so that the distribution and heat exchange performance of fluid at the corner holes are affected.

Disclosure of Invention

To solve the above problems, the present application aims to provide a plate heat exchanger capable of improving strength.

The application provides a plate heat exchanger, which comprises a plurality of first plates and a plurality of second plates, wherein the first plates and the second plates are alternately overlapped along the thickness direction of the plate heat exchanger; the first plate and the second plate each comprise two long sides, the long sides extend along the length direction of the plate heat exchanger, one of the two long sides is a first long side, the other long side is a second long side, the first plate and the second plate are provided with first corner holes, and compared with the second long sides, the first corner holes are closer to the first long sides;

the first slab has first slab ripple, first slab ripple is including being close to first ripple in first angle hole, first ripple has first ripple section, first intermediate ripple section and second ripple section at least partially, first intermediate ripple section connects first ripple section and second ripple section, first ripple section orientation first long limit slope extension, second ripple section orientation second long limit slope extension, first ripple section and second ripple section form first contained angle, first intermediate ripple section has first ripple angle, the angle of first contained angle is less than the angle of first ripple angle.

The application provides a plate heat exchanger, first ripple near the first angular hole has first ripple section, first middle ripple section and second ripple section to first contained angle that first ripple section and second ripple section formed is less than the first ripple angle of first middle ripple section, makes first ripple be close to two long limit ripple sections and all is the structure of buckling, has prolonged ripple length, helps increasing more phase points between the adjacent slab, and then improves plate heat exchanger's intensity.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are needed in the description of the embodiments will be briefly described below, it being obvious that the drawings in the following description are only some embodiments of the present application, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a perspective view of a plate heat exchanger provided in an embodiment of the present application;

fig. 2 is an exploded view of a plate heat exchanger according to an embodiment of the present application;

fig. 3 is a partial structural view of a plate heat exchanger according to an embodiment of the present application;

FIG. 4 is a front view of a first plate in an embodiment of the present application;

FIG. 5 is a front view of a second plate in an embodiment of the present application;

FIG. 6 is an enlarged view of the structure of the portion A of FIG. 4;

FIG. 7 is an enlarged view of the structure of the portion B of FIG. 5;

fig. 8 is a diagram illustrating a corrugated network structure of a plate heat exchanger according to an embodiment of the present application;

FIG. 9 is a block diagram of a third corrugation having first protrusions between adjacent first corrugation segments in accordance with an embodiment of the present application;

FIG. 10 is an exploded view of the back side of a first plate and an adjacent second plate in this embodiment;

fig. 11 is a structural view of the first connecting portion in the present embodiment;

FIG. 12 is an exploded view of the front face of a first plate and an adjacent second plate in this embodiment;

fig. 13 is an exploded view of the first and second plate corrugations in this embodiment.

Detailed Description

For a better understanding of the technical solutions of the present application, embodiments of the present application are described in detail below with reference to the accompanying drawings.

It should be understood that the described embodiments are merely some, but not all, of the embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art based on the embodiments herein without making any inventive effort, are intended to be within the scope of the present application.

As shown in fig. 1 to 3, the present embodiment provides a plate heat exchanger including a plurality of first plates 1 and a plurality of second plates 2, the plurality of first plates 1 and the plurality of second plates 2 being alternately stacked along a thickness direction (T-T direction as shown in fig. 2) of the plate heat exchanger; in addition, the plate heat exchanger has a plurality of first inter-plate channels 5 and a plurality of second inter-plate channels 6, the plurality of first inter-plate channels 5 and the plurality of second inter-plate channels 6 being alternately arranged along the thickness direction of the plate heat exchanger, the first inter-plate channels 5 and the second inter-plate channels 6 not communicating with each other. In this embodiment, the first inter-plate channel 5 is located between the front face of the first plate 1 and the back face of the adjacent second plate 2, and the second inter-plate channel 6 is located between the back face of the first plate 1 and the front face of the adjacent second plate 2.

Referring to fig. 4 and 5, and referring to fig. 1 to 3, each of the first plate 1 and the second plate 2 includes two long sides 3, the long sides 3 extend along a length direction (L-L direction shown in fig. 2, 4, 5) of the plate heat exchanger, one of the two long sides 3 is a first long side 3a, the other is a second long side 3b, and the first long side 3a and the second long side 3b are disposed opposite to each other along a width direction (W-W direction shown in fig. 2, 4, 5) of the plate heat exchanger; the first plate 1 and the second plate 2 each have a first corner hole C1, the first corner hole C1 being closer to the first long side 3a than to the second long side 3 b. The first plate 1 and the second plate 2 comprise two short sides 4, wherein the short sides 4 extend along the width direction of the plate heat exchanger, one of the two short sides 4 is a first short side 4a, and the other short side 4b; the first short side 4a and the second short side 4b are oppositely arranged along the length direction of the plate heat exchanger; the length of the long side 3 is longer than that of the short side 4; the first corner hole C1 is disposed closer to the first short side 4a than the second short side 4b. In other words, the first corner hole C1 is located at a corner position formed by the first long side 3a and the first short side 4 a.

In this embodiment, the plate heat exchanger is perpendicular to each other in the longitudinal direction (L-L direction), the width direction (W-W direction), and the thickness direction (T-T direction) of the plate heat exchanger.

In this embodiment, the first inter-plate channels 5 are used for circulating the refrigerant, the first angular holes C1 are used for allowing the refrigerant to flow into the first inter-plate channels 5, and the second inter-plate channels 6 are used for circulating a heat exchange medium, such as water, which exchanges heat with the refrigerant.

The first corner hole C1 is used as an inlet of the refrigerant, and needs to bear a certain pressure, so that a fluid distribution area where the first corner hole C1 is located is required to have higher compression resistance, in the related art, after the adjacent plates are stacked and brazed, the tail ends of the waves (one end close to the edge of the plates) possibly have the condition of failing to be connected with the waves on the adjacent plates, so that the welding points are fewer, the strength of the unjoined parts is weakened, the compression resistance is low, the problems of pressure-bearing and unwelding, cracking, fluid leakage and the like of the plates are easy to occur in the application process, and a more conventional herringbone wave mode (namely, the wave distribution pitch is reduced) is adopted, so that the distribution performance of the fluid at the corner hole and the heat exchange performance of the whole plate heat exchanger are influenced. For this, the present embodiment adopts the following design:

referring to fig. 4 again, the first plate 1 has a first plate corrugation 10, the second plate 2 has a second plate corrugation 20, and in the adjacent plates, the first plate corrugation 10 and the second plate corrugation 20 are staggered, and the intersections of the peaks and the troughs of the corrugations are welding surfaces. The first plate corrugation 10 comprises a first corrugation 10a near the first corner hole C1, the first corrugation 10a at least partly having a first corrugation segment 10a1, a first intermediate corrugation segment 10a2 and a second corrugation segment 10a3, the first intermediate corrugation segment 10a2 connecting the first corrugation segment 10a1 and the second corrugation segment 10a3, the first corrugation segment 10a1 extending obliquely towards the first long side 3a, the second corrugation segment 10a3 extending obliquely towards the second long side 3b, the first corrugation segment 10a1 and the second corrugation segment 10a3 forming a first angle β1, the first intermediate corrugation segment 10a2 having a first corrugation angle α1, the angle of the first angle β1 being smaller than the angle of the first corrugation angle α1. In this embodiment, the first intermediate corrugated section 10a2 is a herringbone wave, the opening angles of the first included angle β1 and the first corrugated angle α1 face the first short side 4a, two ends of the first intermediate corrugated section 10a2 extend obliquely to corresponding long sides through the first corrugated section 10a1 and the second corrugated section 10a3 respectively, the angle of the first included angle β1 formed by the first corrugated section 10a1 and the second corrugated section 10a3 is smaller than the first corrugated angle α1 of the first intermediate corrugated section 10a2, in other words, the first corrugated section 10a is in a bending structure at one end close to the long side to form a bending angle, so that compared with the common conventional corrugated in the related art, the extending length of the corrugated is prolonged, more welding points can be increased after the two ends are in butt joint with the adjacent second plate 2, the welding area of the adjacent plate in the fluid distribution area of the first corner hole C1 is further increased, the structural strength of the plate heat exchanger near the first corner hole C1 is naturally improved, the performance of the plate heat exchanger at the position of the first corner hole C1 is further improved, the pressure-resistant property of the plate heat exchanger is reduced, the pressure-resistant joint probability of the plate heat exchanger is reduced, the fluid distribution situation of the plate heat exchanger is broken, and the leakage probability occurs in the fluid distribution process of the position of the plate heat exchanger is reduced, and the pressure-resistant joint probability of the plate heat exchanger is formed; moreover, the corrugation of the distribution part where the first corner hole C1 is arranged adopts a bending design, so that additional corrugation is not required to be added, the corrugation is prolonged, the expansion of the corrugation can be better utilized to distribute the fluid of the refrigerant flowing into the first corner hole C1, and the distribution performance and the heat exchange performance of the fluid of the plate heat exchanger at the first corner hole C1 are improved. In some embodiments, the angle of the first corrugation angle α1 is 90 ° or greater; the angle of the first included angle beta 1 is larger than or equal to 60 degrees and smaller than the angle of the first ripple angle alpha 1, namely, the angle is larger than or equal to 60 degrees and is smaller than or equal to beta 1 and smaller than alpha 1.

Further, the first plate 1 and the second plate 2 each have a second angular hole C2, and the second angular holes C2 are disposed closer to the second short side 4b than to the first short side 4 a. In this embodiment, the second corner hole C2 is used as an inlet of a heat exchange medium for exchanging heat with the refrigerant, and the heat exchange medium enters the second plate-to-plate channel 6, so that the fluid distribution area where the second corner hole C2 is located needs to have better compression resistance and structural strength, and the compression resistance and bearing performance of the fluid distribution area of the second corner hole C2 of the plate heat exchanger in the application process are improved. For this, the present embodiment is designed as follows:

referring to fig. 5 and 7, the second plate corrugation 20 includes a second corrugation 20a adjacent to the second corner hole C2, the second corrugation 20a has at least partially a third corrugation segment 20a1, a second middle corrugation segment 20a2 and a fourth corrugation segment 20a3, the second middle corrugation segment 20a2 connects the third corrugation segment 20a1 and the fourth corrugation segment 20a3, the third corrugation segment 20a1 extends obliquely toward the second long side 3b, the fourth corrugation segment 20a3 extends obliquely toward the first long side 3a, the third corrugation segment 20a1 and the fourth corrugation segment 20a3 form a second included angle β2, the second middle corrugation segment 20a2 has a second corrugation angle α2, and the angle of the second included angle β2 is smaller than the angle of the second corrugation angle α2. Specifically, the opening angle of the second included angle β2 is toward the second short side 4b; the opening angle of the second ripple angle α2 is directed towards the second short side 4b. In this embodiment, the second middle corrugated section 20a2 is a herringbone wave, two ends of the second middle corrugated section 20a2 extend obliquely to corresponding long sides through the third corrugated section 20a1 and the fourth corrugated section 20a3 respectively, and the angle of a second included angle beta 2 formed by the third corrugated section 20a1 and the fourth corrugated section 20a3 is smaller than the angle of the second corrugated angle alpha 2, in other words, one end of the second corrugated section 20a close to the long sides is in a bending structure to form a bending angle, so that compared with the common conventional corrugated in the related art, the design has the advantages that the extending length of the corrugated is prolonged, more welding points can be added after the abutting joint of the second corrugated section and the adjacent first plate sheet 1, the welding area of the adjacent plate in a fluid distribution area where the second angular hole C2 is located is further increased, the structural strength of the plate heat exchanger near the second angular hole C2 is naturally improved, the compression resistance performance of the plate heat exchanger at the position of the second angular hole C2 is further improved, and the probability of occurrence of cracking, fluid leakage and the like when the plate heat exchanger is pressed and the plate sheet is split at the distribution position where the second angular hole C2 is located in the application process is reduced; moreover, the corrugation of the fluid distribution area where the second angular hole C2 is located adopts a bending design, additional corrugation is not required to be added, and simultaneously the corrugation is prolonged, so that the fluid distribution of the heat exchange medium flowing into the second angular hole C2 can be better carried out by utilizing the extension of the corrugation, and the distribution performance and the heat exchange performance of the fluid at the second angular hole C2 of the plate heat exchanger can be improved. In some embodiments, the angle of the second corrugation angle α2 is 90 ° or greater; the angle of the second included angle beta 2 is more than or equal to 60 degrees and is smaller than the angle of the second ripple angle alpha 2, namely, the angle beta 2 is more than or equal to 60 degrees and less than alpha 2.

In addition, the angle of the first ripple angle alpha 1 is less than or equal to 130 degrees, and the angle of the second ripple angle alpha 2 is less than or equal to 130 degrees, so that the pressure drop is not excessive, and the heat exchange performance is ensured.

In the above embodiment, after the first plate 1 and the second plate 2 are stacked, the first plate corrugation 10 and the second plate corrugation 20 form a network distribution, as shown in fig. 8, and the network distribution corrugation makes the fluid generate turbulence at a smaller flow velocity, so that a higher surface heat transfer coefficient can be obtained, and the heat exchange effect of the plate heat exchanger is improved. The angular orientation of the first plate corrugation 10 is set opposite to the angular orientation of the second plate corrugation 20, and the angular orientation of the second corrugation angle α2 is opposite to the angular orientation of the first corrugation angle α1. Referring again to fig. 4, the first plate corrugation 10 further comprises a third corrugation 10b, the third corrugation 10b and the first corrugation 10a being arranged adjacent to each other in the length direction of the plate heat exchanger, the third corrugation 10b having a third corrugation angle α3, the opening angle of the third corrugation angle α3 being oriented in the same direction as the opening angle of the first corrugation angle α1. Referring again to fig. 5, the second plate corrugation 20 comprises a fourth corrugation 20b, the fourth corrugation 20b and the second corrugation 20a being arranged adjacently along the length of the plate heat exchanger, the fourth corrugation 20b having a fourth corrugation angle α4, the opening angle of the fourth corrugation angle α4 being oriented in the same direction as the opening angle of the second corrugation angle α2.

In the above embodiment, after the first corrugation 10a is designed by bending, a gap is formed between the bent section of the first corrugation 10a and the adjacent third corrugation 10b, and the structural strength of the portion is reduced due to the excessive gap, for this reason, referring to fig. 9, the first sheet corrugation 10 further includes at least one first protrusion 10c, the first protrusion 10c is formed between the third corrugation 10b and at least one of the adjacent first corrugation section 10a1 and the adjacent second corrugation section 10a3, only the first protrusion 10c is formed between the third corrugation 10b and the adjacent first corrugation section 10a1, and the first protrusion 10c is formed between the third corrugation 10b and the adjacent second corrugation section 10a3 is not shown in fig. 9. By adding the first protrusions 10c, the problem that the structural strength of the bending section of the first corrugation 10a and the adjacent position of the third corrugation 10b is low due to overlarge gaps is avoided. Similarly, after the second corrugation 20a is bent, a gap is formed between the second corrugation 20a and the adjacent fourth corrugation 20b, and the structural strength of the portion is also reduced due to the excessive gap, for this reason, referring to fig. 7 again, the second plate corrugation 20 further includes at least one second protrusion 20c, and the fourth corrugation 20b has the second protrusion 20c between the adjacent third corrugation segment 20a1 and at least one of the adjacent fourth corrugation segments 20a 3. Only the case where the second protrusion 20c is provided between the third corrugated segment 20a1 and the adjacent fourth corrugated segment 20b is shown in fig. 7, and the case where the second protrusion 20c is provided between the fourth corrugated segment 20a3 and the adjacent fourth corrugated segment 20b is not shown. By adding the second protrusions 20c, the problem of low structural strength of the second corrugation 20a at the position where the bending section of the second corrugation 20a is adjacent to the fourth corrugation 20b due to the overlarge gap is avoided.

In order to further enhance the pressure resistance and the structural strength of the plate heat exchanger in the inlet area, the present embodiment also has the following design: referring to fig. 13, the third corrugation 10b includes a first primary heat exchange corrugation 10b1 adjacent to the first corrugation 10a and a first secondary heat exchange corrugation 10b2 adjacent to the second short side 4b, and a corrugation interface width (w 1 shown in fig. 13) of at least one of the first corrugation 10a and the first secondary heat exchange corrugation 10b2 is larger than an interface width (w 2 shown in fig. 13) of the first primary heat exchange corrugation 10b 1. Likewise, the fourth corrugation 20b includes a second primary heat exchange corrugation 20b1 adjacent to the second corrugation 20a and a second width heat exchange corrugation 20b2 adjacent to the first short side 4a, and a corrugation interface width (w 3 as shown in fig. 13) of at least one of the second corrugation 20a and the second width heat exchange corrugation 20b2 is greater than an interface width (w 4 as shown in fig. 13) of the second primary heat exchange corrugation 20b 1. The welding area of the corrugation is increased by increasing the width of the corrugated joint surface of the distribution area where the first corner hole C1 and the second corner hole C2 are located, so that the welding strength and the pressure resistance are improved.

Referring again to fig. 1, 3-5, the first and second plates 1, 2 each have third and fourth angular holes C3, C4, the first and third angular holes C1, C3 each communicate with the first inter-plate channel 5, and the second and fourth angular holes C2, C4 each communicate with the second inter-plate channel 6. The third angular holes C3 are used for the outflow of the refrigerant from the first inter-plate channels 5, and the fourth angular holes C4 are used for the outflow of the heat exchange medium from the second inter-plate channels 6. In some embodiments, the first corner hole C1 and the third corner hole C3 are diagonally distributed, and the second corner hole C2 and the fourth corner hole C4 are diagonally distributed as well, so that the refrigerant and the heat exchange medium cross each other in the application process of the plate heat exchanger; in other embodiments, the first corner hole C1 and the third corner hole C3 are distributed along one long side 3, the second corner hole C2 and the fourth corner hole C4 are distributed along the other long side 3, which are not shown in the figures, and at this time, the plate heat exchanger has a parallel flow of refrigerant and heat exchange medium during application. In this embodiment, the first sheet 1 and the second sheet 2 each comprise a rounded edge 7, and adjacent long edges 3 and short edges 4 are connected by means of the rounded edges 7.

The plate heat exchanger provided by the application can be used as an evaporator or a condenser. When the heat exchanger is used as a hair expander, as the temperature of the refrigerant inlet side (namely the first corner hole C1) is lower, the heat exchange medium exchanging heat with the refrigerant flows to the position corresponding to the refrigerant inlet, the risk of freezing is high, and the volume expansion is easy to cause once the freezing occurs, so that the heat exchange plate at the freezing position is subjected to the problems of stress cracking, tearing, breakage and the like, and the refrigerant is bypassed to one side of the heat exchange medium, so that the plate heat exchanger is invalid. In order to reduce or prevent the freezing phenomenon of the heat exchange medium at the position, the embodiment is designed as follows: referring to fig. 10, the plate heat exchanger has a first connection portion 100, a first corner hole C1 is located in the first connection portion 100, the first connection portion 100 includes a first flat connection portion 100a and a second flat connection portion 100b, the first flat connection portion 100a is located at a peripheral side of the first corner hole C1 of the first plate 1, the second flat connection portion 100b is located at a peripheral side of the first corner hole C1 of the second plate 2, that is, the first corner hole C1 is located in the first connection portion 100, and the first corner hole C1 penetrates through the first connection portion 100 along a thickness direction of the plate heat exchanger. In addition, the back surface of the first flat connection portion 100a is connected with the front surface of the adjacent second flat connection portion 100b, the first connection portion 100 is connected with the round corner edge 7 on the periphery side of the first corner hole C1, namely, at least one of the first flat connection portion 100a and the second flat connection portion 100b protrudes towards the second plate-to-plate channel 6, so that the first corner hole C1 and the second plate-to-plate channel 6 are separated, the space between the low-temperature refrigerant flowing in from the first corner hole C1 and the heat exchange medium in the second plate-to-plate channel 6 in the application process of the plate heat exchanger is ensured, the situation that the heat exchange medium in the second plate-to-plate channel 6 is frozen due to the low-temperature influence of the refrigerant at the first corner hole C1 is avoided, the risk of freezing is effectively reduced, the durability of the plate heat exchanger is improved, and the performance of the plate heat exchanger is improved. Further, referring to fig. 11, defining an edge 8 at a position where the first butt joint portion 100a and the second butt joint portion 100b are connected and adjacent to the second inter-plate channel 6, wherein a minimum distance between the edge 8 and the first corner hole C1 is equal to or greater than 3mm; for example 3mm, 3.5mm, 4mm, 5mm etc. while guaranteeing the connection strength there, by defining the minimum distance between the edge 8 and the edge of the first porthole C1, the heat exchange medium in the second plate interspaces 6 is guaranteed to have a distance from the first porthole C1, reducing the risk of freezing, improving the effectiveness of anti-freezing, while also guaranteeing the connection strength of adjacent plates at the first porthole C1, improving the durability of the plate heat exchanger.

Still further, referring to fig. 11 again, two ends of the edge 8 are respectively connected to the first long side 3a and the first short side 4a on the peripheral side of the first corner hole C1, the point where the edge 8 is connected to the first long side 3a is defined as O1, the point where the edge 8 is connected to the first short side 4a is defined as O2, and the minimum distance from the point on the line from O1 to O2 to the first short side 4a decreases, i.e. the problem that the second inter-plate channel 6 has a stagnation area in the area close to the first corner hole C1 is avoided, so that when the heat exchange medium in the second inter-plate channel 6 flows to the edge 8, the heat exchange medium can smoothly flow, the stagnation time of the heat exchange medium is reduced, and the risk that the heat exchange medium is frozen due to the low temperature influence of the refrigerant flowing into the first corner hole C1 is reduced.

In the following embodiments, the first corner hole C1 and the fourth corner hole C4 are each distributed along the first short side 4a, and the first corner hole C1 and the second corner hole C2 are each diagonally distributed as an example.

Because the fourth corner hole C4 is closer to the first corner hole C1, and the first corner hole C1 is used as a refrigerant inlet, the temperature near the first corner hole C1 is lower, if the heat exchange medium stays at the part for a long time, the risk of freezing is also caused, and the corner of the second plate-to-plate channel 6 at the periphery of the fourth corner hole C4 is very easy to cause slow flowing and even stay due to smaller flowing space, so that the occurrence of freezing is caused, and the problems of plate desoldering, cracking and the like of the heat exchange medium of the adjacent plates at the part are caused due to freezing expansion, so that the plate heat exchanger is invalid. For this, the present embodiment is designed as follows: referring again to fig. 10, the plate heat exchanger has a second connection portion 200, the second connection portion 200 being located between the fourth corner hole C4 and the rounded corner edge 7 on the peripheral side of the fourth corner hole C4; the second connecting portion 200 includes a third butt joint portion 200a and a fourth butt joint portion 200b, the third butt joint portion 200a is located on the fourth corner hole C4 peripheral side of the first sheet 1, the fourth butt joint portion 200b is located on the fourth corner hole C4 peripheral side of the second sheet 2, the back surface of the third butt joint portion 200a is connected with the front surface of the adjacent fourth butt joint portion 200b, and the second connecting portion 200 is connected with the rounded corner edge 7 on the fourth corner hole C4 peripheral side. In other words, the second inter-plate channels 6 are closed at the corners of the peripheral sides of the fourth corner holes C4 by the second connection parts 200, so that the heat exchange medium in the second inter-plate channels 6 cannot enter the corners of the peripheral sides of the fourth corner holes C4, the risk of freezing caused by stagnation of the heat exchange medium at the corners and the influence of low-temperature environment is reduced, and the reliability and durability of the plate heat exchanger are further improved.

Further, if the second angular hole C2 is used as an inlet of the heat exchange medium, if the second inter-plate channel 6 has a flow channel at a corner of the peripheral side of the second angular hole C2, after the heat exchange medium enters from the second angular hole C2, the heat exchange medium can enter the flow channel at first because the flow channel is located at a corner of the peripheral side of the second angular hole C2, the distance is short, the flow resistance is small, then the flow of the heat exchange medium near the second long side 3b is large, the flow near the first long side 3a is small, so that the uneven fluid distribution is caused, and further the heat exchange medium cannot fully utilize the heat exchange surface of the plate, and the heat exchange effect is affected. Therefore, in order to improve the distribution uniformity of the heat exchange medium, the present embodiment is designed as follows: referring again to fig. 10, the plate heat exchanger has a third connection portion 300, the third connection portion 300 being located between the second corner hole C2 and the rounded corner edge 7 on the peripheral side of the second corner hole C2; the third connecting portion 300 includes a fifth butt joint portion 300a and a sixth butt joint portion 300b, the fifth butt joint portion 300a is located on the second corner hole C2 peripheral side of the first sheet 1, the sixth butt joint portion 300b is located on the second corner hole C2 peripheral side of the second sheet 2, the back surface of the fifth butt joint portion 300a is connected with the front surface of the adjacent sixth butt joint portion 300b, and the third connecting portion 300 is connected with the rounded corner edge 7 on the fourth corner hole C4 peripheral side. In other words, the corners of the second plate-to-plate channels 6 at the peripheral sides of the second corner holes C2 are sealed by the third connecting portions 300, so that the heat exchange medium in the second plate-to-plate channels 6 cannot enter the corners of the peripheral sides of the second corner holes C2, after the heat exchange medium enters from the second corner holes C2, the heat exchange medium can be more distributed towards the first long sides 3a far away from the second corner holes C2 due to the sealing of the corners of the peripheral sides of the second corner holes C2, so that the heat exchange medium can be distributed more smoothly and uniformly, flows more uniformly in the main heat exchange area, heat exchange can be performed by fully utilizing the heat exchange surfaces of the plates and the refrigerant in the channels between the adjacent side plates, the heat exchange effect is improved, and the heat exchange performance of the plate heat exchanger is enhanced. In addition, because the second corner hole C2 is used as an inlet of a heat exchange medium and needs to bear certain pressure, the connection strength of the plate at the position of the second corner hole C2 can be effectively improved through the closed design of the corners at the periphery of the second corner hole C2, and the compression resistance of the position is improved.

Further, the third corner hole C3 and the first corner hole C1 are distributed along the first long side 3a, so that the third corner hole C3 is relatively far away from the first corner hole C1, the heat exchange medium at the position corresponding to the third corner hole C3 in the second plate-to-plate channel 6 is less affected by the low temperature of the refrigerant placed in the phase of the first corner hole C1, the risk of freezing is low, and in order to increase the flow area of the heat exchange medium, improve the distribution uniformity and enhance the heat exchange effect, the embodiment is designed as follows: referring to fig. 12, the plate heat exchanger has a fourth connection portion 400, the fourth connection portion 400 being located between the third corner hole C3 and the rounded corner edge 7 on the peripheral side of the third corner hole C3; the fourth connecting portion 400 includes a seventh butt joint portion 400a and an eighth butt joint portion 400b, the seventh butt joint portion 400a is located on the third corner hole C3 peripheral side of the first sheet 1, the eighth butt joint portion 400b is located on the third corner hole C3 peripheral side of the second sheet 2, the back surface of the seventh butt joint portion 400a is disposed at an interval from the front surface of the eighth butt joint portion 400b, the front surface of the seventh butt joint portion 400a is in contact with the back surface of the eighth butt joint portion 400b, and the fourth connecting portion 400 is in contact with the rounded corner edge 7 on the third corner hole C3 peripheral side. In other words, the first inter-plate channels 5 are closed at the corners of the circumferential side of the third corner hole C3, and the second inter-plate channels 6 open the channels at the corners of the circumferential side of the third corner hole C3, so that when the heat exchange medium flows to the circumferential side of the third corner hole C3, a part of the heat exchange medium can flow to the first long side 3a close to the first corner hole C1 through the channels at the corners of the circumferential side of the third corner hole C3, so that the distribution uniformity of the heat exchange medium can be further enhanced, the flow area of the heat exchange medium is increased, and the heat exchange efficiency is improved.

In the above embodiment, the first butt joint portion 100a, the third butt joint portion 200a, the fifth butt joint portion 300a, and the seventh butt joint portion 400a are all part of the first sheet 1, that is, the first butt joint portion 100a, the third butt joint portion 200a, the fifth butt joint portion 300a, and the seventh butt joint portion 400a are press-formed during the processing of the first sheet 1. Similarly, the second butt portion 100b, the fourth butt portion 200b, the sixth butt portion 300b, and the eighth butt portion 400b are all part of the second sheet 2, that is, the second butt portion 100b, the fourth butt portion 200b, the sixth butt portion 300b, and the eighth butt portion 400b are press-formed during the processing of the second sheet 2. At least one of the first and

second butt portions

100a and 100b protrudes toward the second inter-plate channel 6, at least one of the third and

fourth butt portions

200a and 200b protrudes toward the second inter-plate channel 6, at least one of the fifth and sixth butt portions 300a and 300b protrudes toward the second inter-plate channel 6, and at least one of the seventh and

eighth butt portions

400a and 400b protrudes toward the first inter-plate channel 5.

In the above embodiment, the plane perpendicular to the thickness direction of the plate heat exchanger is defined as the projection plane, and the projection area of the first connection portion 100 on the projection plane is larger than the projection area of any one of the second connection portion 200, the third connection portion 300, and the fourth connection portion 400 on the projection plane. In other words, the area of the first connection part 100 at the position of the first corner hole C1 is larger than the areas of the connection parts at the positions of the other corner holes, so that the interval between the second plate-to-plate channels 6 and the first corner hole C1 is ensured, the anti-freezing effect of the plate heat exchanger is achieved, the actual service performance of the plate heat exchanger is improved, and the service life of the plate heat exchanger is prolonged.

In order to achieve better heat exchange performance and reduce pressure drop of the structure, one of the first plate corrugation and the second plate corrugation is asymmetric corrugation, namely, the wave crest of one of the first plate corrugation and the second plate corrugation is high or low, a single-side asymmetric channel structure (namely, two plate channels with different volumes) is formed, and the pressure drop of the structure can be effectively reduced under the condition that the heat exchange performance is not influenced.

Some of the technical implementations in the above embodiments may be combined or replaced.

The technical principles of the present application have been described above in connection with specific embodiments, but it should be noted that the above descriptions are merely for explaining the principles of the present application and should not be construed as limiting the scope of the present application in any way. Other embodiments of the present application, or equivalents thereof, will suggest themselves to those skilled in the art without undue burden from the present application based on the explanations herein.

Claims

1. A plate heat exchanger, characterized in that: the heat exchanger comprises a plurality of first plates and a plurality of second plates, wherein the first plates and the second plates are alternately overlapped along the thickness direction of the plate heat exchanger; the first plate and the second plate each comprise two long sides, the long sides extend along the length direction of the plate heat exchanger, one of the two long sides is a first long side, the other long side is a second long side, the first plate and the second plate are provided with first corner holes, and compared with the second long sides, the first corner holes are closer to the first long sides;

2. A plate heat exchanger according to claim 1, wherein: the first long edge and the second long edge are oppositely arranged along the width direction of the plate heat exchanger;

the first plate and the second plate comprise two short sides, the short sides extend along the width direction of the plate heat exchanger, one of the two short sides is a first short side, and the other short side is a second short side; the first short side and the second short side are oppositely arranged along the length direction of the plate heat exchanger; the length of the long side is longer than that of the short side;

the first angular aperture is disposed closer to the first short side than the second short side;

the angle of the first included angle is more than or equal to 60 degrees, and the opening angle of the first included angle faces the first short side;

the angle of the first ripple angle is more than or equal to 90 degrees and less than or equal to 130 degrees; the opening angle of the first ripple angle is toward the first short side.

3. A plate heat exchanger according to claim 2, wherein: the first and second plates each have a second angular aperture disposed closer to the second short side than the first short side;

the second plate has second plate corrugations including second corrugations adjacent to the second angular holes, the second corrugations having at least partially third, second intermediate and fourth corrugation segments, the second intermediate corrugation segments connecting the third and fourth corrugation segments, the third corrugation segment extending obliquely toward the second long side, the fourth corrugation segment extending obliquely toward the first long side, the third and fourth corrugation segments forming a second included angle, the second intermediate corrugation segments having a second corrugation angle, the second included angle being smaller than the second corrugation angle;

the angle of the second included angle is more than or equal to 60 degrees, and the opening angle of the second included angle faces the second short side;

the angle of the second ripple angle is more than or equal to 90 degrees and less than or equal to 130 degrees; the opening angle of the second ripple angle is towards the second short side;

the angular orientation of the second corrugation angle is opposite to the angular orientation of the first corrugation angle.

4. A plate heat exchanger according to claim 3, wherein: the first plate corrugation comprises third corrugation, the third corrugation and the first corrugation are adjacently arranged along the length direction of the plate heat exchanger, the third corrugation has a third corrugation angle, and the opening angle of the third corrugation angle is the same as the opening angle of the first corrugation angle;

the first plate corrugation further comprises at least one first protrusion, the third corrugation having the first protrusion between at least one of an adjacent first corrugation segment, an adjacent second corrugation segment.

5. A plate heat exchanger according to claim 3, wherein: the second plate corrugation comprises a fourth corrugation, the fourth corrugation and the second corrugation are adjacently arranged along the length direction of the plate heat exchanger, the fourth corrugation has a fourth corrugation angle, and the opening angle orientation of the fourth corrugation angle is the same as the opening angle orientation of the second corrugation angle;

the second plate corrugation further comprises at least one second bulge, and the fourth corrugation has the second bulge between the fourth corrugation and at least one of the adjacent third corrugation segment and the adjacent fourth corrugation segment.

6. A plate heat exchanger according to claim 3, wherein: the first and second plates each have third and fourth corner holes,

the plate heat exchanger is provided with a plurality of first plate-to-plate channels and a plurality of second plate-to-plate channels, the plurality of first plate-to-plate channels and the plurality of second plate-to-plate channels are alternately arranged along the thickness direction of the plate heat exchanger, the first plate-to-plate channels and the second plate-to-plate channels are not communicated with each other, the first angle holes and the third angle holes are communicated with the first plate-to-plate channels, and the second angle holes and the fourth angle holes are communicated with the second plate-to-plate channels;

the first inter-plate channel is located between the front face of a first plate and the back face of an adjacent second plate, and the second inter-plate channel is located between the back face of the first plate and the front face of an adjacent second plate;

the first angle holes and the third angle holes are distributed diagonally, or the first angle holes and the third angle holes are distributed along one long side;

the first plate and the second plate both comprise round corner edges, and adjacent long edges and short edges are connected through the round corner edges.

7. A plate heat exchanger according to claim 6, wherein: the plate heat exchanger is provided with a first connecting part, the first corner hole is positioned in the first connecting part, the first connecting part comprises a first flat connecting part and a second flat connecting part, the first flat connecting part is positioned at the periphery side of a first corner hole of a first plate, the second flat connecting part is positioned at the periphery side of the first corner hole of a second plate, the back surface of the first flat connecting part is connected with the front surface of an adjacent second flat connecting part, the first connecting part is connected with the round corner edge of the periphery side of the first corner hole, the edge is defined at the joint of the first flat connecting part and the second flat connecting part, and the side adjacent to a channel between the second plates, and the minimum distance between the edge and the first corner hole is more than or equal to 3mm;

the two ends of the edge are respectively connected with a first long side and a first short side of the periphery of the first angle hole, the point where the edge is connected with the first long side is defined as O1, the point where the edge is connected with the first short side is O2, and the minimum distance from the point on the line from O1 to O2 to the first short side is reduced.

8. A plate heat exchanger according to claim 6, wherein: the plate heat exchanger is provided with a second connecting part, and the second connecting part is positioned between the fourth corner hole and the round corner edge on the periphery side of the fourth corner hole; the second connecting part comprises a third butt joint part and a fourth butt joint part, the third butt joint part is positioned at the periphery side of a fourth corner hole of the first plate, the fourth butt joint part is positioned at the periphery side of the fourth corner hole of the second plate, the back surface of the third butt joint part is connected with the front surface of the adjacent fourth butt joint part, and the second connecting part is connected with the round corner edge at the periphery side of the fourth corner hole;

the plate heat exchanger is provided with a third connecting part, and the third connecting part is positioned between the second corner hole and the round corner edge on the periphery side of the second corner hole; the third connecting portion comprises a fifth butt joint portion and a sixth butt joint portion, the fifth butt joint portion is located on the second corner hole periphery side of the first plate, the sixth butt joint portion is located on the second corner hole periphery side of the second plate, the back face of the fifth butt joint portion is connected with the front face of the adjacent sixth butt joint portion, and the third connecting portion is connected with the round corner edge of the fourth corner hole periphery side.

9. A plate heat exchanger according to claim 6, wherein: the plate heat exchanger is provided with a fourth connecting part, and the fourth connecting part is positioned between the third corner hole and the round corner edge on the periphery side of the third corner hole; the fourth connecting portion comprises a seventh butt joint portion and an eighth butt joint portion, the seventh butt joint portion is located on the periphery of the third corner hole of the first plate, the eighth butt joint portion is located on the periphery of the third corner hole of the second plate, the back face of the seventh butt joint portion is arranged at intervals with the front face of the eighth butt joint portion, the front face of the seventh butt joint portion is connected with the back face of the eighth butt joint portion, and the fourth connecting portion is connected with the round corner edge of the periphery of the third corner hole.

10. A plate heat exchanger according to claim 7, wherein: the third corrugation comprises a first main heat exchange corrugation close to the first corrugation and a first auxiliary heat exchange corrugation close to the second short side, and the width of a corrugated joint surface of at least one of the first corrugation and the first auxiliary heat exchange corrugation is larger than that of the first main heat exchange corrugation;

the fourth corrugation comprises a second main heat exchange corrugation close to the second corrugation and a second heat exchange corrugation close to the first short side, and the width of a corrugated joint surface of at least one of the second corrugation and the second heat exchange corrugation is larger than that of the second main heat exchange corrugation.