CN112414184A

CN112414184A - Plate heat exchanger

Info

Publication number: CN112414184A
Application number: CN202010891756.5A
Authority: CN
Inventors: 李永平; 李华; 邵汉
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2020-08-28
Filing date: 2020-08-28
Publication date: 2021-02-26

Abstract

The application discloses a plate heat exchanger, which comprises at least one group of first plate sheets and second plate sheets which are adjacent, wherein each plate sheet in the first plate sheets and the second plate sheets comprises a base plate part, each plate sheet is provided with at least one group of first angle holes and second angle holes, and the first angle holes are arranged in a boss part; the boss part of the first plate is hermetically connected with at least part of the area of the plate part on the periphery side of the second corner hole of the second plate; the plate part on the periphery side of the second corner hole of the first plate is not contacted with at least partial area of the boss part of the second plate; the first plate is also provided with a matching convex part and a circulating part; the groove formed on the reverse side of the first plate by the matching convex part is communicated with the groove formed on the reverse side of the first plate by the convex part; the broadsides of the two opposite broadsides of the plate sheet, which are relatively close to the first corner hole and the second corner hole in the same group, are marked as first broadsides; the matching convex part is closer to the first wide side than the circulating part; the circulating part is arranged on the front surface of the first plate sheet in a concave mode relative to the top of the boss part; this application is favorable to improving plate heat exchanger's heat transfer performance.

Description

Plate heat exchanger

Background

Refrigerant and secondary refrigerant flowing in the plate heat exchanger can respectively flow on the front side and the back side of each plate sheet so as to realize partition wall heat exchange through the plate sheets. With the continuous improvement of the requirement for the service performance of the plate heat exchanger, the plate heat exchanger needs to be structurally optimized to obtain the plate heat exchanger with stronger heat exchange performance. In the related art, the uniformity of fluid flowing at two sides of each plate is difficult to be considered, so that the heat exchange effect of the plate heat exchanger still has a space for improvement.

Disclosure of Invention

This application improves plate heat exchanger, is favorable to compromise the homogeneity that the positive and negative both sides fluid of slab flows, improves plate heat exchanger's heat transfer effect.

The embodiment of the application provides a plate heat exchanger, which comprises a plurality of stacked circulation plates, wherein at least one group of adjacent first plate and second plate is arranged in the plurality of circulation plates, and the front surface of each first plate is opposite to the back surface of each second plate; each of the first plate piece and the second plate piece comprises a base plate part, the plate pieces are provided with at least one group of first angle holes and second angle holes, and the first angle holes and the second angle holes in the same group are arranged along the width direction of the plate pieces; the sheet is also provided with a boss part; the boss part is protruded on the front surface of the sheet relative to the base plate part; the first corner hole is formed in the boss part; the plate part on the periphery of the second corner hole of the second plate is connected with the boss part of the first plate in a sealing way; the plate part on the periphery side of the second corner hole of the first plate is not contacted with at least partial area of the boss part of the second plate;

the first plate is also provided with a matching convex part and a circulating part; the matching convex part protrudes from the side wall of the boss part to one side far away from the first corner hole, and the maximum distance between the side wall of the boss part and the edge of the first corner hole is smaller than the distance between the tail end of the matching convex part and the edge of the first corner hole; the matching convex part protrudes on the front surface of the first plate relative to the base plate part, and a groove formed on the back surface of the first plate by the matching convex part is communicated with a groove formed on the back surface of the first plate by the boss part; the broadsides of the two opposite broadsides of the plate sheet, which are relatively close to the first corner hole and the second corner hole in the same group, are marked as first broadsides; the flow part is positioned on the outer peripheral side of the boss part, and the engaging convex part is closer to the first broad side than the flow part; the circulating part is arranged on the front surface of the first plate sheet in a concave mode relative to the top of the boss part;

defining one of planes perpendicular to the stacking direction of the flow-through plates as a first plane; the projection outline of the wall surface of the first plate piece forming the first corner hole on the plane perpendicular to the front surface of the base plate part of the first plate piece is provided with a first circular arc and a second circular arc which are opposite in the width direction of the plate piece; the first circular arc is closer to the second corner hole than the second circular arc; defining a sector area in the first plane; the center of a circle where the first arc is located is defined as the center of the fan-shaped area, and the radius of the first arc is recorded as R; the fan-shaped area is provided with a first line segment and a second line segment which are matched with the circle center to form an acute central angle, and the lengths of the first line segment and the second line segment are both 2R; the direction perpendicular from this centre of a circle and keeping away from the first broadside of slab defines as first direction, and the contained angle that first line section leaned on the side of second angle hole for first direction is 45, and the contained angle that second line section leaned on the side of second angle hole for first direction is 70, circulation portion is in the projection of first plane is at least partly located fan-shaped region, and along boss portion circumferential direction, first projection one side extends to fan-shaped regional first line section at least, and the opposite side extends to fan-shaped regional second line section at least.

In the application, the flow-through part is arranged in a concave way relative to the top of the boss part, and the corresponding first projection of the flow-through part is at least partially positioned in the fan-shaped area, and for the fluid flowing on the front side of the plate, the flow-through part is beneficial to distributing the fluid from the second corner hole to the width direction of the plate through the flow-through part at a low flow pressure drop; the matching convex part is closer to the first wide edge than the circulating part, and for the fluid flowing on the reverse side of the plate, the matching convex part is beneficial to distributing the fluid from the first corner hole at a lower flowing pressure drop through the groove formed on the reverse side of the plate by the matching convex part in the area close to the first wide edge; therefore, the uniform distribution of the fluid on the plates on the front side and the back side of the first plate and the reduction of the flowing pressure drop of the fluid are both facilitated, and the heat exchange effect of the plate heat exchanger is improved.

Drawings

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

FIG. 2 is a schematic view of a first plate of the present application;

FIG. 3 is an enlarged view of a portion of the structure of a first plate and a second plate assembled together according to the present application;

FIG. 4 is an enlarged view of a structure of the first plate shown in FIG. 2;

FIG. 5 is an enlarged view of another structure shown in phantom in FIG. 2 of the present application;

FIG. 6 is another schematic illustration of a panel assembly formed by a first panel and a second panel assembled together according to the present application;

FIG. 7 is an enlarged view of a portion of the first plate of FIG. 6 of the present application;

FIG. 8 is an enlarged view of the opposite side of the plate assembly of FIG. 6 according to the present application;

FIG. 9 is another schematic view of the first plate of the present application;

FIG. 10 is an enlarged view of a portion of the first plate of FIG. 9 of the present application;

fig. 11 is an enlarged view of another angle portion of the first plate in fig. 9 of the present application.

Detailed Description

In order to make the technical solutions of the present invention better understood, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.

Referring to fig. 1, the present application provides a plate heat exchanger 10 including at least one set of adjacent first and

second plates

101 and 102, in some embodiments, the number of the first and

second plates

101 and 102 may be multiple, and the plate heat exchanger 10 may further include other third and fourth plates, etc. having different structures from the first and

second plates

101 and 102. 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 plate heat exchanger 10 generally includes a plurality of flow plates, and the plurality of flow plates are stacked. In any two adjacent flow plates, the front surface 1001 of the lower plate is opposed to the back surface 1002 of the upper plate, and in fig. 2, the surface of the first plate 101 facing outward, that is, the visible surface is defined as the front surface 1001, and the surface facing inward, that is, the invisible surface is defined as the back surface 1002. For a plurality of plates, the plates can be molded through a single pair of dies, namely each plate is a plate with the same shape and structure, when the plates are assembled, adjacent plates can be arranged reversely, of course, the plates can be molded through two pairs of dies or even more pairs of dies, namely the plates can be in different shapes or structures, for example, the main heat exchange area of one plate is in a flat plate structure, the main heat exchange area of the other plate is provided with a point wave-shaped convex structure, the two plates can be assembled together and alternately stacked, as long as the plates meet the corresponding relation of the plate structure and the plate assembly described in the application.

A plurality of plates are stacked in the direction D-D in fig. 1 to form a heat exchange core, the front surface 1001 of the first plate 101 is opposite to the back surface 1002 of the second plate 102, and when the number of the first plate 101 and the number of the second plate 102 are both multiple, the back surface 1002 of the first plate 101 may be opposite to the front surface 1001 of another second plate 102. The plates also include flanges surrounding the base plate portion 11, which can be sealed by welding, such as brazing, when the plates are assembled, to facilitate the retention of fluid in the flow passages formed between the plates.

Referring to fig. 2 and 3, each of the first sheet 101 and the second sheet 102 includes a base plate portion 11, and for ease of distinction, the base plate portion of the second sheet 102 is denoted by 11' in fig. 3. The first plate 101 is provided with at least one set of first angular holes 21 and second angular holes 22, and the second plate 102 is also provided with at least one set of first angular holes 21 'and second angular holes 22'. The first corner hole 21 is provided with a boss portion 200, and the boss portion 200 is protruded on the front surface 1001 of the first sheet 101 with respect to the base plate portion 11. The second corner hole 22 is provided with a boss portion 200 ', the boss portion 200' protruding from the base plate portion 11 'on the front face 1001' of the second plate 102. The first corner hole 21 is provided to the boss portion 200 so that the first corner hole 21 forms a boss hole. The second corner hole 22 may be a planar hole provided in the substrate portion 11, but the second corner hole 22 may be a boss hole provided in a boss, and the boss in which the second corner hole 22 is provided may protrude from the substrate portion 11 toward the front side or the back side of the sheet.

As illustrated in the first sheet 101, the first corner holes 21 and the second corner holes 22 of the same group of the first sheet 101 are arranged along the sheet width direction W-W, and when two sheets are assembled, as shown in fig. 3, the plate portion on the peripheral side of the second corner hole 22 'of the second sheet 102 above is connected with the boss portion 200 of the first sheet 101 below in a sealing manner, so that the first corner holes 21 of the first sheet 101 and the second corner holes 22' of the second sheet 102 are both blocked from the plate-to-plate passages between the first sheet 101 and the second sheet 102, and as illustrated in the flow schematic of the fluid in the first sheet 101, the fluid cannot flow from the first corner holes 21 of the first sheet 101 into the front surface of the first sheet 101. Accordingly, the plate portion on the periphery side of the second corner hole 22 of the lower first plate 101 is not in contact with the boss portion 200' of the upper second plate 102 at least in part. Thus, the second corner hole 22 of the first plate 101 and the first corner hole 21' of the second plate 102 are both in communication with the interplate channel between the first plate 101 and the second plate 102, and fluid can flow from the second corner hole 22 of the first plate 101 into the front surface of the first plate 101.

In some embodiments, the first plate 101 and the second plate 102 are each provided with two first corner holes 21 and two second corner holes 22. Specifically, the first plate 101 includes corner hole distribution areas on both sides in the length direction and a main heat exchange area located between the two corner hole distribution areas, and in each corner hole distribution area, a set of first corner holes 21 and second corner holes 22 may be provided. Referring to fig. 2, the first plate 101 is taken as an illustration, and the two first corner holes 21 are located on the same side of the first plate 101 in the width direction W-W, and the two second corner holes 22 are located on the other side of the first plate 101 in the width direction W-W. In the angular hole layout mode, the flowing mode of the fluid is unilateral flow. Of course, in some other modes, the fluid may also flow diagonally, that is, the two first corner holes 21 of the first plate 101 are diagonally arranged, and the two second corner holes 22 are diagonally arranged.

Referring to fig. 2, 4 to 11, the first sheet 101 is further provided with a fitting protrusion 31 and a circulating part 32, the fitting protrusion 31 protrudes at a front surface 1001 of the first sheet 101 with respect to the base plate part 11, the fitting protrusion 31 is connected to the boss part 200, the fitting protrusion 31 protrudes from a side wall of the boss part 200 to a side away from the first corner hole 21, and a distance between a tip of the fitting protrusion 31 and an edge of the first corner hole 21 is larger than a maximum distance between a side wall of the boss part 200 and an edge of the first corner hole 21, so that the tip of the fitting protrusion 31 is further away from the first corner hole 21 than the side wall of the boss part 200. The end of the fitting protrusion 31 is the farthest end of the fitting protrusion 31 from the first corner hole 21, and the distance between the end of the fitting protrusion 31 and the edge of the first corner hole 21 is the distance between the farthest end of the fitting protrusion 31 from the first corner hole 21 and the edge of the first corner hole 21, and the fitting protrusion 31 and the boss portion 200 form an integral structure which partially protrudes outward.

Referring to a schematic view of the reverse structure of the first plate 101 in one form illustrated in fig. 8, the fitting projection 31 forms a first groove 33 on the reverse side 1002 of the first plate 101, the boss portion 200 forms a second groove 34 on the reverse side 1002 of the first plate 101, and since the fitting projection 31 is connected to the boss portion 200 on the front side of the first plate 101, the first groove 33 and the second groove 34 are communicated with each other on the reverse side of the first plate 101. Therefore, the problems of larger flow resistance and smaller flow capacity in the corner hole area, particularly in the curve area where the fluid turns because of longer path, can be effectively solved. Referring to the fluid flow pattern indicated by the dotted line with an arrow in fig. 8, when the fluid flows into the opposite side 1002 of the first plate 101 from the first corner hole 21, the fluid enters the first groove 33 through the second groove 34, and under the flow guiding effect of the first groove 33, the fluid can be distributed in the width direction of the plate with a lower flow pressure drop, which is beneficial to improving the uniformity of the fluid flow on the opposite side of the plate.

The flow portion 32 is located on the outer peripheral side of the boss portion 200, and the flow portion 32 is recessed from the top of the boss portion 200 on the front surface 1001 of the first sheet 101. The broadside of the two opposite broadsides (501, 502) of the first sheet, which is relatively close to the first corner hole 21 and the second corner hole 22 of the same group, is designated as a first broadside 501, and correspondingly, the broadside of the other sheet, which is far away from the first broadside, is designated as a second broadside 502. The engaging projection 31 is closer to the first broad side 501 than the circulating portion 32. For the fluid flowing on the front surface 1001 side of the first plate 101, since the circulation part 32 is recessed with respect to the top of the boss part 200, the fluid can flow at the circulation part 32, and accordingly, when the fluid flows into the front surface of the first plate 101 from the second corner hole 22, the circulation part 32 can have a certain flow guiding effect on the fluid, so that the fluid can flow into the main heat exchange area of the plate through the circulation part 32 with a relatively low flow pressure drop.

The fitting projection 31 is closer to the first broad side 501 than the circulating part 32, and for the fluid flowing on the reverse side 1002 of the first plate 101, the fitting projection 31 facilitates the flow distribution of the fluid from the first corner hole 21 to the corner hole distribution area near the first broad side 501 through the first groove 33 formed on the reverse side 1002 of the first plate 101 by the fitting projection 31. The first grooves 33 are beneficial to reducing the flow pressure drop of the fluid and have a certain flow guiding effect on the fluid, so that the fluid can flow in the corner hole distribution area more easily, and the flow uniformity of the fluid is improved. Moreover, since the first corner hole 21 and the second corner hole 22 are relatively close to the first broad side 501, in the corner hole distribution area provided with the corner holes, the top of the matching protrusion 31 can be in contact with the base plate 11 of the opposite side 1002 of the adjacent second plate sheet 102, thereby also being beneficial to improving the connection strength between the plate sheets and contributing to the overall stability of the product. This is advantageous for both the uniform distribution of fluid over the plates on both the front and back sides of the first plate 101 and for reducing the fluid flow pressure drop, and thus helps to improve the heat exchange performance of the plate heat exchanger 10.

Referring to fig. 4, one of several planes perpendicular to the stacking direction of the flow-through plates is defined as a first plane, in a particular product, the first plane may define a reference plane in the plate structure of the first plate 101, for example, the plane where the front surface of the substrate portion 11 of the first sheet 101 is located may be referred to as a first plane S1 for projection of other structures, although the first plane S1 may be a plane perpendicular to the sheet stacking direction, it should be understood that the plane of the front surface of the base plate portion 11 of the first sheet 101 is an absolute plane perpendicular to the sheet stacking direction, which is difficult to be ensured by the manufacturing process during the sheet forming and pressing process, but still has a certain flatness, and therefore, a reference surface within a range of flatness allowed by design and manufacturing tolerances may be used as a reference datum for the first plane, e.g. the top front face of the boss portion 200 may also be used as the first plane, etc.

The first plate 101 forms a wall surface of the first corner hole 21, that is, a projection profile of the wall surface of the hole wall located at the periphery of the first corner hole 21 on the first plane S1 has a first circular arc 211 and a second circular arc 212 which are opposite to each other in the plate width direction W-W, and the first circular arc 211 is closer to the second corner hole 22 than the second circular arc 212.

A sector area S2 is defined on the plane S1, a center O of a circle where the first arc 211 is located is defined as the center O of the sector area S2, a radius of the first arc 211 is denoted as R, and the sector area S2 has a first line segment P1 and a second line segment P2 which form an acute central angle with the center O. The first line segment P1, the second line segment P2 and the circle O cooperate to form a larger fan shape and a smaller fan shape, the fan-shaped area S2 is a smaller fan shape including the circle O and two sides (the first line segment P1 and the second line segment P2), a direction perpendicular to the circle center O and away from the first wide side 501 of the plate is defined as a first direction X1, an included angle β 1 of the first line segment P1 inclined to the side of the second corner hole 22 with respect to the first direction X1 is 45 °, an included angle β 2 of the second line segment P2 inclined to the side of the second corner hole 22 with respect to the first direction X1 is 70 °, and the lengths of the first line segment P1 and the second line segment P2 are both 2R.

The projection of the flow portion 32 on the first plane S1 is at least partially located in the fan-shaped region S2, and the flow portion 32 extends at least to the first line segment P1 of the fan-shaped region S2 on the side of the projection of the first plane S1 and at least to the second line segment P2 of the fan-shaped region S2 in the circumferential direction of the boss portion 200. Fluid may flow at the flow-through 32 at the peripheral region of the sidewall of the boss portion 200. The inventors have conducted a great deal of experimental verification to find that the sector area S2 is a critical area where the flow portion 32 is provided, and the fluid can flow from the first line segment P1 side to the second line segment P2 side or vice versa, i.e., from the second line segment P2 side to the first line segment P1 side at the sector area S2 under the condition that the position of the flow portion 32 satisfies the sector area S2. Referring to the fluid flow direction schematic shown by the dotted line with arrows in fig. 4, when fluid flows on the front surface 1001 of the first plate 101, the fluid first flows into the corner hole distribution area of the plate through the second corner hole 22, and due to the existence of the boss portion 200, a part of the fluid needs to flow around the boss portion 200 and enter the main heat exchange area of the first plate 101, so that, based on the existence of the flow through portion 32, the heat exchange elements provided in the main heat exchange area of the plate or the heat exchange elements such as fin plates sandwiched between the plates are not easily connected to the boss portion 200 in a flush manner or even with a punching depth exceeding the boss portion 200 at the fan-shaped area S2, so that the fluid can reenter the main heat exchange area of the plate through the flow through portion 32 relatively forming the concave structure, which facilitates the fluid to be distributed to the width direction W-W of the first plate 101 with a smaller flow pressure drop as soon. Thereby improving the flow uniformity of the fluid on the front side of the plate.

In some embodiments, the aspect ratio of the first plate 101 and the second plate 102 is 3 or less. In such a relatively "squat" plate, the flow-through 32 may be more beneficial to the distribution effect of the fluid flowing on the front side of the plate in the width direction of the plate. And the first grooves 33 formed on the opposite side of the plate by the fitting projections 31 further contribute to the distribution effect of the fluid flowing on the opposite side of the plate in the width direction of the plate. The length-width ratio L/W of the plate is less than or equal to 3. Referring to fig. 2, the length-width ratio L/W of the sheet is 3 or less, and the length and width of the sheet may not include the length and width of the burring part. Or further, on the basis that the length-width ratio of the plate is less than or equal to 3, the ratio of the distance between the centers of two corner holes on the same side in the width direction of the plate to the width of the whole plate is less than or equal to 2.

The first plate 101 is further provided with a plurality of heat exchanging protrusions 60, the heat exchanging protrusions 60 protrude toward the front surface 1001 side of the first plate 101 with respect to the base plate 11, the heat exchanging protrusions 60 are integrally formed with the base plate 11, for example, the heat exchanging protrusions 60 may be press-formed, and the heat exchanging protrusions 60 are formed with recesses in the base plate 11 on the plate back surface 104. Or, the heat exchanging protrusion 60 may be a separate component, for example, the heat exchanging protrusion 60 is a fin plate, and in the main heat exchanging area of the plate, the heat exchanging protrusion 60 is brazed with the first plate 101, and is finally formed into a whole, except for adopting a channel structure such as a fin plate, a corrugated plate, a point wave plate, a filiform filler, a porous medium, etc. may also be adopted, so as to achieve structural satisfaction of plate strength, and simultaneously enhance the effects of turbulence, mixing, increasing heat exchanging area, etc. of fluid in a channel formed by two adjacent plates, and finally achieve enhanced heat exchange, and improve the performance of the plate heat exchanger product. The height of the heat exchanging protrusion 60 may be equivalent to the height of the boss portion 200.

Referring to the structural schematic of the first plate 101 in fig. 2 and 3, the plate has a relatively dense point wave structure, and adjacent heat exchanging protrusions 60 can be transited by a concave curved surface structure. Of course, adjacent heat exchanging protrusions 60 may be separated from each other by the base plate portion 11, so that each heat exchanging protrusion 60 may form an independent bump structure. Of course, the heat exchanging protrusions 60 may not exist in the form of dotted bosses, and the heat exchanging protrusions 60 may be herringbone-wave heat exchanging elements, and as shown in fig. 6, a plurality of heat exchanging protrusions 60 in the form of multiple herringbone waves are arranged along the length direction of the first plate 101. The heat exchange convex parts 60 in the herringbone wave form have more complicated flow channel structures, and when fluid flows in the plate main heat exchange area, the fluid has a flow form along a channel formed by two adjacent heat exchange convex parts 60 and also has a flow form turning over the heat exchange convex parts 60 in the vertical direction, so that the plate has better heat exchange performance.

When the first fluid enters the first plate 101 from the second corner hole 22 in the front surface thereof, the boss portion 200 needs to be in sealing contact with the plate portion on the peripheral side of the second corner hole 22 of the adjacent second plate, so as to block the passage of the second fluid entering the plates. So that the first fluid cannot pass through the first corner hole 21. And the heat exchange protrusions 60 arranged in the main heat exchange area are relatively close to the boss portion 200, so that the fluid around the boss portion 200 is easily jammed to bring a high pressure drop, and the flow portion 32 of the present application can effectively reduce such a pressure drop. In some embodiments, the sidewall of the boss portion 200 and the sidewall of the heat exchanging protrusion 60 are separated by the substrate portion 11, and a part of the substrate portion 11 forms the flow portion 32. Reference may be made to the structural illustration of the first plate 101 in fig. 2.

In some other embodiments, the first plate 101 is also provided with a plurality of heat exchanging protrusions 60, the heat exchanging protrusions 60 protrude toward the front surface 1001 side of the first plate 101 with respect to the base plate portion 11, and at least one heat exchanging protrusion 60 of the plurality of heat exchanging protrusions 60 is connected to the boss portion 200. Reference may be made to the structure of the first sheet 101 as illustrated in fig. 7 and the structure of the first sheet 101 illustrated as described in fig. 10.

In fig. 7, a fan-shaped area S2 is defined, a projection of the flow portion 32 on the first plane S1 is at least partially located in the fan-shaped area S2, and in the circumferential direction of the boss portion 200, the flow portion 32 extends at least to a first line segment P1 of the fan-shaped area S2 on the projection side of the first plane S1 and at least to a second line segment P2 of the fan-shaped area S2 on the other side, and in the fan-shaped area S2, a side wall of the boss portion 200 and a side wall of the heat exchanging protrusion 60 are separated by the base plate portion 11, and a part of the base plate portion 11 forms the flow portion 32.

In fig. 10 and 11, a plurality of heat exchanging protrusions 60 are connected to the boss portion 200, at least one heat exchanging protrusion 60 is provided with a flow guiding groove 601, the flow guiding groove 601 is recessed from the top of the heat exchanging protrusion 60, and the depth of the flow guiding groove 601 may be the depth of the flow channel between the adjacent heat exchanging protrusions 60. The flow guide groove 601 is at least a part of the flow-through portion 32. In fig. 11, a sector area S2 is defined, the projection of the flow-through 32 onto the first plane S1 is at least partially located in the sector area S2, and the flow-through 32 comprises two flow-guiding grooves 601 and flow-through channels located between adjacent heat exchanging protrusions 60. The depths of the respective positions of the flow-through 32 may not be equal, but the flow-through 32 still satisfies that the flow-through 32 extends at least to the first line segment P1 of the sector-shaped area S2 on the side of the projection of the first plane S1 and at least to the second line segment P2 of the sector-shaped area S2 in the circumferential direction of the boss portion 200.

Referring to fig. 5, 7, 10, and 11, the fitting convex portion 31 includes a first extending portion 311, the first extending portion 311 has a linear extending direction, the first extending portion 311 is connected to the boss portion 200, a center line of the extending direction corresponding to a projection pattern of the first extending portion 311 on the first plane S1 is a first center line L1, an intersection point of the first center line L1 and the first arc 211 is a first intersection point a1, and an included angle β 3, which is an inclined angle of a connecting line L2 of the first intersection point a1 and the center O to the side of the second corner hole 22 with respect to the first direction X1, ranges from 70 ° to 160 °. In some embodiments, a line L2 connecting the first intersection a1 with the center O extends in a direction coincident with the direction of extension of the first centerline L1. This is more advantageous in reducing the flow pressure drop of the fluid.

Of course, the fitting convex portion 31 may have a curved extended form, or the fitting convex portion 31 may have a block shape or a dot shape, and the shape of the fitting convex portion 31 is not particularly limited in the present application.

As shown in fig. 9, 10 and 11, the fitting protrusion 31 further includes a second extending portion 312 and a curved transition portion 313, the second extending portion 312 also has a linear extending direction, and the curved transition portion 313 is connected between an end of the first extending portion 311 in the extending direction and an end of the second extending portion 312 in the extending direction. The first extension 311 and the second extension 312 are rounded by a curved transition 313. The matching convex part 31 can also form a structure similar to a herringbone wave type, on one hand, the heat exchange performance of the corner hole distribution area is enhanced, on the other hand, welding spots are increased, and the connection strength between the plates at the corner hole distribution area is enhanced.

Referring to the plate structure illustrated in fig. 2, 3 and 4, the projection profile of the wall surface of the first plate 101 forming the first corner hole 21 on the first plane S1 is an oval, the first circular arc 211 and the second circular arc 212 are both semi-circular arcs, the projection profile of the wall surface of the first plate 101 forming the first corner hole 21 on the first plane S1 further includes two parallel third line segments 213, the third line segments 213 are connected between the first circular arc 211 and the second circular arc 212, and the extension direction of the third line segments 213 coincides with the width direction W-W of the plate. The second corner hole 22 may be substantially comparable in shape and size to the first corner hole 21. Namely, the projection profile of the second angular hole 22 on the first plane S1 is also oblong. The first angular holes 21 and the second angular holes 22 are arranged to be relatively slender holes, so that the flow equalizing effect of the space around the angular holes can be effectively improved, and distribution of fluid in the width direction of the plate is facilitated.

Referring to fig. 11, the projection profile of the wall surface of the first plate 101 forming the first angular hole 21 on the first plane S1 is oblong, i.e., the projection profile includes two semicircular arcs and two parallel third line segments, and the second angular hole 22 may be a perfect circle. One of the first angled holes 21 and the second angled holes 22 serves as an inlet and an outlet of the refrigerant, and the other serves as an inlet and an outlet of the coolant. Of course, the projection profile of the wall surface of the first plate 101 forming the first corner hole 21 on the first plane S1 may also be a perfect circle. The projection profile of the wall surface of the first sheet 101 forming the second angular hole 22 on the first plane S1 may be one of an oblong, a perfect circle or an ellipse. Similarly, the projection profile of the wall surface of the second plate 102 forming the first angular hole 21 on the first plane S1 and the projection profile of the wall surface forming the second angular hole 22 may also be similar to the first plate 101, which is not limited in the present application.

The plate heat exchanger according to the invention has been described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the core concepts of the present invention. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.

Claims

1. A plate heat exchanger (10) comprises a plurality of flow plates which are arranged in a stacked mode, wherein the plurality of flow plates comprise at least one group of first plate sheets (101) and second plate sheets (102) which are adjacent to each other, and the front surfaces of the first plate sheets (101) are opposite to the back surfaces of the second plate sheets (102); each of the first plate (101) and the second plate (102) comprises a base plate part (11), the plates are provided with at least one group of first corner holes (21) and second corner holes (22), and the first corner holes (21) and the second corner holes (22) in the same group are arranged along the width direction of the plates; the sheet is also provided with a boss part (200); the boss part (200) protrudes from the base plate part (11) on the front surface of the sheet; the first corner hole (21) is provided in the boss portion (200); the plate part on the periphery side of the second corner hole (22) of the second plate (102) is connected with the boss part (200) of the first plate (101) in a sealing way; the plate part on the periphery side of the second corner hole (22) of the first plate (101) is not contacted with at least part of the area of the boss part (200) of the second plate (102);

the first plate (101) is also provided with a matching convex part (31) and a circulating part (32); the matching convex part (31) is arranged in a protruding mode from the side wall of the boss part (200) to the side far away from the first corner hole (21), and the maximum distance between the side wall of the boss part (200) and the edge of the first corner hole (21) is smaller than the distance between the tail end of the matching convex part (31) and the edge of the first corner hole (21); the matching convex part (31) protrudes on the front surface of the first plate piece (101) relative to the base plate part (11), and a groove formed on the back surface of the first plate piece (101) by the matching convex part (31) is communicated with a groove formed on the back surface of the first plate piece by the boss part (200); the broadside of the two opposite broadsides of the plate, which is relatively close to the first corner hole (21) and the second corner hole (22) of the same group, is marked as a first broadside (501); the circulation part (32) is positioned on the outer peripheral side of the boss part (200), and the matching convex part (31) is closer to the first wide side (501) than the circulation part (32); the circulation part (32) is arranged on the front surface of the first plate (101) and is recessed relative to the top of the boss part (200);

defining one of planes perpendicular to the stacking direction of the flow-through plates as a first plane; the projection outline of the wall surface of the first plate (101) forming the first corner hole (21) on the first plane is provided with a first circular arc (211) and a second circular arc (212) which are opposite in the width direction of the plate; the first circular arc (211) is closer to the second corner hole (22) than the second circular arc (212); a fan-shaped area (S2) is defined on a first plane, the center of a circle where a first circular arc (211) is located is defined as the center (O) of the fan-shaped area (S2), the radius of the first circular arc (211) is recorded as R, the fan-shaped area (S2) is provided with a first line segment (P1) and a second line segment (P2) which are matched with the center (O) to form an acute central angle, and the lengths of the first line segment (P1) and the second line segment (P2) are both 2R; the direction perpendicular to the circle center (O) and far away from the first wide edge (501) of the plate is defined as a first direction (X1), the included angle (beta 1) of the first line segment (P1) inclining to the side where the second corner hole (22) is located relative to the first direction (X1) is 45 degrees, and the included angle (beta 2) of the second line segment (P2) inclining to the side where the second corner hole (22) is located relative to the first direction (X1) is 70 degrees;

the projection of the flow-through part (32) onto the first plane is at least partially located in a sector area (S2) and extends, in the circumferential direction along the boss part (200), on one side at least to a first line segment (P1) and on the other side at least to a second line segment (P2).

2. A plate heat exchanger (10) according to claim 1, wherein the length to width ratio of the plates is 3 or less.

3. A plate heat exchanger (10) according to claim 1, wherein the first plate (101) is further provided with a number of heat exchanging protrusions (60); the heat exchange convex part (60) is convex towards the front surface of the first plate piece (101) relative to the base plate part (11); the side wall of the boss part (200) and the side wall of the heat exchanging protrusion (60) are separated by a substrate part (11), and a part of the substrate part (11) forms the flow part (32).

4. A plate heat exchanger (10) according to claim 1, wherein the first plate (101) is further provided with a number of heat exchanging protrusions (60); the heat exchange convex part (60) is convex towards the front surface of the first plate piece (101) relative to the base plate part (11); the heat exchange convex part (60) is connected with the convex part (200), the heat exchange convex part (60) is provided with a flow guide groove (601), the flow guide groove (601) is recessed from the top of the heat exchange convex part (60), and the flow guide groove (601) is at least one part of the circulating part (32).

5. A plate heat exchanger (10) according to claim 1, wherein the mating protrusion (31) comprises a first extension portion (311), the first extension portion (311) has a linear extension direction, the first extension portion (311) is connected to the boss portion (200), a center line of a projection pattern of the first extension portion (311) on the plane is denoted as a first center line (L1), an intersection point of the first center line (L1) and the first circular arc (211) is denoted as a first intersection point (a1), and an included angle (β 3) of a connecting line (L2) of the first intersection point (a1) and the center point (O) inclined to a side of the second angular hole (22) with respect to the first direction (X1) ranges from 70 ° to 160 °.

6. A plate heat exchanger (10) according to claim 5, wherein a line (L2) connecting the first intersection point (A1) with the centre (O) extends in a direction coinciding with the direction of extension of the first centre line (L1).

7. A plate heat exchanger (10) according to claim 5, wherein the mating protrusion (31) further comprises a second extension (312) and a curved transition (313); the second extension part (312) also has a linear extension direction, the curved transition part (313) is connected between the end of the first extension part (311) in the extension direction and the end of the second extension part (312) in the extension direction, and the first extension part (311) and the second extension part (312) are in round transition through the curved transition part (313).

8. A plate heat exchanger (10) according to claim 1, wherein the second corner hole (22) is a planar hole provided in the base plate portion (11).

9. A plate heat exchanger (10) according to claim 1, wherein the projection profile of the wall surface of the first plate (101) forming the first corner hole (21) on the plane further comprises two parallel third line segments (213), and the first circular arc (211) and the second circular arc (212) are both semicircular circular arcs; the third line segment (213) is connected between the first circular arc (211) and the second circular arc (212), and the extending direction of the third line segment (213) is overlapped with the width direction of the plate; or the projection outline of the wall surface of the first sheet piece (101) forming the first corner hole (21) on the plane is a perfect circle;

the projection outline of the wall surface of the first sheet piece (101) forming the second corner hole (22) on the plane is one of a perfect circle, an ellipse or an oblong.

10. A plate heat exchanger (10) according to claim 1, wherein the plates are provided with two first corner holes (21) and two second corner holes (22); the two first corner holes (21) are located on one side of the plate in the width direction, and the two second corner holes (22) are located on the other side of the plate in the width direction; or, the two first corner holes (21) are arranged diagonally, and the two second corner holes (22) are arranged diagonally.