CN112146484A - Plate heat exchanger - Google Patents
Plate heat exchanger Download PDFInfo
- Publication number
- CN112146484A CN112146484A CN201910579121.9A CN201910579121A CN112146484A CN 112146484 A CN112146484 A CN 112146484A CN 201910579121 A CN201910579121 A CN 201910579121A CN 112146484 A CN112146484 A CN 112146484A
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- China
- Prior art keywords
- heat exchange
- plate
- heat
- exchange surface
- matching part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
Abstract
The invention discloses a plate heat exchanger, which comprises a first plate and a second plate; the first plate comprises a first flat plate part, a first heat exchange surface, a second heat exchange surface and a first heat exchange matching part, and the first heat exchange matching part protrudes out of the first flat plate part on the first heat exchange surface; the second plate comprises a second flat plate part, a third heat exchange surface, a fourth heat exchange surface and a second heat exchange matching part, and the second heat exchange matching part protrudes out of the second flat plate part on the third heat exchange surface; the first heat exchange surface is opposite to the third heat exchange surface, and the second heat exchange surface is opposite to the fourth heat exchange surface; the first flat plate part is opposite to the second heat exchange matching part, and at least part of the second heat exchange matching part extends into the first concave area; the first heat exchange matching part is opposite to the second flat plate part; the first heat exchange matching part at least partially extends into the second concave area; a first inter-plate channel is formed between the first heat exchange surface and the third heat exchange surface, and a second inter-plate channel is formed between the second heat exchange surface and the fourth heat exchange surface. The invention improves the heat exchange performance of the plate heat exchanger, reduces the filling amount of the refrigerant of the system and enhances the channel strength.
Description
Technical Field
The invention relates to the technical field of heat exchange, in particular to a plate type heat exchanger.
Background
As shown in fig. 1, the inventor knows a scheme that a dot-shaped protrusion 31 on a first heat exchange surface 21 on an nth plate and a dot-shaped groove 32 on a second heat exchange surface 22 on an (n + 1) th plate are arranged in a staggered manner, and the top end portion of the dot-shaped protrusion 31 on the first heat exchange surface 21 on the nth plate is welded on a flat plate surface 221 and is pushed to the plurality of plates in sequence. According to the assembly scheme, for the fluids with high requirements of refrigerants on channel pressure drop, the maximum depth of the flow section of the flow channel on the refrigerant side can reach 2 times of the stamping depth Dp, under the requirements of small installation space and high heat exchange performance of the plate heat exchanger, the flow channel formed between the plates is limited by a sheet metal stamping process, the compactness and the compactness of the flow channel formed between the plates are not good, and the integral heat exchange effect of the plate heat exchanger is not facilitated.
Disclosure of Invention
The invention improves the plate heat exchanger, and is beneficial to improving the heat exchange performance of the plate heat exchanger.
The embodiment of the application provides a plate heat exchanger, which comprises a plate, a first inter-plate channel and a second inter-plate channel, wherein the plate comprises a plurality of first plates and second plates which are stacked;
the two sides of the first plate form a first heat exchange surface and a second heat exchange surface, the first plate comprises a first flat plate part and a first heat exchange matching part, the first heat exchange matching part protrudes out of the first flat plate part on the first heat exchange surface, the first heat exchange matching part forms a concave part on the second heat exchange surface, and a first concave area is formed between the adjacent first heat exchange matching parts relative to the top of the first heat exchange matching part;
a third heat exchange surface and a fourth heat exchange surface are formed on two sides of the second plate, the second plate comprises a second flat plate part and a second heat exchange matching part, the second heat exchange matching part protrudes out of the second flat plate part on the third heat exchange surface, a concave part is formed on the fourth heat exchange surface by the second heat exchange matching part, and a second concave area is formed between the adjacent second heat exchange matching parts relative to the top of the second heat exchange matching part;
the first inter-plate channel is located between a first heat exchange surface of the first plate and a third heat exchange surface of the second plate, and the second inter-plate channel is located between a second heat exchange surface of the first plate and a fourth heat exchange surface of the second plate; for the first plate and the second plate on two sides of the first plate passage, at least part of the second heat exchange matching part extends into the first recessed area and is opposite to the first flat plate part of the first plate, and at least part of the first heat exchange matching part extends into the second recessed area and is opposite to the second flat plate part of the second plate.
This application is through improving plate heat exchanger's structure, and to first slab and the second slab of first inter-plate channel both sides, the at least part of second heat transfer cooperation portion stretches into first depressed area and is relative with the first flat board portion of first slab, and the at least part of first heat transfer cooperation portion stretches into second depressed area and is relative with the second flat board portion of second slab. The first heat exchange matching part is of a convex structure facing the first inter-plate channels relative to the first flat plate part, the second heat exchange matching part is of a convex structure facing the first inter-plate channels relative to the second flat plate part, the circulation area of the first inter-plate channels is restrained by the two convex structures, the depth of the circulation section of the first inter-plate channels can be reduced, a more compact and compact flow channel structure is favorably formed in the space of the first inter-plate channels of the plate heat exchanger, particularly, a fluid with higher requirement on channel pressure drop for a refrigerant is favorably improved, the heat exchange coefficient of a refrigerant side is favorably improved, relatively, for the second inter-plate channels, the first heat exchange matching part is of a concave structure far away from the second inter-plate channels relative to the first flat plate part, the second heat exchange matching part is of a concave structure far away from the second inter-plate channels relative to the second flat plate part, and the space of the second inter-plate channels of the plate heat, the fluid mixing effect of the secondary refrigerant side is enhanced, and the assembly structure of the first plate and the second plate is beneficial to improving the overall heat exchange performance of the plate heat exchanger.
Drawings
FIG. 1 is a schematic view of a portion of a panel as described in the background of the invention;
FIG. 2 is a schematic cross-sectional view of a plate heat exchanger according to the present invention;
FIG. 3 is a schematic structural view of a unit heat transfer area on a first plate of the plate heat exchanger according to the present invention;
FIG. 4 is a schematic structural view of a unit heat transfer area on a second plate of the plate heat exchanger according to the present invention;
FIG. 5 is a schematic diagram illustrating the channel effect of the unit heat transfer area structures of FIGS. 3 and 4 when assembled together according to the present invention;
FIG. 6 is a schematic cross-sectional view of the first heat exchanging engagement portion and the second heat exchanging engagement portion of FIG. 5 on the first heat exchanging surface according to the present invention;
FIG. 7 is a schematic cross-sectional view illustrating the first heat exchanging engagement portion and the second heat exchanging engagement portion of FIG. 5 on a third heat exchanging surface according to the present invention;
FIG. 8 is a schematic structural view of another unit heat transfer area on the second plate of the plate heat exchanger according to the present invention;
FIG. 9 is a schematic diagram illustrating the channel effect of the unit heat transfer area structures of FIGS. 2 and 8 when assembled together according to the present invention;
fig. 10 is a schematic structural view of another unit heat transfer area on the first plate of the plate heat exchanger according to the present invention;
FIG. 11 is a schematic structural view of another unit heat transfer area on the second plate of the plate heat exchanger according to the present invention;
FIG. 12 is a schematic diagram illustrating the channel effect of the unit heat transfer area structures of FIGS. 10 and 11 when assembled together according to the present invention;
fig. 13 is a schematic view of the main flow direction of the fluid of the plate heat exchanger and the direction of the unit heat exchange area according to the present invention.
Detailed Description
According to the plate heat exchanger provided by the invention, by optimizing the assembly structure between the plates of the plate heat exchanger, a more compact and compact flow channel structure is favorably formed in the space on one side of the plates of the plate heat exchanger, the heat exchange performance of the plate heat exchanger is favorably improved, the corresponding refrigerant charge amount is reduced, and the channel strength is enhanced. 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.
The invention as shown in fig. 2 provides a schematic structural view of a plate heat exchanger 100, which comprises a plate, a first plate-to-plate channel 3 and a second plate-to-plate channel 4, wherein the plate comprises a plurality of first plates 1 and second plates 2 which are arranged in a stacked manner. The first plate 1 and the second plate 2 are alternately arranged to form a heat exchange core of the plate heat exchanger 100, and the edge portions of the first plate 1 and the second plate 2 can be sealed and assembled and positioned by brazing or the like. The plate heat exchanger 100 shown in fig. 2 is only illustrated with three first plates 1 and three second plates 2, and a practical plate heat exchanger may comprise a larger number of layers of first plates 1 and second plates 2.
The first plate 1 comprises a first flat plate part 101, a first heat exchange surface 11 and a second heat exchange surface 12 are formed on two sides of the first plate 1, the first plate 1 comprises a first heat exchange matching part 13, the first heat exchange matching part 13 protrudes out of the first flat plate part 101 on the first heat exchange surface 11, and a concave part is formed on the second heat exchange surface 12 side by the first heat exchange matching part 13. The second plate 2 comprises a second flat plate part 201, a third heat exchange surface 21 and a fourth heat exchange surface 22 are formed on two sides of the second plate 2, the second plate 2 comprises a second heat exchange matching part 23, the second heat exchange matching part 23 protrudes out of the second flat plate part 201 on the third heat exchange surface 21, and a concave part is formed on the fourth heat exchange surface by the second heat exchange matching part 23. The first and second heat exchanging mating parts 13 and 23 may be obtained by pressing or stamping techniques.
The first plate-to-plate channel 3 is located between the first heat exchange surface 11 of the first plate 1 and the third heat exchange surface 21 of the second plate 2, and the second plate-to-plate channel 4 is located between the second heat exchange surface 12 of the first plate 1 and the fourth heat exchange surface 22 of the second plate 2. For the first plate sheet 1 and the second plate sheet 2 on both sides of the first plate passage 3, the first heat exchange surface 11 of the first plate sheet 1 is arranged opposite to the third heat exchange surface 21 of the second plate sheet 2, and the second heat exchange surface 12 of the first plate sheet 1 is arranged opposite to the fourth heat exchange surface 22 of the second plate sheet 2.
The second heat exchanging engagement portion 23 of the second plate 2 is convexly provided toward the first flat plate portion 101 of the first plate 1. Relative to the top of the first heat exchange matching parts 13, a first concave area 14 is formed between the adjacent first heat exchange matching parts 13 of the first plate 1, and at least part of the second heat exchange matching part 23 extends into the first concave area 14 and is opposite to the first flat plate part 101 of the first plate 1. The first heat exchange mating portion 13 of the first plate 1 is convexly provided toward the second flat plate portion 201 of the second plate 2. A second recessed area 24 is formed between two second heat exchange matching parts 23 of the second plate 2 relative to the top of the second heat exchange matching parts 23, and at least part of the first heat exchange matching part 13 extends into the second recessed area 24 and is opposite to the second flat plate part 201 of the second plate 2.
The first plate 1 and the second plate 2 may be plates with the same structure and size, and when assembling, for example, the first plate 1 may be assembled together after rotating 180 degrees relative to the second plate 2, of course, the first plate 1 and the second plate 2 may also be plates with different structures and sizes, and correspondingly, the first heat exchange matching part 13 and the second heat exchange matching part 23 may be the same structure or different structures. It should be understood that the plate heat exchanger 100 also comprises relatively flat edge plate structures at the top and bottom of the heat exchange core for retaining the fluids within the heat exchange core, and that, based on the assembly structure illustrated in fig. 2, the flow channel structures at both sides of each plate may be different, and correspondingly the flow characteristics of the two fluids involved may be different, so that the interplate passages of one fluid of the plate heat exchanger 100 may have a relatively high pressure resistance compared to the interplate passages of the other fluid. That is, by designing the size and distribution of the first heat exchange matching part 13 and the second heat exchange matching part 23, a specific flow rate and/or pressure drop can be designed for the flow channel, and meanwhile, the plate heat exchanger 100 can also design parameters such as the size according to the required strength.
Second heat transfer cooperation portion 23 is at least partly stretched into first sunk area 14, and first heat transfer cooperation portion 13 is at least partly stretched into second sunk area 24, and after first slab 1 and second slab 2 assemble, first heat transfer cooperation portion 13 and second heat transfer cooperation portion 23 adjacent setting, can separate through second heat transfer cooperation portion 23 between two adjacent first heat transfer cooperation portions 13, can separate through first heat transfer cooperation portion 13 between two adjacent second heat transfer cooperation portions 23. The heights of the first heat exchange fitting part 13 and the second heat exchange fitting part 23 may be the same or different, and correspondingly, the depths between the first recessed area 14 and the second recessed area 24 may be the same or different. When assembled, the first heat exchange fitting part 13 may be fixedly connected with the second flat plate part 201 through the top, and the second heat exchange fitting part 23 may be fixedly connected with the first flat plate part 101 through the top.
For the first plate 1 and the second plate 2, the fluid flowing on the plates may include various forms, such as flowing from a first side of the plates to an opposite second side, i.e., an I-loop flow (I-flow) mode, or flowing out from one corner hole of the first side of the plates, flowing to the opposite second side of the plates, turning back to another corner hole of the first side, i.e., a U-loop flow (U-flow) mode, and so on.
Referring to fig. 2, the height of the first heat exchange fitting 13 matches the depth of the second recessed area 24, and the top of the first heat exchange fitting 13 is welded to the second flat plate portion 201 in the second recessed area 24. The height of the second heat exchange matching part 23 is matched with the depth of the first concave area 14, and the top of the second heat exchange matching part 23 is welded and fixed with the first flat plate part 101 in the first concave area 14.
Between the side of the first heat exchanging cooperation 13 and the side of the second heat exchanging cooperation 23 there is a gap V, which constitutes a part of the first plate to plate channels 3.
For the first inter-plate channel 3 formed between the first heat exchange surface 11 of the first plate 1 and the third heat exchange surface 21 of the second plate 2, the first heat exchange surface 11 of the first plate 1 and the third heat exchange surface 21 of the second plate 2 are both provided with welding spots, and the improvement of the welding spot density effectively ensures the flow channel strength of the first inter-plate channel 3 and the overall strength of the plate heat exchanger 100, so that the plate heat exchanger 100 provided by the invention can be manufactured and processed by thinner plates under the condition of ensuring the same structural strength, and has the advantages in weight and cost.
Referring to fig. 3 and 4, in a plane perpendicular to the plate stacking direction, a projection of a top a1 of the first heat exchange matching part 13 is located within a projection range of a bottom B1 of the first heat exchange matching part 13, a projection area of a top a1 of the first heat exchange matching part 13 is smaller than or equal to a projection area of a bottom B1 of the first heat exchange matching part 13, a projection of a top a2 of the second heat exchange matching part 23 is located within a projection range of a bottom B2 of the second heat exchange matching part 23, and a projection area of a top a2 of the second heat exchange matching part 23 is smaller than or equal to a projection area of a bottom B2 of the second heat exchange matching part 23.
One feasible scheme is that the side of the first heat exchange matching part 13 and the side of the second heat exchange matching part 23 both have an edge angle of about 45 degrees, the size of the top a1 of the first heat exchange matching part 13 is smaller than the size of the bottom B1 of the first heat exchange matching part 13, the size of the top a2 of the second heat exchange matching part 23 is smaller than the size of the bottom B2 of the second heat exchange matching part 23, and the cross sections of the first heat exchange matching part 13 and the second heat exchange matching part 23 are substantially trapezoidal along the plate stacking direction, so that the pressing or stamping processing is facilitated.
Of course, the top a1 of first heat exchanging fitting 13 may also be approximately the same size as the bottom B1, and the top a2 of second heat exchanging fitting 23 may also be approximately the same size as the bottom B2 of second heat exchanging fitting 23.
The top of the first heat exchanging fitting part 13 and the top of the second heat exchanging fitting part 23 are both provided with a flat portion for facilitating welding or a slightly curved portion that is approximately flat and meets the requirements of assembly and brazing, which will be collectively described below in a "flat" manner, wherein the top a1 of the first heat exchanging fitting part 13 may be entirely flat and is illustrated in a hatched closed shape in fig. 3, or may be partly flat, and the top a2 of the second heat exchanging fitting part 23 may be entirely flat and is illustrated in a hatched closed shape in fig. 4, or may be partly flat.
Referring to fig. 3 to 12, at least partial regions of the first heat exchange surface 11 of the first plate 1 and at least partial regions of the third heat exchange surface 21 of the second plate 2 both include unit heat exchange regions (S1, S2) which are uniformly distributed, the unit heat exchange region S1 has the same size as the unit heat exchange region S2, and the unit heat exchange regions (S1, S2) are substantially diamond-shaped or rectangular-shaped in a plane perpendicular to the plate stacking direction, in the illustration of fig. 3 to 12, the unit heat exchange regions (S1, S2) are illustrated in a diamond shape, wherein the unit heat exchange region S1 on the first heat exchange surface 11 is assembled corresponding to the unit heat exchange region S2 on the third heat exchange surface 21.
As for the unit heat exchange areas S1 on the first heat exchange surface 11, the first heat exchange fitting parts 13 are arranged substantially along the sides of the diamond or rectangular shape. For the unit heat transfer areas S2 on the third heat exchange surface 21, the second heat exchange fitting part 21 is arranged substantially at the center of the diamond or rectangular shape, or the second heat exchange fitting part 21 is arranged substantially at the center and at least one vertex of the diamond or rectangular shape.
Specifically, referring to fig. 3, for each unit heat transfer area S1 of the first heat exchange surface 11, the unit heat transfer area S1 is illustrated in a diamond shape, and the first heat exchange fitting part 13 includes four first sub-parts 131. The four first sub-portions 131 are respectively arranged on four sides of the diamond shape. The first sub-portion 131 arranged on each side has a projection of an elongated shape along the side in a plane perpendicular to the sheet stacking direction. The cross section of the first sub-portions 131 in the plane perpendicular to the stacking direction of the plates may be an elongated ellipse-like shape, or an elongated rectangle and an irregular elongated shape, and adjacent first sub-portions 131 are spaced at each vertex (X1, X2, X3, X4) of the diamond shape, so that an effective fluid area through which fluid can pass, i.e., an inlet or an outlet at a corresponding position, is formed between the ends of two adjacent first sub-portions 131 near the vertex (X1, X2, X3, X4) of the diamond shape.
Referring to fig. 4, for each unit heat exchange area S2 of the third heat exchange surface 21, correspondingly, the unit heat exchange area S2 is also indicated by a diamond shape according to the schematic shape of the unit heat exchange area S1, and the second heat exchange fitting part 23 includes a second sub-part 231, and the second sub-part 231 is arranged at the center of the diamond shape. The cross-section of the second sub-portion 231 in a plane perpendicular to the stacking direction of the plates may be polygonal, such as the shape illustrated in fig. 4, or rhombus, such as the shape illustrated in fig. 11, or may be oval, circular, rectangular, or other regular or irregular patterns.
For the diamond-shaped unit heat exchange regions (S1, S2), in a case where the substantially main flow direction of the fluid is from the vertex X3 to the vertex X1, when the plates are assembled together, the fluid may flow into the portion between the unit heat exchange region S1 and the unit heat exchange region S2 from the opening at the vertex X3 and flow out of the portion between the unit heat exchange region S1 and the unit heat exchange region S2 from the opening at the other vertex X1, of course, the fluid may also flow out of the portion between the unit heat exchange region S1 and the unit heat exchange region S2 from the opening at the vertex X2 or the opening at the vertex X4.
Referring to fig. 5, 6 and 7, fig. 5 illustrates the channel effect when the first plate 1 and the second plate 2 are assembled together, fig. 5 illustrates the general flowing direction of the fluid with black solid lines with arrows, fig. 6 illustrates the sectional effect of the first heat exchange matching part 13 and the second heat exchange matching part 23 on the first heat exchange surface 11 after the first plate 1 and the second plate 2 are assembled, and fig. 7 illustrates the sectional effect of the first heat exchange matching part 13 and the second heat exchange matching part 23 on the third heat exchange surface 21 after the first plate 1 and the second plate 2 are assembled.
For the unit heat exchange area S1 on the first heat exchange surface 11, the length of the projection of the second sub-portion 231 in the direction perpendicular to the line connecting the center of the diamond shape to one of the vertices, which is indicated by the vertex X1, is denoted as a first distance L1, the distance between the openings of two adjacent first sub-portions 131 close to the vertex X1 is denoted as a second distance L2, and the first distance L1 is greater than the second distance L2.
For the unit heat exchange area S2 on the third heat exchange surface 21, the length of the projection of the second sub-portion 231 in the direction perpendicular to the line connecting the center of the diamond shape to the vertex indicated by the vertex X1 is denoted as a third distance L3, the distance between the openings of two adjacent first sub-portions 131 close to the vertex X1 is denoted as a fourth distance L4, and the third distance L3 is greater than the fourth distance L4.
After the first plate 1 and the second plate 2 are assembled, in accordance with the length setting relationship of the first distance L1, the second distance L2, the third distance L3 and the fourth distance L4, a "light-tight" channel structure is formed in the main flow direction of the fluid, when the fluid flows in the part between the unit heat exchange region S1 and the unit heat exchange region S2, a second heat exchange fitting portion arranged at the center position of the region between the unit heat exchange regions (S1, S2) is required to be bypassed between the inlet and the outlet, the fluid flow diagrams of the black curved curve a, curve b and curve c in fig. 6 and the fluid flow path diagrams of the black curved curve d, curve e and curve f in fig. 7 can be referred to, and the "light-tight" channel structure is favorable for avoiding the fluid from flowing in the part between the unit heat exchange region S1 and the unit heat exchange region S2, selecting the shortest path to flow directly from the inlet to the outlet, according to the invention, the fluid flows along the zigzag path between the first heat exchange surface 11 and the third heat exchange surface 21, particularly for the refrigerant, the zigzag flow path can effectively improve the heat exchange coefficient of the refrigerant side, so that the refrigerant side has a longer path, especially the boiling heat exchange and condensation heat exchange processes under a two-phase flow state, and a better heat exchange enhancement effect is generated.
On the basis of fig. 4, referring to fig. 8 and 9, schematically, in each unit heat exchange area S2, in addition to the second sub-portion 231, the second heat exchange fitting portion 23 further includes four third sub-portions 232, and the four third sub-portions 232 are respectively arranged at four vertices (X1, X2, X3, X4) of a diamond shape.
The projected area of the third sub-portion 232 is smaller than the projected area of the second sub-portion 231 in a plane perpendicular to the sheet stacking direction. The third sub-portion 232 may increase the disturbance effect of the fluid at the vertex position between the unit heat transfer areas (S1, S2) to further improve the heat transfer coefficient of the fluid, and the cross section of the third sub-portion 232 in the plane perpendicular to the lamination direction of the plates may be circular, elliptical, rhombic, and various regular or irregular shapes.
For each vertex of the rhomboid shape (X1, X2, X3, X4), there is a gap between the side of the third sub-portion 232 and the sides of the two first sub-portions 131 close to each vertex (X1, X2, X3, X4), illustrated with the third sub-portion 232 disposed at vertex X1, at vertex X1. The gap may be such that the third sub-portion 232 and the ends of the two first sub-portions 131 near the apex X1 form an opening therebetween through which fluid can pass.
As described with reference to fig. 10, 11 and 12, unlike the structure illustrated in fig. 3, the first heat exchange engagement part 13 includes the fourth sub-part 132 and the fifth sub-part 133, also for the unit heat transfer areas S1 on the first heat exchange surface 11, the unit heat transfer areas S1 are illustrated in the shape of a diamond, the fourth sub-sections 132 are arranged on two adjacent sides of the diamond shape, e.g., m1, m2, the fifth sub-portion 133 is disposed on two other adjacent sides of the diamond shape, e.g., m3, m4, for the fourth sub-portion 132, the fourth sub-portion 132 and the adjacent fifth sub-portion 133 on one side are spaced apart from each other with respect to a group of opposite vertices (X1, X3) of the diamond shape, so that openings through which fluid can pass are respectively formed between two ends (a1, a2) of the fourth sub-portion 132 close to the group of opposite vertices (X1, X3) and two ends (b1, b2) of the fifth sub-portion 133 close to the group of opposite vertices (X1, X3). The fourth sub-portion 132 and the other side-adjacent fifth sub-portion 133 are spaced apart with respect to the apex of the diamond shape.
Taking the unit heat exchanging area S11 as an example, the end a1 of the fourth sub-portion 132 corresponds to the end b1 of the fifth sub-portion 133, and an opening N1 is formed between the end a1 of the fourth sub-portion 132 and the end b1 of the fifth sub-portion 133 at an interval. The end a2 of the fourth sub-portion 132 corresponds to the end b2 of the fifth sub-portion 133, the end a2 of the fourth sub-portion 132 is spaced from the end b2 of the fifth sub-portion 133 to form an opening N2, and when the main flow direction of the fluid is from the opening N2 to the opening N1, the opening N2 can be used as a fluid inlet and the opening N1 can be used as a fluid outlet.
Taking the unit heat exchanging area S12 as an example, the end a3 of the fourth sub-portion 132 and the end b3 of the fifth sub-portion are located at two sides of the vertex X1, and an opening with an opening located at the vertex X1 is formed between the end a3 of the fourth sub-portion 132 and the end b3 of the fifth sub-portion 133 at an interval, and the opening can be used as an inlet or an outlet of the fluid. Similarly, the end a3 of the fourth sub-portion 132 and the end b3 of the fifth sub-portion are located at two sides of the vertex X3, and an opening is formed between the end a3 of the fourth sub-portion 132 and the end b3 of the fifth sub-portion 133 at the vertex X3, and the opening can be used as an inlet or an outlet of the fluid. Correspondingly, at the vertex X2, an opening N3 is formed at a distance between the end b2 of the fifth sub-portion 132 and the end b1 of the fifth sub-portion, and the opening may serve as an inlet or an outlet for the fluid, and at the vertex X4, an opening N4 is formed at a distance between the end a2 of the fourth sub-portion 132 and the end a1 of the fourth sub-portion, and the opening N4 may serve as an inlet or an outlet for the fluid.
Two openings are provided for a unit heat transfer region similar to the unit heat transfer region S11, and four openings are provided for a unit heat transfer region similar to the unit heat transfer region S12.
For the unit heat transfer areas S2 on the second heat exchange surface 21, the second heat exchange fitting part 23 is arranged at the center of the rhombus shape, or the second heat exchange fitting part 23 is arranged at the center of the rhombus shape and at least one vertex.
Fig. 12 illustrates the channel effect when the first plate 1 and the second plate 2 are assembled together, and the curved black solid line in the figure illustrates one general flowing direction of the fluid, and the flowing path of the fluid is relatively tortuous, which is beneficial to improving the heat exchange coefficient of the fluid in the channel, and further beneficial to improving the heat exchange effect of the plate heat exchanger.
Referring to fig. 13, the unit heat transfer regions (S1, S2) are substantially rhomboid in shape in a plane perpendicular to the sheet stacking direction, and the direction of a line connecting the apexes of a set of obtuse angles of the rhomboid shape is substantially parallel to the longitudinal direction of the plate heat exchanger 100. In one aspect, the four corners of the first plate 1 and the second plate 2 are provided with corner holes, and when fluid flows between the plates, the fluid can enter from the corner holes on one side of the plates and flow out from the corner holes on the other side of the plates along the length direction of the plate heat exchanger 100, so that the flow direction of the fluid in the unit heat exchange areas (S1, S2) is substantially the same as the main flow direction of the fluid, for example, the main flow direction of the fluid is indicated by black arrows in 12, and a group of obtuse angles in the shape of a rhombus of the unit heat exchange areas (S1, S2) are used as main inlets and outlets of the fluid, thereby facilitating uniform distribution of the fluid in the width direction of the plate heat exchanger 100 and facilitating improvement of the heat exchange performance of the plate heat.
Of course, the direction of the connecting line of the vertices of the group of acute angles of the diamond shape is substantially parallel to the length direction of the plate heat exchanger 100, which also achieves the "opaque" effect, but the invention is not limited thereto.
Referring to fig. 2, on the basis of the above solution, the plate heat exchanger 100 further includes a fin plate 501, and the fin plate 501 is disposed between the second heat exchange surface 12 of the first plate 1 and the fourth heat exchange surface 22 of the second plate 2, where the fin plate 501 is only partially illustrated in fig. 2. The fin plate 501 is welded and fixed with at least one of the second heat exchange surface 12 of the first plate 1 and the fourth heat exchange surface 22 of the second plate 2.
For the second interplate channel 4 formed between the second heat exchange surface 12 of the first plate 1 and the fourth heat exchange surface 22 of the second plate 2, the second interplate channel 4 may circulate a second fluid different from the first fluid in the first interplate channel 3, the fin plate 501 may enhance the heat exchange area of the second fluid, and the fin plate 501 cooperates with various groove structures of the second interplate channel 4 to enhance the mixing between fluids, so as to further improve the heat exchange performance of the plate heat exchanger 100. In addition, in the second interplate channels 4, besides the channel structure of the fin plate 501, corrugated plates, point wave plates, filiform fillers, porous media and the like can be adopted, and on the premise that the strength of the second interplate channels is structurally met, the modes also enhance the effects of turbulence, mixing, heat exchange area increase and the like of fluid in the second interplate channels, and finally realize enhanced heat exchange and improve the performance of the plate heat exchanger product.
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 (10)
1. A plate heat exchanger comprises a plate, a first plate-to-plate channel and a second plate-to-plate channel, wherein the plate comprises a plurality of first plates and second plates which are arranged in a stacked mode;
the two sides of the first plate form a first heat exchange surface and a second heat exchange surface, the first plate comprises a first flat plate part and a first heat exchange matching part, the first heat exchange matching part protrudes out of the first flat plate part on the first heat exchange surface, the first heat exchange matching part forms a concave part on the second heat exchange surface, and a first concave area is formed between the adjacent first heat exchange matching parts relative to the top of the first heat exchange matching part;
a third heat exchange surface and a fourth heat exchange surface are formed on two sides of the second plate, the second plate comprises a second flat plate part and a second heat exchange matching part, the second heat exchange matching part protrudes out of the second flat plate part on the third heat exchange surface, a concave part is formed on the fourth heat exchange surface by the second heat exchange matching part, and a second concave area is formed between the adjacent second heat exchange matching parts relative to the top of the second heat exchange matching part;
the first inter-plate channel is located between a first heat exchange surface of the first plate and a third heat exchange surface of the second plate, and the second inter-plate channel is located between a second heat exchange surface of the first plate and a fourth heat exchange surface of the second plate; for the first plate and the second plate on two sides of the first plate passage, at least part of the second heat exchange matching part extends into the first recessed area and is opposite to the first flat plate part of the first plate, and at least part of the first heat exchange matching part extends into the second recessed area and is opposite to the second flat plate part of the second plate.
2. The plate heat exchanger of claim 1, wherein the height of the first heat exchange mating portion matches the depth of the second recessed area, and the top of the first heat exchange mating portion is welded to the second flat plate portion in the second recessed area;
the height of the second heat exchange matching part is matched with the depth of the first concave area, and the top of the second heat exchange matching part is welded and fixed with the first flat plate part in the first concave area;
and a gap is formed between the side part of the first heat exchange matching part and the side part of the second heat exchange matching part.
3. The plate heat exchanger according to claim 1 or 2, wherein in a plane perpendicular to the plate stacking direction, a projection of a top of the first heat exchange fitting portion is located within a projection range of a bottom of the first heat exchange fitting portion, and a projection of a top of the second heat exchange fitting portion is located within a projection range of a bottom of the second heat exchange fitting portion; the top of first heat transfer cooperation portion with the top of second heat transfer cooperation portion all is equipped with the plane or the little curved surface of being convenient for weld.
4. A plate heat exchanger according to any one of claims 1-3, wherein at least part of the area of the first heat exchange surface of the first plate and at least part of the area of the third heat exchange surface of the second plate comprise uniformly distributed unit heat exchange areas, and the unit heat exchange areas are substantially rhombus or rectangular in a plane perpendicular to the stacking direction of the plates;
for the unit heat exchange area on the first heat exchange surface, the first heat exchange matching part is arranged along the edge of the rhombus or the rectangular shape; for the unit heat exchange area on the third heat exchange surface, the second heat exchange matching part is arranged at the center of the diamond shape or the rectangular shape, or the second heat exchange matching part is arranged at the center and at least one vertex of the diamond shape or the rectangular shape;
and the unit heat exchange area on the first heat exchange surface is assembled corresponding to the unit heat exchange area on the third heat exchange surface.
5. A plate heat exchanger according to claim 4, wherein the first heat exchanging engagement portion comprises four first sub-portions for each of the unit heat exchanging areas of the first heat exchanging surface; the four first sub-portions are respectively arranged on four sides of the rhombus or the rectangular shape; the first sub-portion arranged on each side has, in a plane perpendicular to the sheet stacking direction, a projection of an elongated shape along the side; and adjacent first sub-portions are spaced apart at the vertices of the diamond or rectangular shape.
6. A plate heat exchanger according to claim 5, wherein the second heat exchanging engagement comprises, for each of the unit heat exchanging areas of the third heat exchanging surface, a second sub-portion arranged in the center of the rhombus or rectangular shape;
for the unit heat exchange area on the first heat exchange surface, the length of the projection of the second sub-portion in the direction perpendicular to the connecting line between the center of the rhombic or rectangular shape and a vertex is recorded as a first distance, the distance between the openings of two adjacent first sub-portions close to the vertex is recorded as a second distance, and the first distance is greater than the second distance;
for the unit heat exchange area on the third heat exchange surface, the length of the projection of the second sub-portion in the direction perpendicular to the connecting line between the center of the diamond or rectangular shape and a vertex is recorded as a third distance, the distance between the openings of two adjacent first sub-portions close to the vertex is recorded as a fourth distance, and the third distance is greater than the fourth distance.
7. A plate heat exchanger according to claim 6, wherein the second heat exchanging engagement portion further comprises, for each of the unit heat exchanging areas of the third heat exchanging surface, four third sub-portions arranged at four vertices of the rhombus or rectangular shape, respectively;
the projection area of the third sub-portion is smaller than that of the second sub-portion on a plane perpendicular to the plate stacking direction.
8. A plate heat exchanger according to claim 5, wherein the first heat exchanging engagement portion comprises a fourth subsection arranged on two adjacent sides of the rhombus or rectangular shape for the unit heat exchanging zones on the first heat exchanging surface and a fifth subsection arranged on the other two of the four sides of the rhombus or rectangular shape, wherein the fifth subsection adjacent to one side is spaced apart relative to a set of opposing vertices of the rhombus or rectangular shape for the fourth subsection and the fifth subsection adjacent to the other side is spaced apart relative to the vertices of the rhombus or rectangular shape;
for the unit heat exchange area on the second heat exchange surface, the second heat exchange matching part is arranged at the center of the diamond shape or the rectangular shape, or the second heat exchange matching part is arranged at the center of the diamond shape or the rectangular shape and at least one vertex.
9. A plate heat exchanger according to any one of claims 4-8, wherein the unit heat exchange areas are substantially rhomboidal in shape in a plane perpendicular to the direction in which the plates are stacked, and the direction of the line connecting the vertices of a set of obtuse angles of the rhomboidal shape is substantially parallel to the length direction of the plate heat exchanger.
10. A plate heat exchanger according to claims 1-9, further comprising a fin plate arranged between the second heat exchange surface of the first plate and the fourth heat exchange surface of the second plate; the fin plate is welded and fixed with at least one of the second heat exchange surface of the first plate and the fourth heat exchange surface of the second plate.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910579121.9A CN112146484B (en) | 2019-06-28 | 2019-06-28 | Plate heat exchanger |
| PCT/CN2020/098332 WO2020259645A1 (en) | 2019-06-28 | 2020-06-26 | Plate heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910579121.9A CN112146484B (en) | 2019-06-28 | 2019-06-28 | Plate heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112146484A true CN112146484A (en) | 2020-12-29 |
| CN112146484B CN112146484B (en) | 2021-07-06 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910579121.9A Active CN112146484B (en) | 2019-06-28 | 2019-06-28 | Plate heat exchanger |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN112146484B (en) |
| WO (1) | WO2020259645A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023274375A1 (en) * | 2021-06-30 | 2023-01-05 | 浙江雪波蓝科技有限公司 | Heat exchanger and manufacturing method therefor |
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2020
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| CN1656351A (en) * | 2002-04-24 | 2005-08-17 | 达纳加拿大公司 | Inverted lid sealing plate for heat exchanger |
| CN101120223A (en) * | 2005-02-15 | 2008-02-06 | 阿尔法拉瓦尔股份有限公司 | Heat exchanger |
| CN206430609U (en) * | 2017-01-23 | 2017-08-22 | 江苏宝得换热设备有限公司 | Corrugated plate-type heat exchangers |
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| WO2023274375A1 (en) * | 2021-06-30 | 2023-01-05 | 浙江雪波蓝科技有限公司 | Heat exchanger and manufacturing method therefor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112146484B (en) | 2021-07-06 |
| WO2020259645A1 (en) | 2020-12-30 |
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