CN112414185B

CN112414185B - Plate heat exchanger

Info

Publication number: CN112414185B
Application number: CN202010982825.3A
Authority: CN
Inventors: 李华; 邵汉; 李永平; 郑希茹
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2020-09-17
Filing date: 2020-09-17
Publication date: 2022-06-21
Anticipated expiration: 2040-09-17
Also published as: CN112414185A

Abstract

The application discloses a plate heat exchanger, which comprises at least one fin plate and a plurality of plates; the fin plate is positioned between two adjacent plate sheets; the fin plate comprises a base part and a plurality of fin units arranged along a first direction; each fin unit comprises a plurality of first fins and a plurality of second fins; each fin comprises a top and two sides; at least one group of side parts on the top side of the first fin and side parts on the top side of the second fin are staggered in the second direction, so that a window is formed between two side parts of the group of side parts respectively belonging to the adjacent first fin and the second fin; at least one of the plurality of sheet bars is provided with a plurality of corrugated bulges, a groove is formed between every two adjacent corrugated bulges, and the opening of the groove faces to the side of the fin plate; the tops of the corrugated protrusions are at least partially in contact with the fin plate, and the windows communicate with the grooves. The plate heat exchanger of this application is favorable to reducing the pressure drop that flows when promoting heat transfer performance.

Description

Plate heat exchanger

Technical Field

The application relates to the technical field of heat exchange, in particular to a plate heat exchanger.

Background

The plate heat exchanger in the related art includes a plate, a fin, and the like. The fins are usually positioned between two adjacent plates, and the fins are arranged in a flow channel formed by the plates, or the side gravity flow resistance is low, or the side gravity heat exchange performance is good, and usually balance or include two technical effects of low flow resistance and good heat exchange.

As shown in fig. 22, some techniques employ a fin structure disposed in the fluid flowing direction to disturb and block the fluid, so as to obtain a better heat exchange effect, but at the same time, the resistance of the fluid flowing through the flow channel is increased, and accordingly, a higher pumping work is required. In order to reduce the flow resistance, some techniques adopt a fin structure in a wave-shaped bent form, and the wave troughs of the wave-shaped fins are arranged in an extending manner along the fluid flow direction, so that the fluid can easily flow through channels formed by the wave troughs of the wave-shaped fins, the fluid flow resistance is small, and the heat exchange effect is poor.

Therefore, the related plate heat exchanger technology balances two technical indexes of heat exchange performance and fluid pressure drop, and for an application scenario with higher requirements on heat exchange performance and fluid pressure drop, the increase of the number of flow channels, the size of fins, the expansion of plate sizes and the like have to be considered, so that not only is the cost increased, but also the weight and the volume of a heat exchanger product are not facilitated, and therefore, the related technology still needs to be improved.

Disclosure of Invention

This application improves plate heat exchanger, can improve plate heat exchanger's heat transfer performance to be favorable to reducing the fluid pressure drop.

The embodiment of the application provides a plate heat exchanger, which comprises a plurality of plates and at least one fin plate;

the fin plate comprises a base part and a plurality of fin units arranged along a first direction; each fin unit comprises a plurality of fins protruding out of the base, and each fin comprises a top and two side parts; the two side parts are respectively positioned on two opposite sides of the top part, and the two side parts are connected between the top part and the base part;

the fins comprise a plurality of first fins and a plurality of second fins; the first fins and the second fins are alternately arranged along a second direction; the first direction and the second direction are not co-directional; for two side parts which are positioned on two opposite sides of the tops of the fins, at least one group of side parts positioned on one side of the tops of the first fins and side parts positioned on one side of the tops of the second fins are staggered in the second direction, and the side parts positioned on one side of the tops of the first fins and the side parts positioned on one side of the tops of the second fins are positioned on the same side of the tops of the corresponding fins, so that windows are formed between the two side parts of the group of side parts respectively belonging to the adjacent first fins and the second fins;

the plurality of plates comprise a first plate and a second plate, and the fin plate is positioned between the first plate and the second plate; at least one of the first plate and the second plate is provided with a plurality of corrugated bulges which are distributed along the length direction of the plate, and a groove is formed between every two adjacent corrugated bulges; the corrugated bulge comprises at least one extension section, and the extension section is obliquely arranged relative to the length direction of the plate sheet; wherein at least a portion of the crests of the corrugated protrusions are in contact with the bases of the fin plates or at least a portion of the crests of the fins, and the windows communicate with the grooves.

In the application, since at least one of the first plate sheet and the second plate sheet is provided with the corrugated bulges, and the top parts of the corrugated bulges are at least partially contacted with the base parts of the fin plates or at least partially contacted with the top parts of the fins, the window structures of the fin units are communicated with the grooves formed by the adjacent two corrugated bulges. The fin plate not only increases the contact area of the heat exchange wall surface of the plate heat exchanger product and fluid heat exchange, but also can influence the circulation and the heat exchange area of the fluid together by the cooperation of the corrugated bulges and the grooves of the fin plate and the plate, thus, the effective circulation sectional area of the fluid is enlarged while a more complex flow channel form is formed, the heat exchange effect close to the heat exchange wall surface is improved by the relatively complex channel turbulence form, and the heat transfer and transportation between the fluid and the heat exchange wall surface are also improved. Therefore, the novel flow channel structure constructed by the fin plates and the plate sheets has the technical effects of good heat exchange performance and low flow pressure drop.

Drawings

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

FIG. 2 is a schematic illustration of an exploded structure of a first sheet, fin plate and second sheet of the present application;

FIG. 3 is a bottom view of a portion of the plate structure of the present application;

FIG. 4 is a schematic illustration of another exploded structure of the first sheet, fin plate and second sheet of the present application;

FIG. 5 is a schematic structural view of a fin plate provided herein;

FIG. 6 is a schematic cross-sectional view of a portion of a fin structure of the fin plate of the present application;

FIG. 7 is a perspective view of a portion of the fin structure of the fin plate of the present application;

FIG. 8 is a schematic view of the fin plate of the present application in coordination with the direction of fluid flow;

FIG. 9 is a schematic top view of the fin plate of FIG. 8 of the present application in fluid engagement;

FIG. 10 is another schematic view of the fin plate of the present application in coordination with the direction of fluid flow;

FIG. 11 is a schematic view of yet another exploded structure of the first sheet, fin plate and second sheet of the present application;

FIG. 12 is a perspective cut-away view of the assembled plate assembly of FIG. 11;

FIG. 13 is an enlarged view of the plate assembly of FIG. 12;

FIG. 14 is a schematic view of yet another exploded structure of the first sheet, fin plate and second sheet of the present application;

FIG. 15 is another cross-sectional structural schematic view of the assembled plate assembly of the present application;

FIG. 16 is an enlarged view of a structure on the reverse side of a first plate of the present application;

FIG. 17 is an enlarged view of another embodiment of the present application on the reverse side of the first plate;

FIG. 18 is a schematic view of the assembly of the fin plate of the present application with a first asymmetric chevron plate;

FIG. 19 is a schematic view of the assembly of a fin plate of the present application with a second asymmetric chevron plate;

FIG. 20 is a schematic view of the assembled structure of the fin plate and a third asymmetric chevron plate of the present application;

fig. 21 is a schematic top view of two adjacent fin units corresponding to the fin plate of the present application;

fig. 22 is a schematic view of an assembly structure of a plate and a fin according to the related art of the present application.

Detailed Description

Referring to fig. 1, the present application provides a plate heat exchanger 10 comprising a plurality of plates and at least one fin plate 60, and in particular, the fin plate 60 may be secured between two plates by brazing. The plurality of plates include a first plate 101 and a second plate 102, and the number of the first plate 101 and the second plate 102 may be multiple. Of course, the plate heat exchanger 10 may also comprise other third, fourth, fifth etc. plates having a different structure than the first plate 101 and the second plate 102.

In some embodiments, referring to fig. 2, the fin sheet 60 is located between the reverse side 300 of the first sheet 101 and the front side 200 of the second sheet 102. The reverse side 300 of the plate, not shown in fig. 2, and with reference to the exploded view of fig. 4, the fin plate 60 may increase the heat exchange area of the fluid flowing between the reverse side 300 of the first plate 101 and the front side 200 of the second plate 102, thereby improving the heat exchange performance of the fluid. Referring to fig. 2, which illustrates an exploded view of a part-plate structure of a plate heat exchanger, wherein the first plate 101 is the plate in the uppermost position, the second plate 102 is the plate in the lowermost position, and the fin plate 60 is in the middle position. In fig. 2, the outward facing side of the first plate 101, i.e. the visible side, is defined as the front side 200, the inward facing side, i.e. the invisible side, is defined as the back side 300, and the same applies to the front side and the back side of the second plate 102. The front side 200 of a first plate 101 of the plate heat exchanger 10 may be located opposite the back side 300 of another second plate 102, as viewed from below in fig. 3, with the fin plate 60 being the most proximal in the bottom direction, followed by the first plate 101, then the second plate 102, and so on. The plates also include a flange structure formed on the outer edge of the plates, and when the plates are assembled, the flanges of the plates can be sealed by welding, such as brazing, so as to facilitate the retention of fluid in the flow channel formed between the plates.

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, for any one of the first plate 101 and the second plate 102, the plate includes corner hole distribution areas on both sides in the length direction and a main heat transfer 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. After the sheets are assembled, the plate portion around the first corner hole 21 of the first sheet 101 is in contact with the plate portion around the first corner hole 21 of the front surface 200 of the second sheet 102 at the back surface 300 of the first sheet 101, so that fluid cannot enter the inter-plate passage formed between the back surface 300 of the first sheet 101 and the front surface 200 of the second sheet 102 from the first corner hole 21 of the first sheet 101 and the first corner hole 21 of the second sheet 102. The plate portion around the second corner hole 22 of the first plate 101 has a gap in at least a partial region between the back surface 300 of the first plate 101 and the plate portion around the second corner hole 22 of the front surface 200 of the second plate 102. Thus, fluid may enter the interplate passages formed between the reverse side 300 of the first plate 101 and the front side 200 of the second plate 102 from the second corner hole 22 of the first plate 101 and the second corner hole 22 of the second plate 102. In this way, only one fluid can flow in the interplate channels, and after a plurality of such plate units are stacked, at least two fluid channels can be formed, and accordingly, two fluids such as refrigerant and coolant can exchange heat through the partition walls via the plates.

Referring to fig. 2, 3 and 4, the first plate 101 is used for illustrating that two first corner holes 21 and two second corner holes 22 of the first plate 101 are diagonally arranged, the fluid flow mode in such a corner hole layout mode can also be diagonal flow, referring to the illustration of fig. 4, the first fluid flowing on the reverse side 300 side of the first plate 101, the second corner holes 22 form the inlet and outlet of the first fluid, and the flow mode of the first fluid can refer to the illustration with black arrowed lines in fig. 4. Accordingly, the first corner holes 21 form the inlet and outlet of the second fluid flowing on the opposite side 300 of the second plate 102, and the second fluid also flows diagonally. Of course, in other embodiments, as shown in fig. 12, the two first corner holes 21 are located on the same side in the width direction W-W of the first plate 101, and the two second corner holes 22 are located on the other side in the width direction W-W of the first plate 101. In the angular hole layout mode, the flow mode of the fluid is a single-side flow, which can be illustrated with reference to the flow mode of the fluid with arrows.

In order to increase the heat exchange area of the fluid and the stability of the welded assembly of the plate heat exchanger, the surface area of the fin plate 60 may be enlarged as much as possible, and in some embodiments, as shown with reference to fig. 5, the fin plate 60 is provided with two first indentations 61 and two second indentations 62. The first notch 61 corresponds to the first corner hole 21 of each plate, and the second notch 62 corresponds to the second corner hole 22 of each plate. On a reference plane formed by the length direction and the width direction of the plate, the projection of the first corner hole 21 on the plane is positioned within the projection range of the first notch 61 on the plane, and the projection of the second corner hole 22 on the plane is positioned within the projection range of the second notch 62 on the plane. The first notch 61 may be slightly larger than the first corner hole 21 and the second notch 62 may be slightly larger than the second corner hole 22. The first notch 61 and the second notch 62 may have a circular, elliptical, or oblong profile shape. The first and

second indentations

61, 62 may all be the same shape and size.

Referring to fig. 5 and 6, the fin plate 60 includes a base 63 and a plurality of fin units 64 arranged in the first direction X. The fin unit 64 comprises a plurality of fins protruding from the base 63, the fins comprising a top 605, a first side 603 and a second side 604; the first side 603 and the second side 604 are located on opposite sides of the top 605, respectively, and the first side 603 and the second side 604 are connected between the top 605 and the base 63. The first side portion 603 and the second side portion 604 are inclined with respect to the height direction of the fin, which facilitates the manufacturing and provides a certain strength supporting structure to meet the requirement of product stability.

Referring to the schematic sectional structure of the partial fin in fig. 6 and the schematic enlarged structure of the partial fin illustrated in fig. 7, in each fin unit 64, the plurality of fins include a plurality of first fins 65 and a plurality of second fins 66, and the plurality of first fins 65 and the plurality of second fins 66 are alternately arranged along the second direction Y. The first direction X and the second direction Y are different directions, that is, the two directions are not in common, and the first direction X and the second direction Y are not coincident or parallel.

In the embodiments provided herein, the first direction X is perpendicular to the second direction Y. In the embodiment shown in fig. 2, the first direction X coincides with the longitudinal direction of the sheet, and the second direction Y coincides with the width direction of the sheet. I.e., the fluid flows over the fins, from side to side, also along the first direction X of the fin plate 60, i.e., its length. In some other embodiments, the first direction X also coincides with the width direction of the panel and the second direction Y coincides with the length direction of the panel. Corresponding to the assembly of the fin plate 60 of fig. 2 rotated 90 horizontally. The first direction X and the second direction Y may not be perpendicular, so that the fins in the fin unit 64 may be disposed obliquely with respect to the longitudinal direction of the plate, which is not limited in this application.

In the present embodiment, the first direction X of the fin plate 60 coincides with the longitudinal direction of the sheet, and the second direction Y coincides with the width direction of the sheet. In the second direction Y, two adjacent first fins 65 are respectively located on two opposite sides of the second fin 66 in the second direction Y, and two adjacent second fins 66 are respectively located on two opposite sides of the first fin 65 in the second direction Y. The first side 603 of the first fin 65 and the first side 603 of the second fin 66 are offset in the second direction Y with a first window 601 therebetween, and the second side 604 of the first fin 65 and the second side 604 of the second fin 66 are offset in the second direction Y with a second window 602 therebetween. Accordingly, the second side portion 604 of the first fin 65 and the first side portion 603 of the second fin 66 may be offset in the second direction Y and may form a window structure therebetween. Of course, the fin plate may have only the first windows 601 formed by the first sides 603 of the two fins being offset in the second direction Y, or only the second windows 602 formed by the second sides 604 of the two fins being offset in the second direction Y. That is, as for the two side portions located on the opposite sides of the fin top portion 605, at least one set of the side portion located on the side of the top portion 605 of the first fin 65 and the side portion located on the side of the top portion 605 of the second fin 66 is displaced in the second direction Y, and both the side portion located on the side of the top portion 605 of the first fin 65 and the side portion located on the side of the top portion 605 of the second fin 66 are located on the same side as the corresponding fin top portion 605, so that a window is formed between the two side portions belonging to the adjacent first fin 65 and second fin 66 among the set of side portions. The simple modification and replacement of the above-described window structure is not particularly limited in this application.

In some embodiments, after flipping the front and back sides of fin plate 60, fin plate 60 still has several identical fin units 64 as described above. That is, when the base portion 63 of the reversed front fin plate 60 becomes the tip portion 605 of the reversed rear fin, the tip portion 605 of the fin of the reversed front fin plate 60 becomes the base portion 63 of the reversed rear fin plate 60. The top 605 of the first fin 65 is flush with the top 605 of the second fin 66, and is partially connected therebetween.

Referring to fig. 8 and 9, when the first direction X coincides with the longitudinal direction of the plate and the second direction Y coincides with the width direction of the plate, black thick arrows indicate the flow direction of the fluid, and in fig. 9, for the sake of convenience of distinction, the two sides of the first fin 65 are a first side 603 and a second side 604, respectively, and the two sides of the second fin 66 are a first side 603 'and a second side 604', respectively. Describing the flow path of the fluid from bottom to top, the fluid is firstly blocked by the second side portion 604 of the first fin 65 to be divided during the flow process, and then continues to advance after being converged with other divided fluid through the second windows 602 on both sides of the second side portion 604, and the first side portion 603 of the first fin 65 and the second side portion 604' of the second fin 66 may have a gap in the direction along the first direction X and/or a gap in the direction along the second direction Y. Therefore, the fluid can flow to the first side portion 603 'of the second fin 66 through the gap after being blocked by the first side portion 603 of the first fin 65, then is blocked and divided by the first side portion 603', and then is converged with other fluid which is divided by the first side portion or the second side portion through the first window 601, so that the fluid is continuously blocked and divided by the fins, and is continuously converged with other fluid which is divided by the window. The fin structure of high vortex forms comparatively complicated runner structure, is favorable to improving fluidic heat transfer coefficient, promotes heat transfer performance.

Referring to fig. 10, in other embodiments, the first direction X may also coincide with a width direction of the plate, the second direction Y coincides with a length direction of the plate, and a thick black arrow indicates a flowing direction of the fluid, that is, the fluid may continuously flow forward through the first window 601 or the second window 602, and when the fluid passes through the first side portion 603 and the second side portion 604, the temperature of the wall surface near the surface of the side portion may be effectively swept, so as to enhance heat exchange, which also has a certain advantage in improving the heat exchange performance of the plate heat exchanger.

For the main heat exchange area of the plate between two corner hole distribution areas, at least one plate of the first plate 101 and the second plate 102 is provided with a plurality of corrugated bulges 41 arranged along the length direction of the plate, and a groove 31 is formed between two adjacent corrugated bulges 41.

The groove 31 is open toward the fin plate 60, wherein at least a part of the top of the corrugated protrusion 41 is in contact with the fin plate 60, specifically, the top of the corrugated protrusion 41 may be in contact with the fin top 605 of the fin plate 60 or the top of the corrugated protrusion 41 may be in contact with the base 63 of the fin plate 60. After the plate and fin are assembled, the first window 601 and the second window 602 of the fin plate 60 are both in communication with the groove 31. On one hand, in the assembled flow passage area, the fin plate 60 can increase the heat exchange area of the fluid, the fluid can be continuously dispersed and converged among a plurality of windows of the fin plate 60, the transmission and the transportation of heat between the fin and the fluid are enhanced through the impact and the friction between the fluid and the first side portion 603 and the second side portion 604 of the fin, and the heat exchange effect is further improved through the continuous damage and reconstruction of a fluid boundary layer. On the other hand, in the near-wall area of the plate, the grooves 31 and the fin tops 605 construct a relatively complex flow channel structure, which not only provides more wall heat exchange areas, but also is beneficial to the effect of the fluid and the wall, and finally improves the heat exchange performance of the whole flow channel. Meanwhile, as the fin plate 60 and the groove 31 are both provided with corresponding flowing spaces, compared with the related art, the flow channel space of the plate heat exchanger after being integrally assembled is larger, the corresponding fluid flowing speed is lower, and the guarantee is provided for the fluid to pass through the flow channel with the complex geometry by lower pressure drop. Finally, the technical effect of remarkably reducing the flow pressure drop while ensuring the heat exchange performance is achieved. It will be appreciated that the corrugated protrusions 41 and the grooves 31 are relative concepts, with the corrugated protrusions 41 protruding from the bottom of the grooves 31 on one side of the sheet, and the grooves 31 becoming a convex structure on the other side of the sheet, and the corrugated protrusions 41 becoming a grooved structure. Namely, the plate has two structural forms of a bulge and a groove on either the front side or the back side of the plate. As illustrated in fig. 4, on the opposite side of the first plate 101, the notches of the grooves 31 are arranged toward the fin plate 60, and accordingly, the corrugated protrusions 41 are protruded toward the side of the fin plate 60 with respect to the groove bottoms of the grooves 31.

For a plate provided with a corrugated protrusion 41 structure, the corrugated protrusion 41 includes at least one extension 411, and the extension 411 may have a linear extension direction or an extension direction with a smaller curvature and an arc shape. The extension 411 is inclined with respect to the longitudinal direction of the plate. In some embodiments, the corrugated protrusion 41 may have only one extension 31, the extension 31 may extend from one side edge to the other side edge of the panel, or the ratio of the one extension 411 in the width direction of the panel is greater than or equal to 1/2 of the panel width. The extending sections 411 of the two adjacent sheets are inclined toward different sides in the sheet width direction, and the angles at which the extending sections 411 of the two adjacent sheets are inclined with respect to the longitudinal direction of the sheet may be the same or different. For example, the angle β between the extension 411 of one sheet and the length of the sheet 101 is 30 °, and the angle β between the extension 411 of the other sheet and the length of the sheet 101 is 60 °.

In some embodiments, the number of the extending sections 411 of the corrugated protrusion 41 is greater than or equal to 2, and two adjacent extending sections 411 are respectively inclined to both sides of the width direction of the plate 101 with respect to the length direction of the plate. The corrugated protrusion 41 further includes a connecting section 412 connected to the extending direction end of the two adjacent extending sections 411, and the two adjacent extending sections 412 are rounded and transited by the connecting section 412. Such a form of the corrugated protrusion 41 may be referred to as a wave form of a so-called letter, and the corrugated protrusion 41 may extend in a continuous form from one side edge to the other side edge in the width direction of the sheet. The chevron structure formed by the corrugated projections 41 may thus have a plurality of periods in the width direction of the plate, thereby forming a continuous multiple of chevrons. It is emphasized that the technical advantages of the multiple chevron waves described above. On one hand, as mentioned above, the multiple herringbone wave structure not only increases the heat exchange area near the wall, but also establishes an effective heat exchange strengthening mechanism with the fins. On the other hand, as shown in fig. 2 and 11, the multiple chevron waves establish communication grooves 31 which penetrate through the width of the whole plate surface at a short length distance along the length direction of the plate, so that the flow adjustment of the fluid at a short length along the width direction can be realized. This arrangement is very advantageous for achieving an even distribution in the surface of the fluid plates in the plate heat exchanger. In addition, in the flow channel without the fins, the multiple herringbone wave structure can realize effective heat exchange enhancement effect on the fluid in a turbulent flow mode or even a transition flow mode. Thus, the integral plate heat exchanger product takes a laminar flow form or a transition form as a dominant flow form, and adopts the mode that the multiple herringbone wave flow-through plates are matched with the fin plates. And on the other side which takes the turbulent flow form as the leading side, a finless runner form with multiple herringbone waves and multiple herringbone waves matched is adopted, and the effective heat exchange enhancement effect is also realized. Finally, the product form has good cost performance. The technical characteristics form good technical effects under the application scenes of large difference of fluid or flow forms on two sides, such as an oil cooler, an evaporator, a condenser and the like. The technical features will be further described in connection with the scenario below.

In some embodiments, the first plate 101 and the second plate 102 are multiple in number, and the front side of the first plate 101 is opposite to the back side of the second plate 102, that is, the fin plate 60 is located on the back side of the first plate 101, and the second plate 102 is located on the front side of the first plate 101.

The first plate 101 and the second plate 102 may each be a plate of a chevron structure provided with a number of corrugated protrusions 41. When the first plate 101 and the second plate 102 form an assembling relationship, the convex structure of the first plate 101 facing the reverse side of the second plate 102 has a herringbone wave form, and the convex structure of the second plate 102 facing the front side of the first plate 101 also has a herringbone wave form, and the assembling mode of the herringbone wave to the herringbone wave can adopt an assembling mode of a sharp angle and a sharp angle in a reverse direction, so that fluid flows in a zigzag flow mode in a plate channel formed by the two plates, and the heat exchange effect of the plates is further improved.

Of course, one of the first plate 101 and the second plate 102, for example, the second plate 102, may also be a plate without a chevron structure, for example, the main heat exchange area of the second plate 102 may be a flat plate structure, or the main heat exchange area of the second plate 102 may be provided with a plurality of bump structures arranged at intervals, the cross section of the bump structure may have a circular shape, an oval shape, or another shape, and the bump structure may also be a triangular pyramid, a rectangular pyramid, or a hexagonal pyramid, and such a second plate 102 may be referred to as a point wave plate by those skilled in the art. Or the main heat exchange area of the second plate 102 is provided with a complex curved surface structure, for example, the surface of the main heat exchange area of the plate is provided with a plurality of concave parts and convex parts, adjacent concave parts are connected with each other in a curved surface transition way, and the bottom of the curved surface is higher than the bottom of the concave part, and so on.

In some embodiments, for the corrugated protrusion 41 of the first plate 101, the angle fitted by the extending directions of the two adjacent extending segments 411 is denoted as a first angle, and for the corrugated protrusion 41 of the second plate 102, the angle fitted by the extending directions of the two adjacent extending segments 411 is denoted as a second angle, where the first angle and the second angle may be the same. The first plate 101 and the second plate 102 may be plates made by molds of the same specification, and the first plate 101 is rotated 180 ° horizontally with respect to the second plate 102. Of course, the first angle and the second angle may be different. The value ranges of the first included angle and the second included angle may both be 40 ° to 165 °, for example: the first included angle is substantially a right angle of 90 deg., and the second included angle is substantially an obtuse angle of 120 deg.. In practice, the first included angle and the second included angle can be one of an acute angle, a right angle and an obtuse angle, different angle collocation can be selected under different application scenes, and two adjacent plates of the plate heat exchanger can be self-assembled at the same angle or can be mixed and assembled at different angles.

When the contained angle of the extending direction fit of two adjacent extending sections of the corrugated protrusion is an acute angle, the corrugated protrusion has more extending sections and connecting sections under the condition of limited plate width, namely, the number of herringbone periodic patterns formed by the corrugated protrusion is increased, so that the better heat exchange performance is ensured, the flowing trend of fluid along the groove direction is blocked by the connecting sections, the longitudinal flow along the length direction of the plate is switched, and the pressure drop is favorably reduced.

In the assembly illustrated in fig. 3 and 4, the front surface 200 of the first plate 101 and the back surface 300 of the second plate 102 are in direct contact without the fin plate 60 or other structure therebetween. In this way, a refrigerant-like fluid may flow between the front side 200 of the first plate 101 and the back side 300 of the second plate 102, while a coolant-like fluid may flow between the back side 300 of the first plate 101 and the front side 200 of the other second plate 102, and the heat exchange area of the coolant is increased by the fin plates 60. The back surface 300 of the first plate 101, the front surface 200 of the other second plate 102 and the fin plate 60 together form a flow channel of the coolant. Of course, the refrigerant and coolant flow paths could be reversed. And depending on different application scenarios or operating conditions, a fin plate 60 or other structures may be disposed between the front surface 200 of the first plate 101 and the back surface 300 of the second plate 102. The present application is not limited thereto.

The first sheet 101 and the second sheet 102 each comprise a base plate portion 20, and the base plate portion 20 may be flush with the bottom of the groove 31 of the corresponding sheet or the base plate portion 20 may also be flush with the top of the corrugated protrusion 41 of the corresponding sheet. It should be understood that the base plate portion 20 is difficult to ensure an absolute plane perpendicular to the lamination direction of the sheet plates during the sheet plate forming and punching process, but still has a certain flatness, so that the base plate portion 20 may have a substantially planar structure within a range of flatness allowed by design and manufacturing tolerances. When the first plate 101, the second plate 102 and the fin plate 60 of the plate heat exchanger are assembled in the assembly manner illustrated in fig. 12 and 13. The base plate portion 20 of the first plate piece 101 is disposed substantially flush with the tops of the corrugated protrusions 41. The first corner holes 21 of the first plate 101 are arranged in a sunken manner with respect to the base plate portion 20, the first corner holes 21 form sunken table holes, the second corner holes 22 may be arranged in a protruding manner with respect to the base plate portion 20, and the second corner holes 22 form raised table holes. In the case of the second plate 102, the base plate portion 20 is also disposed substantially flush with the top of the corrugated protrusion 41, the first corner hole 21 of the second plate 102 may be disposed protrudingly relative to the base plate portion 20, the first corner hole 21 forms a boss hole, the second corner hole 22 of the first plate 101 is disposed sunken relative to the base plate portion 20, and the second corner hole 22 forms a counter-boss hole. For any angle hole, in different assembling modes, the angle hole may be a boss hole provided on the boss, a counter sink hole provided on the counter sink structure, or a planar angle hole provided on the flat plate structure, which is not limited in this application.

When the first plate 101, the second plate 102 and the fin plate 60 of the plate heat exchanger are assembled in the assembly manner illustrated in fig. 14 and 15. The base plate portion 20 of the first plate piece 101 is disposed substantially flush with the tops of the corrugated protrusions 41. The first corner hole 21 of the first plate 101 is provided in the base plate portion 20, the first corner hole 21 forms a planar hole, the second corner hole 22 may be provided to protrude from the base plate portion 20, and the second corner hole 22 forms a boss hole. The base plate portion 20 of the second plate piece 102 is also disposed substantially flush with the bottom of the groove 31, the first corner hole 21 of the second plate piece 102 may be disposed to protrude from the base plate portion 20, the first corner hole 21 forms a boss hole, the second corner hole 22 of the first plate piece 101 is disposed on the base plate portion, and the second corner hole 22 forms a planar hole. The fin plate 60 is of a smaller size and the fin plate 60 can be fixed only between the main heat exchange areas of adjacent plates, so that the fin plate 60 has no structure such as a notch or the like which is matched with the corner hole of the plate. In the plate structure of the first plate 101 and the second plate 102 shown in fig. 16, taking the first plate 101 as an example, the first plate 101 has four extending sections 411, and an included angle fitted to the extending direction of two adjacent extending sections 411 is an obtuse angle, and the included angle may be an acute angle or a right angle in other manners. Fig. 16 is an enlarged schematic view of a part of the structure of the first plate 101 in fig. 15. The corrugated protrusions 41 are also in a groove-like structure on the front side (the side not visible in fig. 16) of the first plate 101, and accordingly, the cross section of the groove structure formed by the corrugated protrusions 41 on the front side (the side not visible in fig. 16) of the first plate 101 may be equal to the cross section area of the grooves 31 on the opposite side of the first plate 101. The corrugated protrusions 41 are arranged at a distance from each other along the length of the plate on the main heat transfer area of the first plate 101, and the pitch between the plurality of corrugated protrusions 41 may be equal or different.

The flow pattern of the fluid in the first plate 101 having the herringbone wave structure is decomposed into a slot-wise flow (currow flow) along the grooves 31 and a longitudinal flow (longitudinal flow) formed between the inlet and outlet of the first plate 101. By matching the first window 601 and the second window 602 of the fin plate 60, the fluid has a flow mode of dispersing and converging between the windows, and also has a flow along the groove direction of the groove and a longitudinal flow along the inlet and the outlet, and the multi-dimensional flow mode of the fluid increases the complexity of the flow mode of the fluid, so that the heat exchange coefficient of the fluid is higher, and the heat exchange performance and the heat exchange efficiency of the plate are relatively better. Meanwhile, the first plate 101 and the fin plate 60 are matched, so that the influence of high flow resistance of the fin plate on pressure drop can be effectively reduced.

Referring to fig. 17, the corrugated protrusion 41 is provided with a recess 413, the recess 413 is recessed from the top surface of the corrugated protrusion 41, at each extending section 411, the extending direction of the recess 413 is the same as the extending direction of the corrugated protrusion 41, and the depth of the bottom of the recess 413 relative to the top of the corrugated protrusion 41 is smaller than the depth of the bottom of the groove 31 relative to the top of the corrugated protrusion 41. Fig. 18 is a schematic cross-sectional view of the plate of fig. 17 taken along direction a-a, which is generally perpendicular through the extension 31. In the direction a-a, the reverse side 300 of the first plate 101 has a channel structure of "one deep and one shallow", and the front side 200 of the first plate 101 has a convex structure of "large and small protrusions". The recess 413 can increase the asymmetry degree of the plate, namely the groove channel volumes of herringbone waves on the front side and the back side of the plate are different, so that the fluid flowing on the front side and the back side of the plate can be suitable for application scenes with different pressure drop requirements.

Alternatively, the corrugated protrusion 41 may not be provided with the recess 413, and other structures may be adopted to realize the asymmetrical form. Referring to fig. 19, the groove 31 is provided with a convex rib 414, the convex rib 414 protrudes from the bottom of the groove 31 to the fin plate 60 side, and the convex rib 414 correspondingly forms a concave pit on the front surface 200 side of the first plate 101. The corrugated protrusion 41 adjacent to the ridge portion 414 is in parallel relation to the ridge portion 414 at each of the extending sections 411 thereof, and the height of the top of the ridge portion 414 with respect to the groove bottom of the groove 31 is smaller than the height of the top of the corrugated protrusion 41 with respect to the groove bottom of the groove 31.

Alternatively, the corrugated protrusion 41 may be provided with neither the concave portion 413 nor the convex portion 414, and other structures may be adopted to realize the asymmetric form. Referring to fig. 20, the corrugated protrusion 41 includes a top wall portion 415 and two side wall portions 416, the top wall portion 415 has a plane or a micro-curved surface for welding, the two side wall portions 416 are respectively located at two sides of the top wall portion 415 in the width direction, and the side wall portions 416 are connected between the top wall portion 415 and the bottom of the groove 31, at a certain extending section 411, the width direction of the top wall portion 415 of the corrugated protrusion 41 is substantially perpendicular to the extending direction of the extending section 411, and correspondingly, the width of the bottom of the groove 31 is substantially perpendicular to the extending direction of the extending section 411 adjacent thereto. The width-directional dimension L1 of the top wall portion 415 is not equal to the width-directional dimension L2 of the groove bottom of the groove 31. In fig. 20, the width-directional dimension L1 of the top wall portion 415 is smaller than the width-directional dimension L2 of the groove bottom of the groove 31. In this way, the volume of the channel structures on both sides of the first plate 101 can be made different, and an asymmetric channel structure can be realized.

As shown in fig. 21, in some embodiments, a plurality of fin units 64 are uniformly arranged on the fin plate 60 along the first direction X, the fin units 64 are periodically present along the base 63 along the first direction X, and two adjacent fin units 64 are separated by the base 63. Two adjacent fin units 64 are respectively marked as a first fin unit 671 and a second fin unit 672, the first fin unit 671 has a center line M1 along the second direction Y, the second fin unit 672 has a center line M2 along the second direction Y, the distance between the center line M1 of the first fin unit and the center line M2 of the second fin unit is marked as a first distance P, the height of the fin protruding relative to the base 63 is marked as a first height H, wherein the first distance P ranges from 1.0mm to 9.5mm and/or the ratio of the first distance P to the first height H ranges from 0.5 to 2.5. Overall, this has the advantage that better flow and heat exchange performance and channel strength will be obtained for the fluid channel formed by the plate corrugation lobes 41, the grooves 31 and the fin plates 60. On the one hand, as mentioned above, for a flow channel form similar to a herringbone wave structure, there are some optimization conditions between the pitch of the corrugated projections and the height of the corrugated projections. The prior art in the industry recognizes that better product performance can be obtained when the wave distance and the wave height meet a certain proportion range. After the current introduction of fin plate structures, this technology recognizes the need to synchronously consider relevant structural parameters on the fin plate. For the staggered sawtooth fin structure adopted in the application, the fin height of the fins, namely the first height H, and the distance between two adjacent rows of fins, namely the first distance P, need to be further combined with a herringbone wave structure for constraint, so as to obtain an integral optimized state. The first height H expresses the disturbing effect of the fluid in the fin plate area in the height direction of the flow channel, and the first pitch P expresses the periodicity of such disturbing effect. There are constraints and influence relationships between the two. In order to obtain effective fin working effect and synergy with the herringbone wave structure. The application provides a reasonable range of the ratio of the first pitch P to the first height H: 0.5-2.5. Or on the premise of reasonable corrugated bump and groove structures, the periodic action range of the fin unit, namely the first pitch P, cannot be higher than 9.5mm, and the lower limit is defined to be 1mm in consideration of the thickness and the manufacturing performance of the fin. Under the structural parameters, the flow channel area taking the fin structure as the leading part establishes a better synergistic effect in the process that fluid impacts or acts on the wall surface of the wave groove in a disturbance mode and the periodicity of disturbance, thereby obtaining better flow and heat exchange effects of the flow channel area. Meanwhile, the top of the fin and the near-wall surface flow channel form established by the corrugated protruding structure form a better contact effect with the wall surface of the groove on the one hand, and the strength of the flow channel is ensured. In the near-wall flow channel established by the corrugated bulges, the grooves and the tops of the fins, the relations of fluid distribution in the width direction of the plate surface, near-wall fluid heat exchange, near-wall and flow channel region fluid distribution, interaction and the like are well coordinated, and finally, a more reasonable performance effect of the heat exchanger is obtained.

Further given the dimensional ranges provided herein in some embodiments, the wave height of the herringbone wave structure, i.e., the height of the corrugated protrusions relative to the groove bottom, ranges from 0.7mm to 2.5mm, and the ratio of the average pitch of the corrugated protrusions to the wave height ranges from 2 to 6. Meanwhile, the matched fin plate needs to meet the requirement that the value range of the first pitch P is 2mm-8mm, and the ratio range of the first pitch P to the first height H is 0.8-1.5.

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) comprising a plurality of plates and at least one fin plate (60);

the fin plate (60) comprises a base (63) and a plurality of fin units (64) arranged along a first direction (X); each fin unit (64) comprises a plurality of fins protruding from the base (63), wherein each fin comprises a top (605) and two sides; the two side parts are respectively positioned at two opposite sides of the top part (605), and the two side parts are connected between the top part (605) and the base part (63);

the plurality of fins comprise a plurality of first fins (65) and a plurality of second fins (66); the first fins (65) and the second fins (66) are arranged alternately in a second direction (Y); the first direction (X) and the second direction (Y) are not co-directional; for two side parts which are positioned on two opposite sides of the fin top part (605), at least one group of side parts which are positioned on one side of the top part (605) of the first fin (65) and side parts which are positioned on one side of the top part (605) of the second fin (66) are staggered in the second direction (Y), and the side parts which are positioned on one side of the top part (605) of the first fin (65) and the side parts which are positioned on one side of the top part (605) of the second fin (66) are positioned on the same side of the corresponding fin top part (605), so that windows are formed between the two side parts which belong to the adjacent first fin (65) and the second fin (66) in the side parts respectively;

the plurality of plates comprise a plurality of first plates (101) and a plurality of second plates (102), wherein one second plate (102) is directly contacted with one first plate (101) and forms a fluid channel between the two first plates, and the fin plate (60) is positioned between the other first plate (101) and the other second plate (102) and forms another fluid channel between the two second plates; at least one of the first plate (101) and the second plate (102) is provided with a plurality of corrugated bulges (41) which are arranged along the length direction of the plate, and a groove (31) is formed between every two adjacent corrugated bulges (41); the corrugated bulge (41) comprises at least one extension section (411), and the extension section (411) is obliquely arranged relative to the length direction of the plate sheet; wherein at least a partial area of the tops of the corrugated protrusions (41) is in contact with the base (63) of the fin plate (60) or at least a partial fin top (605), and the window is in communication with the groove (31).

2. A plate heat exchanger (10) according to claim 1, wherein the number of the extending sections (411) of the corrugated protrusion (41) is greater than or equal to 2, and two adjacent extending sections (411) are respectively inclined to two sides of the width direction of the plate relative to the length direction of the plate; the corrugated bulge (41) further comprises a connecting section (412) connected to the extending direction end of two adjacent extending sections (411), and the two adjacent extending sections (411) are in round transition through the connecting section (412); the corrugated protrusions (41) are connected between the two side edges of the plate in the width direction in a continuous manner.

3. A plate heat exchanger (10) according to claim 2, wherein the two sides comprise a first side (603) and a second side (604); the first side (603) of the first fin (65) and the first side (603) of the second fin (66) are offset in the second direction (Y) with a first window (601) formed therebetween; the second side (604) of the first fin (65) and the second side (604) of the second fin (66) are offset in a second direction (Y) with a second window (602) formed therebetween;

the first direction (X) is perpendicular to the second direction (Y); wherein the first direction (X) coincides with the length direction of the plate, and the second direction (Y) coincides with the width direction of the plate; or the first direction (X) coincides with the width direction of the plate and the second direction (Y) coincides with the length direction of the plate.

4. A plate heat exchanger (10) according to claim 1, wherein the corrugation lobe (41) is provided with a recess (413), the recess (413) being recessed from a top surface of the corrugation lobe (41); at each extension (411), the direction of extension of the recess (413) is the same as the direction of extension of the corrugated protrusion (41), the depth of the bottom of the recess (413) with respect to the top of the corrugated protrusion (41) being smaller than the depth of the bottom of the groove (31) with respect to the top of the corrugated protrusion (41);

or the groove (31) is provided with a convex edge part (414), and the convex edge part (414) protrudes from the bottom of the groove (31) to one side of the fin plate (60); -the corrugated projections (41) adjacent to the raised ridge (414) form a parallel relationship with the raised ridge (414) at each of its extensions (411), the height of the tops of the raised ridges (414) relative to the bottom of the groove (31) being smaller than the height of the tops of the corrugated projections (41) relative to the bottom of the groove (31);

alternatively, the corrugated protrusion (41) comprises a top wall portion (415) and two side wall portions (416), the top wall portion (415) having a flat or micro-curved surface to facilitate welding; the two side wall parts (416) are respectively positioned at two sides of the width direction of the top wall part (415), and the side wall parts (416) are connected between the top wall part (415) and the bottom of the groove (31); the dimension of the top wall section (415) in the width direction is not equal to the dimension of the groove bottom of the groove (31) in the width direction.

5. A plate heat exchanger (10) according to claim 2, wherein the first plate (101) and the second plate (102) are each in a plurality;

wherein the first plate (101) and the second plate (102) are provided with a plurality of corrugated bulges (41); the first sheet (101) and the second sheet (102) each comprise a base plate portion (20); the base plate portion (20) is flush with the bottom of the groove (31) of the corresponding plate piece or the base plate portion (20) is flush with the top of the corrugated protrusion (41) of the corresponding plate piece.

6. A plate heat exchanger (10) according to claim 5, wherein for the corrugated protrusion (41) of the first plate (101), the included angle fitted by the extending directions of two adjacent extending sections (411) is taken as a first included angle; for the corrugated bulges (41) of the second plate (102), an included angle fitted by the extending directions of two adjacent extending sections (411) is recorded as a second included angle; wherein the first included angle is different from the second included angle.

7. A plate heat exchanger (10) according to claim 5, wherein the first plate (101) and the second plate (102) are each provided with two first corner holes (21) and two second corner holes (22); the plate part of the first plate (101) on the periphery of the first corner hole (21) is in contact with the plate part of the second plate (102) on the periphery of the first corner hole (21) on the front surface (200) at the back surface (300) of the first plate (101); the plate part of the first plate (101) on the periphery of the second corner hole (22) has a gap in at least partial region between the back surface (300) of the first plate (101) and the plate part of the second plate (102) on the periphery of the second corner hole (22) on the front surface (200).

8. A plate heat exchanger (10) according to claim 7, wherein the fin plate (60) is provided with two first notches (61) and two second notches (62);

on a reference plane formed by the length direction and the width direction of the plate, the projection of the first corner hole (21) on the plane is positioned in the projection range of the first notch (61) on the plane; the projection of the second corner hole (22) on the plane is positioned within the projection range of the second notch (62) on the plane.

9. A plate heat exchanger (10) according to claim 8, wherein two first corner holes (21) are located at one side of the width direction of the corresponding plate and two second corner holes (22) are located at the other side of the width direction of the corresponding plate;

or the two first corner holes (21) are arranged diagonally, and the two second corner holes (22) are arranged diagonally.

10. A plate heat exchanger (10) according to claim 3, wherein a number of the fin units (64) are evenly arranged in the first direction (X) on the fin plate (60); two adjacent fin units (64) are separated by a base (63); the distance between the central lines of two adjacent fin units (64) along the second direction (Y) is recorded as a first distance (P); the height of the fin protruding relative to the base (63) is recorded as a first height (H); wherein the value range of the first pitch (P) is 1.0 mm-9.5 mm and/or the value range of the ratio of the first pitch (P) to the first height (H) is 0.5-2.5.