CN116659275A

CN116659275A - Plate heat exchanger

Info

Publication number: CN116659275A
Application number: CN202210147713.5A
Authority: CN
Inventors: 请求不公布姓名
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2022-02-17
Filing date: 2022-02-17
Publication date: 2023-08-29

Abstract

The application provides a plate heat exchanger, which comprises a first plate and a second plate which are adjacent; the plate heat exchanger is also provided with a first pore canal; the first plate comprises a first circumferential wall and the second plate comprises a second circumferential wall; the plate heat exchanger also has first inter-plate channels; the plate heat exchanger is also provided with a distribution channel and a groove wall part; the first circumferential wall comprises a first matching wall and a first groove wall, the first groove wall is recessed from the first matching wall, and the maximum distance between the first matching wall and the plate structure farthest from the first plate and far away from the second plate is smaller than the maximum distance between the two plates; the second circumferential wall comprises a second matching wall and a second groove wall, and the second groove wall is connected with the second matching wall and is flush with the second matching wall; the first groove wall and the second groove wall are part of the groove wall part, and at least part of the first matching wall and the second matching wall are in sealing connection; the distribution channel communicates with the first porthole and the first inter-plate channel. The application is beneficial to improving the reliability of the plate heat exchanger.

Description

Plate heat exchanger

Background

Plate heat exchangers generally comprise a plurality of plates stacked together with adjacent plates defining inter-plate channels therebetween for fluid flow, and refrigerant and coolant may flow on opposite sides of the plates, respectively, to effect heat exchange between the plates. With the continuous improvement of the requirements of the service performance of the plate heat exchanger, a distribution channel can be added on one side of the plate close to the fluid inlet so as to improve the distribution performance of the fluid, thereby improving the heat exchange effect of the plate heat exchanger. The distribution channels will also have a certain influence on the overall strength of the plate and the plate heat exchanger.

In some plate heat exchangers in the prior art, a small recess is formed at a local position near each of two adjacent plate angle holes, and then two recess structures are correspondingly spliced to form a distribution channel, so that the two plates are recessed by a small position, and accordingly, the loss of strength of the plate heat exchanger can be reduced. However, the distribution channel is spliced by depending on the concave structures of the two plates, so that the distribution structure has higher requirements on the processing precision of the processing dies corresponding to the two plates and the heat exchanger in the assembling process, and in practice, the problems such as dislocation of the concave structures and the like easily occur, so that the distribution channel is easily changed into two channel structures with smaller flow cross sections, and the risk of blocking the distribution channel caused by welding flux or refrigerant with higher viscosity further influences the reliability of the plate heat exchanger.

Disclosure of Invention

The application is beneficial to reducing the blocking risk of the distribution channel, thereby improving the reliability of the plate heat exchanger.

The application provides a plate heat exchanger, which comprises a plurality of plates, wherein the plates are arranged in a stacked manner and comprise a first plate and a second plate which are adjacent; the plate heat exchanger is also provided with a first pore canal penetrating through the two plates along the stacking direction of the plates; the first plate comprises a first annular wall, the second plate comprises a second annular wall, and the two annular walls are positioned at the periphery of the first pore canal;

the plate also has a main heat transfer area, and the main heat transfer area of the first plate is positioned at one side of the first annular wall away from the first portholes; the main heat exchange area of the second plate is positioned at one side of the second annular wall away from the first pore canal; the plate heat exchanger further has first inter-plate channels, at least part of which is located between the main heat exchange area of the first plate and the main heat exchange area of the second plate;

the plate heat exchanger is also provided with a distribution channel, and a groove wall part forming the distribution channel; the first circumferential wall comprises a first matching wall and a first groove wall connected with the first matching wall, the first groove wall is recessed from the first matching wall to a direction away from the second plate, and in the stacking direction, a space is reserved between the first matching wall and a plate structure of the first plate farthest away from the second plate and between the first matching wall and a plate structure of the second plate farthest away from the first plate; the second circumferential wall comprises a second matched wall and a second groove wall which are connected, and the wall surface of the second groove wall facing the first groove wall is flush with the wall surface of the second matched wall facing the first matched wall;

the first groove wall and the second groove wall are part of the groove wall part, and the first matching wall and the second matching wall are at least partially connected in a sealing way; the distribution channel communicates with the first porthole and the first inter-plate channel.

In the application, the first groove wall is recessed from the first matching wall, the wall surface of the second groove wall facing the first groove wall is flush with the wall surface of the second matching wall facing the first matching wall, and the first matching wall and the second matching part are at least partially connected in a sealing way, so that the flow section of the distribution channel is mainly influenced by the recessed range of the first groove wall, and the groove wall structure of each part forming the distribution channel is not easy to cause the change of the flow section of the distribution channel due to dislocation, and the distribution channel is not easy to be blocked, thereby being beneficial to improving the reliability of the plate heat exchanger.

Drawings

Fig. 1 is a schematic view of a plate heat exchanger according to an embodiment of the application;

FIG. 2 is a schematic view of an exploded construction of the plate heat exchanger of FIG. 1;

FIG. 3 is a schematic view of a cut-away configuration of the plate heat exchanger of FIG. 1;

FIG. 4 is a schematic view of an exploded view of a portion of a panel according to one embodiment of the present application;

FIG. 5 is a schematic view of a first plate in an embodiment of the application;

FIG. 6 is a schematic view of a second plate in an embodiment of the application;

FIG. 7 is an enlarged schematic view of the first plate portion shown in FIG. 5 in accordance with the present application;

FIG. 8 is a schematic view of an assembled structure of two plates at a distribution channel according to an embodiment of the present application;

FIG. 9 is a schematic view of a cut-away configuration of an assembled plate at an angular aperture in one embodiment of the application;

FIG. 10 is a schematic view of another angular cut-away configuration of the assembled plate shown in FIG. 9 in accordance with the present application;

FIG. 11 is a schematic view of a cross-sectional structure of an assembled plate at an angular hole in accordance with another embodiment of the present application;

fig. 12 is a schematic view showing an assembled structure of two plates in fig. 11 at a distribution channel according to the present application.

Detailed Description

The present application will be further described in detail below with reference to the drawings and specific examples for better understanding of the technical solutions of the present application to those skilled in the art.

Referring to fig. 1 to 12, the present application provides a plate heat exchanger 100 including a plurality of extension tubes 10, a first side plate 20, a heat exchange core 30 composed of a plurality of plates, and a second side plate 40. The first side plate 20 and the second side plate 40 are respectively disposed at different sides in the thickness direction of the heat exchange core 30, and a plurality of plates corresponding to the heat exchange core 30 are fixed together in a stacked manner.

Referring to fig. 1, the plate heat exchanger 100 has a length direction L, a width direction W, and a height direction H, and a stacking direction P of a plurality of plates is co-directional with the height direction H of the plate heat exchanger 100. Two sides of each plate typically flow different types of heat exchange media, one of which is a refrigerant and the other of which is a coolant. The plate heat exchanger 100 has portholes, which generally extend in the stacking direction P of the plates, and plate-to-plate channels, which generally lie between two adjacent plates, formed by the gaps between the plates. In the plate heat exchanger 100, both the portholes and the inter-plate channels are part of the refrigerant flow channels 50 or the coolant flow channels 60. The refrigerant flow channels 50 and the coolant flow channels 60 are not in communication so that the two heat exchange media can perform a dividing wall heat exchange through the spaced apart plate structures.

In embodiments of the present application, the plurality of plates of the heat exchange core 30 includes at least one set of adjacent first plates 11 and second plates 12, and in some embodiments, the number of first plates 11 and second plates 12 may be multiple. In fig. 4, the side of the plate facing the outside, i.e. the side that can be seen, is defined as the first heat exchange surface 1 and the side facing the inside, i.e. the side that cannot be seen, is defined as the second heat exchange surface 2. Each plate has a main heat exchange area 70 and a number of corner holes located at the periphery of the main heat exchange area 70. The corner holes of the plurality of plates are arranged in a stacking direction of the plates to form at least a part of the plurality of cells.

For a plurality of plates, the plates can be formed by a single auxiliary die, namely, each plate is a plate with identical shape and structure, when the plates are assembled, the other plate adjacent to one plate can be assembled after rotating 180 degrees, of course, the plates can also be formed by two or more pairs of auxiliary dies, namely, the plates can be formed by different shapes or structures, for example, the main heat exchange area 70 of one plate is in a flat plate structure, the main heat exchange area 70 of the other Zhang Banpian is provided with a point wave type bulge structure, and the two plates can also be assembled together and alternately stacked, as long as the plates meet the corresponding relationship of the plate structure and the plate assembly described by the application. In some embodiments, fin plates can be added between adjacent plates to increase the fluid heat exchange area and improve the heat exchange performance.

The heat exchange core 30 is formed by stacking a plurality of plates along the P direction in fig. 4, the first heat exchange surface 1 of the first plate 11 is opposite to the second heat exchange surface 2 of the second plate 12, and when the number of the first plate 11 and the second plate 12 is multiple, the second heat exchange surface 2 of the first plate 11 may be opposite to the first heat exchange surface 1 of the other second plate 12. Each plate further comprises a flange 71. When the plates are assembled, the flanges 71 of the plates can be sealed by welding, e.g. brazing, to facilitate retention of the fluid in the flow channels formed between the plates. Each plate is typically provided with a number of angular holes, the angular holes of corresponding locations of the plates being arranged coaxially or eccentrically in the height direction H of the plate heat exchanger 100 to form at least part of the portholes. In the embodiment of the application, each plate is represented by four corner holes, and the four corner holes are distributed at four corner positions of the plate. The first plate 11 is provided with first, third, fifth and sixth corner holes 41, 43, 45, 46 and the second plate 12 is provided with second, fourth, seventh and eighth corner holes 42, 44, 47, 48.

For the first plate 11, the first corner hole 41 may serve as a fluid inlet for the refrigerant to enter and exit the first heat exchange surface 1 of the first plate 11, and the fifth corner hole 45 may serve as a fluid outlet for the refrigerant to enter and exit the first heat exchange surface 1 of the first plate 11. The third corner holes 43 serve as fluid inlets for coolant to and from the second heat exchange surface 2 of the first plate 11 and the sixth corner holes 46 serve as fluid outlets for coolant to and from the second heat exchange surface 2 of the first plate 11. Correspondingly, for the second plate 12, the second corner holes 42 and the seventh corner holes 47 may serve as fluid inlets and outlets for the refrigerant to enter and exit the second heat exchange surface 2 of the second plate 12, and the fourth corner holes 44 and the eighth corner holes 48 may serve as fluid inlets and outlets for the coolant to enter and exit the first heat exchange surface 1 of the second plate 12, respectively. In the first plate 11, the first corner hole 41 and the fifth corner hole 45 are arranged along the long side of the first plate 11. Accordingly, the second and seventh corner holes 42, 47 of the second plate 12 are arranged along the length of the second plate 12, which may be referred to as a unilateral flow arrangement. Of course, in other embodiments, the first corner hole 41 and the fifth corner hole 45 of the first plate 11, and the second corner hole 42 and the seventh corner hole 47 of the second plate 12 may all be diagonally arranged, and this arrangement of corner holes may be referred to as diagonal flow.

Referring to fig. 2, 3 and 4, the plate heat exchanger 100 has first portholes 21 extending in the plate stacking direction P, the first corner holes 41 and the second corner holes 42 being part of the first portholes 21. The first plate 11 comprises a first circumferential wall 31 and the second plate 12 comprises a second circumferential wall 32, both circumferential walls being located at the periphery of the first porthole 21. The first and second circumferential walls 31, 32 cooperate to form a distribution channel 52. The first porthole 21 may serve as an inlet channel for the refrigerant. The main heat exchanger zone 70 of the first plate 11 is located at the side of the first circumferential wall 31 remote from the first portholes 21. The main heat transfer area 70 of the second plate 12 is located at the side of the second circumferential wall 32 remote from the first portholes 21. The plate heat exchanger 100 also has first inter-plate channels 51, at least part of the first inter-plate channels 51 being located between the second heat exchanging surface 2 of the second plate 12 and the first heat exchanging surface 1 of the first plate 11, and at least part of the first inter-plate channels 51 being located between the first plate 11 and the main heat exchanging area 70 of the second plate 12.

The refrigerant enters the first pore canal 21 through the external connection pipe 10, then correspondingly enters the first inter-plate channel 51 through the distribution channel 52, and flows out of the pore canal on the other side of the plate heat exchanger after heat exchange. The general flow path of the refrigerant is illustrated by the broken line in fig. 4, and the refrigerant flows from the first angular holes 41 of the first plate 11 into the first inter-plate channels 51 via the distribution channels 52, and flows out of the first plate 11 from the fifth angular holes 45 of the first plate 11 after heat exchange.

Referring to the illustrations of fig. 5 to 10, the first corner hole 41 and the third corner hole 43 are arranged along the width direction of the first plate 11, and the second corner hole 42 and the fourth corner hole 44 are arranged along the width direction of the second plate 12, respectively. The aperture of the first corner hole 41 is smaller than the aperture of the third corner hole 43, and the apertures of the first corner hole 41 and the second corner hole 42 are the same. The relatively small first angular holes 41 are beneficial to improving the pressure drop of the refrigerant, and further improving the distribution effect of the refrigerant and other gas-liquid two-phase fluid. The plate heat exchanger 100 further comprises a second porthole 22, and a third angle hole 43 and a fourth angle hole 44 are part of the second porthole 22. The second portholes 22 penetrate the first plate 11 in the stacking direction to form third angular holes 43 at the first plate 11, and the second portholes 22 penetrate the second plate 12 in the stacking direction to form fourth angular holes 44 at the second plate 12. The first and third corner holes 43 are arranged along the width direction of the first plate 11, and the second and fourth corner holes 44 are arranged along the width direction of the second plate 12. The plate structure on the peripheral side of the third corner hole 43 is welded and sealed to the plate structure on the peripheral side of the fourth corner hole 44, so that both the third corner hole 43 and the fourth corner hole 44 are blocked from the first inter-plate passage 51.

Further, the plate heat exchanger 100 may further comprise a third porthole 23, a fourth porthole 24. The first portholes 21 communicate with the third portholes 23 and the second portholes 22 communicate with the fourth portholes 24.

The first heat exchanging surface 1 side of the first plate 11 illustrated with reference to fig. 5 and the second heat exchanging surface 2 side of the second plate 12 illustrated with reference to fig. 6 are correspondingly structured schematic diagrams. Referring to fig. 8 to 10, for the first sheet 11, the first circumferential wall 31 includes a first mating wall 311 and a first groove wall 312 connected to the first mating wall 311, the first groove wall 312 is recessed from the first mating wall 311 in a direction away from the second sheet 12, and there is a certain distance between the first mating wall 311 and a plate structure farthest from the second sheet 12 by the first sheet 11 and between the first mating wall 311 and a plate structure farthest from the first sheet 11 by the second sheet 12 in the sheet stacking direction. The maximum spacing between the first plate 11 and the second plate 12 can be calculated in the same direction by the distance between the topmost end of one plate convex structure and the bottommost end of the other Zhang Banpian concave structure. The first circumferential wall 31 is located at the periphery of the first duct 21, and the first groove wall 312 is recessed with respect to the first circumferential wall 311, that is, the first circumferential wall 31 needs to be provided with an angular hole and a recess, so that a higher requirement is placed on the strength of the first circumferential wall 31, otherwise, the first plate 11 is easy to deform under the action of high-pressure fluid, for example, the first plate is easy to leak when being sealed with another Zhang Banpian. In order to improve the strength of the first circumferential wall 31, by reducing the height of the protrusion of the first mating wall 311, the stretching degree of the material of the first circumferential wall 31 and the position near the first circumferential wall can be reduced in the process of stamping the plate material, and the thickness of the first mating wall 311 can be increased relatively, so that the overall strength of the plate material is improved, and the overall strength and stability of the plate heat exchanger 100 are facilitated. Correspondingly, the second circumferential wall 32 includes a second mating wall 321 and a second groove wall 322, and a wall surface of the second groove wall 322 facing the first groove wall 312 is connected with a wall surface of the second mating wall 321 facing the first mating wall 311 and is flush with the first mating wall. I.e. the second groove wall 322 is a structure extending flush with the second mating wall 321. Further, the first groove wall 312 and the second groove wall 322 are part of a groove wall 520 corresponding to the distribution channel 52 formed by the plate heat exchanger, the first mating wall 311 and the second mating wall 321 are at least partially connected in a sealing manner, and the distribution channel 52 is communicated with the first porthole 21 and the first inter-plate channel 51. The groove structure of one plate is matched with the plane structure of the other Zhang Banpian when the first groove wall 312 and the second groove wall 322 are matched, the flow section of the distribution channel 52 is mainly influenced by the concave range of the first groove wall 312, and even if the processing precision and the assembly precision of the two plates are slightly poor, the first groove wall 312 and the second groove wall 322 are not easy to generate the change of the fluid section morphology of the distribution channel 52 caused by dislocation. So that the distribution channels 52 are less prone to clogging and accordingly the reliability of the plate heat exchanger is higher.

Referring to fig. 9 and 10, the first circumferential wall 31 further includes a first side wall 313 and a first connection flange 314, the first side wall 313 extending from a side of the first fitting wall 311 close to the first porthole 21 in a direction away from the second plate 12, the first connection flange 314 extending from an end of the first side wall 313 away from the first fitting wall 311 in a direction perpendicular to the stacking direction P. The second circumferential wall 32 further includes a second side wall 323 extending from a side of the second fitting wall 321 close to the first porthole 21 in a direction away from the first plate 11, and a second connecting flange 324 extending from an end of the second side wall 323 away from the second fitting wall 321 in a direction perpendicular to the stacking direction P.

The first connecting flange 314 is welded to one plate (e.g., another Zhang Dier plate) of the first plate 11 on the side remote from the second plate 12, and the second connecting flange 324 is welded to one plate (e.g., another first plate) of the second plate 12 on the side remote from the first plate 11. The first connecting flange 314 has a first connecting edge 315 connected to the first side wall 313 and a first end edge 316 distant from the first side wall 313 in a direction perpendicular to the stacking direction P, and a maximum distance between the first connecting edge 315 and the first end edge 316 is L1, and 2 mm+.l1+.10 mm. The second connecting flange 324 has a second connecting edge 325 connected to the second side wall 323 and a second end edge 326 distant from the second side wall 323 in a direction perpendicular to the stacking direction, and a maximum distance between the second connecting edge 325 and the second end edge 326 is L2, and 2mm < L2 < 10mm. Further, the maximum distance between the first coupling wall 311 and the first connection flange 314 is equal to the maximum distance between the second coupling wall and the second connection flange 324. Since the first connecting flange and the second connecting flange are welded with the corresponding plates to realize sealing, the size of the welding area is an important parameter affecting the sealing performance. Taking the first connection flange 314 as an example, if the maximum distance between the first connection edge 315 and the first end edge 316 is too small, the welding quality may be affected to cause leakage, if it is too large, the refrigerant may lose more heat exchange area, and in addition, the relatively large space may easily separate the refrigerant of the gas phase and the liquid phase to deteriorate the distribution effect and the heat exchange performance.

In some embodiments, the groove bottom of the first groove wall 312 is recessed with respect to the first mating wall 311 by a depth greater than half of the maximum spacing between the first mating wall 311 and the first connection flange 314. This has the advantage that the recess depth of the bottom of the first groove wall 312 with respect to the first mating wall 311 can effectively increase the size of the flow channel 52 in response to a refrigerant having a relatively high viscosity or a relatively high flow rate, thereby avoiding clogging of the flow channel 52. In an embodiment of the present application, the groove bottom of the first groove wall 312 is flush with the first connection flange 314. A portion of the first connection flange 314 is connected to the first groove wall 312, and another portion of the first connection flange 314 is connected to the first side wall 313. I.e. the depth of the distribution channel 52 is at this point deepest in the direction of stacking of the plates. Of course, in other embodiments, the groove bottom of the first groove wall 312 may be closer to the first mating wall 311 than the first connecting flange 314, and the flow cross section of the distribution channel 52 may be adjusted by adjusting the wall structure adjacent to the groove bottom.

Referring to fig. 8, since the plate heat exchanger 100 of the present application can be applied to a refrigerant scene having a high viscosity or a high flow rate, the flow cross-sectional size of the distribution channel 52 is a key factor affecting the distribution effect. The cross section of the distribution channel 52 having the smallest area among the several cross sections in the direction away from the central axis of the first porthole 21 is denoted as the first cross section M. Will be able to be accommodated in the distribution channel 52 in the plane of the first cross section MThe largest circle of (2) is defined as reference circle O, the area of reference circle O is S, and 0.8mm ² ≤S≤7.1mm ² . If the reference circle corresponding to the smallest cross section among the cross sections at several positions of the distribution channel 52 satisfies the above condition, it is explained that the size of the distribution channel 52 is such that the refrigerant having a relatively high viscosity or a relatively high flow rate is not easily clogged on the one hand, and is not excessively large on the other hand, so as not to affect the distribution effect of the refrigerant.

The outer edge adjacent to the distribution channel 52 among the two outer edges opposed in the longitudinal direction of the plate heat exchanger 100 is referred to as a first side edge, the distribution channel 52 is closer to the first side edge than the axis of the first porthole 21, and the distribution channel 52 is closer to the second porthole 22 than the axis of the first porthole 21. The distribution channels 52 extend in a radial direction away from the axis of the first portholes 21, i.e. the distribution channels 52 are arranged substantially in an oblique direction. Specifically, on a plane perpendicular to the stacking direction of the plates, the extending direction of the distribution channel 52 is referred to as a first direction N1, the width direction of the plates is referred to as a second direction N2, and the first direction N1 is inclined at an angle β of 20 ° to 70 ° to the second direction N2 toward the side closer to the first side edge. For example, in some embodiments of the application the angle β may be 30 °.

For the refrigerant flowing in the first plate-to-plate channel 51, most of the refrigerant directly enters the main heat exchange area 70 near the middle of the plate after leaving the inlet angular hole for flowing, but in order to not waste the heat exchange space around the angular hole of the plate, taking the first heat exchange surface 1 of the first plate 11 as an example, the refrigerant can be led to bypass the narrow turning area between the fourth angular hole 44 and the edge of the plate after exiting from the distribution channel 52, and in order to achieve the effect, by controlling the inclination angle of the first direction N1 relative to the second direction N2 between 20 ° and 70 °, the refrigerant can flow at the narrow turning area with relatively low flow pressure drop, thereby being beneficial to expanding the heat exchange area of the plate participating in heat exchange and improving the heat exchange effect of the plate heat exchanger 100.

In some embodiments of the application, the first circumferential wall 31 and the plate structure of the main heat transfer area 70 of the first plate 11 are integrally formed from the same metal blank at least after stamping, and the second circumferential wall 32 and the plate structure of the main heat transfer area 70 of the second plate 12 are integrally formed from the same metal blank at least after stamping. In practice, the processing of the sheet usually comprises a step of punching before stamping and then perforating, although there are also some sheet blanks in which the corner holes are made directly after stamping. The number of parts can be reduced through the plate structure of integral processing of first slab 11 and second slab 12, and through the complete slab that forms after stamping blank panel possess the relevant structure that forms distribution channel 52 simultaneously, can simplify the assembly, reduce the location degree of difficulty to independent distributor.

Of course, in other embodiments of the application, the plate heat exchanger 100 may comprise a separate distributor, in particular the first plate 11 comprises a first plate body and a distributor welded together with the first plate body. The distributor may be formed by stamping at least the plates, the projected outer contour of the distributor enclosing an area smaller than the projected outer contour of the first plate body in a plane perpendicular to the stacking direction of the plates, and for a separate distributor the distributor comprises the first circumferential wall 31 of the previous embodiment, and correspondingly the main heat exchanging zone 70 of the first plate 11 is provided in the first plate body. The independent distributor can be replaced conveniently, and the cost of the sheet processing mould is reduced.

In some embodiments of the present application, the plate material of the plate heat exchanger 100 is substantially stainless steel, and for the plate heat exchanger 100 of the stainless steel type which is common in the art, the stainless steel plate is in an elongated shape as a whole, the ratio X of the dimension in the width direction to the dimension in the length direction of the plate satisfies 0.2+.x+.0.5, which is smaller in the aspect ratio, larger in the aperture of the angular holes, and the ratio of the aperture of the angular holes in the width direction of the plate is generally approximately 1/3 or more, compared to the plate heat exchanger of the aluminum material. Therefore, for the stainless steel plate type heat exchanger, gas-liquid separation and uneven distribution of the fluid with two phases of gas and liquid are easier to occur at the relatively large angle holes, and therefore, the distribution effect of the refrigerant is required to be improved through the distribution channels, and the heat exchange performance of the stainless steel plate type heat exchanger is improved.

Further, the flow cross section of the refrigerant at the distribution channel 52 is smaller than the flow cross section of the refrigerant at the first corner hole 41, so that a pressure drop of the refrigerant in a certain range can be ensured, and the distribution uniformity of the refrigerant is improved.

Copper foil can be used as connecting solder between the plates of the plate heat exchanger 100, and the copper foil can be melted in the welding process so as to realize sealing and fixing between the parts. Of course, the plates of the plate heat exchanger 100 may be formed into a bimetal structure without copper foil as a connecting solder, that is, the plates are formed by combining stainless steel materials and copper materials, and the copper materials serving as the solder are coated on the surface of the stainless steel, so that copper is melted during high-temperature welding to further weld the stainless steel materials of different plates together. The processing mode of the bimetal plate can adopt a centrifugal casting method, for example, solid stainless steel and liquid copper metal are compositely molded under the centrifugal condition, and the stainless steel material and the copper material are combined into a whole through a transition layer with gradually changed joint positions by adopting the processes of metallurgy, centrifugal casting, heat treatment and the like, so that the wear resistance and the connection strength can be greatly improved.

In other embodiments of the present application, referring to another plate fitting manner corresponding to fig. 11 and 12, in fig. 11, the upper plate is the first plate 11, the lower plate is the second plate 12, and the flanges 71 of the first plate 11 and the second plate 12 are all extended from top to bottom, in which case the first groove wall 312 may be provided at the upper plate. I.e. by the concave first groove wall 312 of the upper first plate 11 mating with the planar second groove wall 322 of the lower second plate 12 to form the distribution channel 52.

In some embodiments of the present application, in the main heat exchange area 70 of the first plate 11, the first plate 11 is further provided with a plurality of herringbone protrusions, and adjacent herringbone protrusions 103 may be arranged alternately, and correspondingly, in the main heat exchange area 70 of the second plate 12, the second plate 12 is also provided with a plurality of herringbone protrusions 103, so that the herringbone protrusions 103 of the two plates cooperate to form a complex flow channel structure, and when fluid flows in the main heat exchange area 70 of the plate, the flowing form of the fluid has a groove direction flowing form along the adjacent herringbone channels and a flowing form crossing the herringbone channels in the up-down direction, so that the heat exchanger can obtain better heat exchange performance. Of course, some point-shaped protrusions can be arranged on the main heat exchange area 70 of each plate, and the heat exchange protrusions in the herringbone wave and point wave forms are common means for enhancing heat exchange of the plates, which are not repeated in the application.

The plate heat exchanger provided by the application is described in detail above. The principles and embodiments of the present application have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the core concepts of the application. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the application can be made without departing from the principles of the application and these modifications and adaptations are intended to be within the scope of the application as defined in the following claims.

Claims

1. A plate heat exchanger, characterized by comprising a plurality of plates arranged in a stack, the plurality of plates comprising adjacent first plates (11) and second plates (12); the plate heat exchanger is also provided with a first pore canal (21) penetrating through the two plates along the stacking direction of the plates; the first plate (11) comprises a first circumferential wall (31) and the second plate (12) comprises a second circumferential wall (32), both circumferential walls being located at the periphery of the first porthole (21);

the plates further have a main heat transfer zone (70), the main heat transfer zone (70) of the first plate (11) being located at a side of the first circumferential wall (31) remote from the first portholes (21); the main heat transfer zone (70) of the second plate (12) is located at the side of the second circumferential wall (32) remote from the first portholes (21); the plate heat exchanger further has a first plate interspaces (51), at least part of the first plate interspaces (51) being located between a main heat transfer area (70) of the first plate (11) and a main heat transfer area (70) of the second plate (12);

the plate heat exchanger further has distribution channels (52), the plate heat exchanger further having groove walls (520) forming the distribution channels (52); the first circumferential wall (31) comprises a first matching wall (311) and a first groove wall (312) connected with the first matching wall (311), and the first groove wall (312) is recessed from the first matching wall (311) in a direction away from the second plate (12); in the stacking direction, a space is reserved between the first matching wall (311) and the plate structure of the first plate (11) which is farthest away from the second plate (12) and between the first matching wall (311) and the plate structure of the second plate (12) which is farthest away from the first plate (11); the second circumferential wall (32) comprises a second matched wall (321) and a second groove wall (322) which are connected, and the wall surface of the second groove wall (322) facing the first groove wall (312) is arranged in parallel with the wall surface of the second matched wall (321) facing the first matched wall (311);

the first groove wall (312) and the second groove wall (322) are part of the groove wall part (520), and the first matching wall (311) and the second matching wall (321) are in sealing connection at least in partial areas; the distribution channel (52) communicates the first porthole (21) with the first inter-plate channel (51).

2. A plate heat exchanger according to claim 1, wherein the first circumferential wall (31) further comprises a first side wall (313) and a first connection flange (314), the first side wall (313) extending from the side of the first mating wall (311) closest to the first porthole (21) in a direction away from the second plate (12), the first connection flange (314) extending from the end of the first side wall (313) remote from the first mating wall (311) in a direction perpendicular to the stacking direction;

the second circumferential wall (32) further comprises a second side wall (323) and a second connecting flange (324), the second side wall (323) extending from a side of the second mating wall (321) close to the first porthole (21) in a direction away from the first plate (11), the second connecting flange (324) extending from an end of the second side wall (323) away from the second mating wall (321) in a direction perpendicular to the stacking direction;

the first connecting flange (314) is welded with one plate piece on the side, far away from the second plate piece (12), of the first plate piece (11), and the second connecting flange (324) is welded with one plate piece on the side, far away from the first plate piece (11), of the second plate piece (12).

3. A plate heat exchanger according to claim 2, wherein the first connection flange (314) has, perpendicular to the stacking direction, a first connection edge (315) connected to the first side wall (313) and a first end edge (316) remote from the first side wall (313), the maximum distance between the first connection edge (315) and the first end edge (316) being L1, and 2mm ∈l1 ∈10mm;

in a direction perpendicular to the stacking direction, the second connecting flange (324) has a second connecting edge (325) connected with the second side wall (323) and a second end edge (326) distant from the second side wall (323), a maximum distance between the second connecting edge (325) and the second end edge (326) is L2, and 2mm < L2 < 10mm;

the maximum distance between the first mating wall (311) and the first connecting flange (314) is equal to the maximum distance between the second mating wall (321) and the second connecting flange (324).

4. A plate heat exchanger according to claim 3, wherein the groove bottom of the first groove wall (312) is recessed with respect to the first mating wall (311) by a depth that is more than half the maximum distance between the first mating wall (311) and the first connection flange (314).

5. A plate heat exchanger according to claim 4, wherein the groove bottom of the first groove wall (312) is flush with the first connection flange (314); a portion of the first connecting flange (314) is connected to the first groove wall (312), and another portion of the first connecting flange (314) is connected to the first side wall (313).

6. A plate heat exchanger according to claim 1, wherein the plates have a length direction and a width direction, the ratio of the width direction dimension of the plates to the length direction dimension being X, and 0.2X 0.5;

-registering the smallest cross-section of the several cross-sections of the distribution channel (52) as a first cross-section in a direction away from the central axis of the first porthole (21); on the plane of the first cross section, the largest circle that can be accommodated in the distribution channel (52) is defined as a reference circle, the reference circle having an area S of 0.8mm ² ≤S≤7.1mm ² 。

7. A plate heat exchanger according to claim 2, wherein the first porthole (21) extends through the first connection flange (314) to form a first angular hole (41) at the first plate (11), the first porthole (21) extending through the second connection flange (324) to form a second angular hole (42) at the second plate (12); the first corner hole (41) and the second corner hole (42) are identical in shape and size;

the plate heat exchanger further comprises a second porthole (22), which second porthole (22) extends through the first plate (11) in the stacking direction to form a third angular hole (43) at the first plate (11), which second porthole (22) extends through the second plate (12) in the stacking direction to form a fourth angular hole (44) at the second plate (12);

-the first corner hole (41) and the third corner hole (43) are arranged along the width direction of the first plate (11), -the second corner hole (42) and the fourth corner hole (44) are arranged along the width direction of the second plate (12); the plate structure at the periphery of the third corner hole (43) is welded and sealed with the plate structure at the periphery of the fourth corner hole (44), so that the third corner hole (43) and the fourth corner hole (44) are separated from the first inter-plate channel (51).

8. A plate heat exchanger according to claim 7, wherein the distribution channel (52) is closer to the second porthole (22) than the axis of the first porthole (21); the distribution channels (52) extend in a radial direction away from the axis of the first portholes (21), and on a plane perpendicular to the stacking direction, the extension direction of the distribution channels (52) is denoted as a first direction, the width direction of the plate is denoted as a second direction, the outer edge of the plate heat exchanger adjacent to the first portholes (21) of two opposite outer edges in the length direction is denoted as a first side edge, and an angle of inclination of the first direction with respect to the second direction on a side close to the first side edge is equal to or greater than β, and 20 ° β is equal to or less than 70 °.

9. A plate heat exchanger according to claim 1, wherein in the first plate (11), the first circumferential wall (31) and the plate structure of the main heat exchanger zone (70) of the first plate (11) are formed as one and the same metal blank at least after stamping; in the second plate (12), the second circumferential wall (32) and the plate structure of the main heat transfer area (70) of the second plate (12) are also formed from the same metal blank at least after stamping.

10. A plate heat exchanger according to claim 1, wherein the first plate (11) comprises a first plate body and a distributor welded together with the first plate body; the distributor is formed by stamping the plates, and the area surrounded by the projection outline of the distributor is smaller than the area surrounded by the projection outline of the first plate main body in a plane perpendicular to the stacking direction; the distributor comprises the first circumferential wall (31), and the main heat exchanger area (70) of the first plate (11) is provided in the first plate body.