CN210741194U

CN210741194U - Plate type heat exchanger

Info

Publication number: CN210741194U
Application number: CN201920764686.XU
Authority: CN
Inventors: 李华; 郑希茹
Original assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Current assignee: Zhejiang Sanhua Intelligent Controls Co Ltd
Priority date: 2019-05-24
Filing date: 2019-05-24
Publication date: 2020-06-12
Anticipated expiration: 2029-05-24

Abstract

The utility model discloses a plate heat exchanger, a first flow channel comprises an inter-plate channel, a first pore channel and a second pore channel; the fitting includes a first lumen, a first port, a second port, and a third port; the draft tube comprises a second cavity, a fourth port and a fifth port; the fitting piece is fixedly connected with the flow guide pipe; the flow guide pipe penetrates through the first cavity and extends into the first pore passage; the first blocking part extends from one of the plates to the inside of the first pore passage and is sealed with the flow guide pipe; the inter-plate channel is divided into a first inter-plate channel and a second inter-plate channel through a plate; the first blocking part divides the exterior of the draft tube into a first circulation area and a second circulation area, the first circulation area is communicated with the second pore passage through the first interplate channel, and the first circulation area is communicated with the first cavity; the second circulation area is communicated with the second hole channel through the second interplate channel, and the second circulation area is communicated with the second cavity. The utility model discloses be favorable to saving the required installation space of plate heat exchanger and improve plate heat exchanger's heat transfer performance.

Description

Plate type heat exchanger

Technical Field

The utility model relates to a heat exchange technology field especially relates to a plate heat exchanger.

Background

The plate heat exchanger can be applied to the fields of air conditioners, automobile battery cooling and the like, the plate heat exchanger is formed by stacking a plurality of plates, two working media which are mutually isolated flow inside the plate heat exchanger, the two working media comprise a refrigerant and a secondary refrigerant, and the two heat exchanges in the plate heat exchanger. Generally, a refrigerant enters a plate heat exchanger mostly from one side of the plate heat exchanger and then leaves the plate heat exchanger from the other side of the plate heat exchanger, and corresponding connecting pipelines are needed on two sides of the plate heat exchanger, so that the installation space needed by the plate heat exchanger is large.

SUMMERY OF THE UTILITY MODEL

The utility model discloses improve plate heat exchanger structure, be favorable to saving the required installation space of plate heat exchanger.

The embodiment of the application provides a plate heat exchanger, which comprises a plurality of plates, wherein the plates are stacked to form a first flow channel and a second flow channel which are not communicated with each other, and the first flow channel comprises an inter-plate channel, a first pore channel formed by one corner hole of each of the plates and a second pore channel formed by the other corner hole of each of the plates;

the plate heat exchanger also comprises an integrated piece and a first blocking part; the integrated piece comprises a fitting piece and a flow guide pipe, the fitting piece comprises a first cavity and a first fitting part positioned on the periphery of the first cavity, the first fitting part is provided with a first port and a second port, the first cavity is communicated with the first pore passage through the first port, and the first cavity is communicated with the outside of the plate heat exchanger through the second port; the honeycomb duct comprises a second cavity and a second matching part located on the periphery of the second cavity, the second matching part is provided with a fourth port and a fifth port, the second matching part is fixedly connected with the first matching part, the second matching part penetrates through the first cavity and extends into the first pore passage through the first port, and the second cavity is communicated with the outside of the plate heat exchanger through the fourth port; the second chamber is in communication with the first orifice through the fifth port; in the first hole channel, the first blocking part extends from the edge of the corner hole of one of the plates to the inside of the first hole channel, and the first blocking part is connected with the second matching part in a sealing manner; the interplate channel is divided into a first interplate channel and a second interplate channel by the one of the plates, the first interplate channel being closer to the fitting than the second interplate channel;

the outer diameter of the part of the second matching part, which is positioned in the first hole channel, is smaller than the inner diameter of the first hole channel, in the first hole channel, the first blocking part divides the outer area of the draft tube into a first circulation area and a second circulation area, the first circulation area is communicated with the second hole channel through the first interplate channel, and the first circulation area is communicated with the first cavity through the first port; the second flow-through region is in communication with the second port channel via the second interplate passages, and the second flow-through region is in communication with the second chamber via the fifth port.

This application is through improving plate heat exchanger's structure for through first chamber, first circulation district, first inter-plate passageway, second pore, second inter-plate passageway, second circulation district, the intercommunication is realized to the second chamber between plate heat exchanger second port and the fourth port, and then realize one in second port and the fourth port as the import, another is as the export, and integrated piece is close to first pore setting, and is corresponding, second port and fourth port also concentrate and are close to first pore setting, be favorable to optimizing plate heat exchanger's installation space.

Drawings

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

fig. 2 is a schematic cross-sectional view of the plate heat exchanger shown in fig. 1 according to the present invention;

fig. 3 is an exploded view of the plate heat exchanger of fig. 1 according to the present invention;

FIG. 4 is a schematic view of the plate heat exchanger of the present invention performing oblique convection;

fig. 5 is a schematic view of a fixing manner of the flow guide pipe and the first blocking portion of the plate heat exchanger of the present invention;

FIG. 6 is an enlarged schematic view of the fixing mode structure of the fitting member and the first side plate of the plate heat exchanger of the present invention;

fig. 7 is another schematic sectional structure diagram of the plate heat exchanger of the present invention;

fig. 8 is a schematic view of another cross-sectional structure of the plate heat exchanger of the present invention;

fig. 9 is a schematic view illustrating a fixing manner of a fitting member of the plate heat exchanger shown in fig. 1 according to the present invention;

fig. 10 is a schematic structural view of an upper shell of the plate heat exchanger in fig. 9;

fig. 11 is a structural schematic view of a lower housing of the plate heat exchanger in fig. 9;

fig. 12 is a schematic view of a flow path of the plate heat exchanger as an evaporator according to the present invention;

fig. 13 is a schematic view of another flow path of the plate heat exchanger of the present invention as an evaporator;

fig. 14 is a schematic view of a flow path of the plate heat exchanger as a condenser according to the present invention;

fig. 15 is a schematic view of another flow path of the plate heat exchanger as a condenser according to the present invention.

Detailed Description

The utility model provides a plate heat exchanger is through optimizing fluidic exit among the plate heat exchanger to and the design of two return strokes runner in the cooperation plate heat exchanger, be favorable to optimizing plate heat exchanger's installation space, improve plate heat exchanger's heat transfer effect. In order to make those skilled in the art better understand the technical solution of the present invention, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.

As shown in fig. 1, 2, and 3, the plate heat exchanger 100 includes a plurality of plates 101, each plate 101 is substantially rectangular, four corners of each plate 101 have a corner hole, the corner holes of the plates 101 align to form four pore channels, the plates 101 are stacked to form a first flow channel and a second flow channel that are not connected, the first flow channel includes an inter-plate channel 102, a first pore channel 103 formed by one corner hole of the plates 101, and a second pore channel 104 formed by another corner hole of the plates 101. The two sides of the plurality of plates are respectively a part of a first flow channel and a part of a second flow channel, for the first flow channel, the first flow channel further comprises two of the four pore channels, namely a first pore channel 103 and a second pore channel 104, the first pore channel 103 and the second pore channel 104 are communicated through the interplate channel 102, correspondingly, the second flow channel comprises the remaining two pore channels, the two pore channels are also communicated, and generally, the first flow channel and the second flow channel are respectively used for different fluids to flow, for example, a refrigerant flows through the first flow channel, and a coolant flows through the second flow channel.

The plate heat exchanger 100 further comprises an integration piece and a first blocking section 13. The integrated piece comprises a fitting 11 and a flow guide pipe 12, the fitting 11 comprises a first cavity 110 and a first fitting part 114 located on the periphery of the first cavity 110, the first fitting part 114 is provided with a first port 111 and a second port 112, the first cavity 110 is communicated with a first hole passage 103 through the first port 111, the first cavity 110 is directly communicated with the first hole passage 103, namely, one side of the first port 111 is the first cavity 110, the other side of the first cavity is the first hole passage 103, the first cavity 110 is communicated with the outside of the plate heat exchanger 100 through the second port 112, the first cavity 110 is also directly communicated with the outside of the plate heat exchanger 100, namely, one side of the second port 112 is the first cavity, and the other side of the second cavity is the outside of the plate heat exchanger 100.

The draft tube 12 includes a second chamber 120 and a second matching portion 126 located at the periphery of the second chamber 120, the second matching portion 126 is provided with a fourth port 121 and a fifth port 122, the second matching portion 126 is fixedly connected with the first matching portion 114, and the second chamber 120 is communicated with the outside of the plate heat exchanger 100 through the fourth port 121. The second chamber 120 is also in direct communication with the outside of the plate heat exchanger 100, i.e. the fourth port 121 is on one side of the second chamber 120 and on the other side of the plate heat exchanger 100. In the direction in which the plates 101 are stacked, which is substantially vertical in fig. 2, reference may be made to the direction indicated by the solid line with a double-headed arrow in fig. 2, the second fitting portion 126 extends through the first cavity 110 and protrudes into the first hole 103 through the first port 111, and the second cavity 120 communicates with the first hole 103 through the fifth port 122, that is, the end of the flow guide tube 12 including the fifth port 122 is located in the first hole 103.

The second matching portion 126 of the draft tube 12 penetrates through the first cavity 110, at least part of the draft tube 12 is located in the first cavity 110, one end of the draft tube 12 extends into the first hole passage, the other end of the draft tube 12 faces the outside of the plate heat exchanger 100, the second matching portion 126 of the draft tube 12 is matched and fixedly connected with the first matching portion 114 of the matching piece 11, the first cavity 110 of the matching piece 11 is communicated with the first hole passage 103 through the first port 111, in this way, the first matching portion 114 and the first hole passage 103 are located on two sides of the first port 111 relatively, part of the second cavity 120 of the draft tube 12 is located in the first cavity 110, the matching piece 11 is equivalently sleeved outside the draft tube 12, the first cavity 110 and the second cavity 120 are communicated with the first hole passage 103, the overall volume of the integrated component is favorably reduced, the integrated component is integrally arranged close to the first hole passage 103, the second port 112 and the fourth port 121 are also integrally arranged close to the first, thus, the plate heat exchanger 100 can save part of space at the position corresponding to the second hole channel 104, which is beneficial to optimizing the installation space of the whole plate heat exchanger 100, the inlet and outlet of fluid such as refrigerant are integrated together, the first hole channel 103 simultaneously realizes the inlet and outlet of refrigerant, compared with the channel with the first hole channel 103 as the inlet, the second hole channel 104 as the outlet, which is beneficial to the integrated installation of the plate heat exchanger 100 and other components, and the requirement of system compactness is met, and for the fitting piece 11, the structure of the first fitting part 114 is simple, which is convenient for processing and manufacturing, and the whole volume of the fitting piece 11 is reduced.

In the first hole passage 103, the first blocking part 13 extends from the edge of the corner hole of one of the sheets 101 to the inside of the first hole passage 103, and the first blocking part 13 is connected with the second matching part 126 in a sealing manner; the interplate channel 102 is divided into a first interplate channel 1021 and a second interplate channel 1022 by the one plate, the first interplate channel 1021 is closer to the mating piece 11 than the second interplate channel 1022, the first interplate channel 1021 may be an interplate channel formed between an uppermost plate and the one plate, the uppermost plate refers to the plate closest to the mating piece 11, correspondingly, the second interplate channel 1022 may be an interplate channel formed between a lowermost plate and the one plate, and the lowermost plate refers to the plate farthest from the mating piece 11.

When the first blocking portion 13 is used for processing and manufacturing the corner hole position of one of the plates 101, a small hole is separately punched at the corresponding corner hole position, that is, the corner hole position is not completely punched according to the size of the corner hole, the remaining part of the plate structure may form the first blocking portion 13, the hole diameter of the punched small hole is matched with the outer diameter of the part of the second matching portion 126 located in the first duct 103, and the first blocking portion 13 may also be a separate component, and may be fixed with the plate 101 at the corresponding corner hole position into a whole by welding or the like.

The first blocking portion 13 extends into the first hole 103 through the corner hole edge of one of the plates 101, and the first blocking portion 13 is arranged substantially parallel to the plate 101. Along the direction of lamination of the plates 101, the first inter-plate channel 1021 is relatively close to the fitting piece 11, the second inter-plate channel 1022 is relatively far away from the fitting piece 11, the flowing direction of fluid in the first inter-plate channel 1021 is opposite to that of fluid in the second inter-plate channel 1022, fluid realizes one return stroke in the first inter-plate channel 1021, and the other return stroke in the second inter-plate channel 1022, so that under the condition that the size of the plate heat exchanger 100 is small, the flowing path of the fluid can be effectively increased, and the good heat exchange performance of the plate heat exchanger is ensured.

The outer diameter L1 of the portion of the second fitting portion 126 located in the first hole 103 is smaller than the inner diameter L2 of the first hole 103, the first blocking portion 13 divides the outer area of the draft tube 12 into a first flow-through area 123 and a second flow-through area 124 in the first hole 103, the first flow-through area 123 is communicated with the second hole 104 through the first interplate passage 1021, and the first flow-through area 123 is communicated with the first chamber 110 through the first port 111. The second flow-through section 124 communicates with the second port 104 via the second interplate passages 1022, and the second flow-through section 124 communicates with the second chamber 120 via the fifth port 122.

The first flow-through area 123 and the second flow-through area 124 are adjacently arranged, the first flow-through area 123 is closer to the fitting 11 than the second flow-through area 124, in the first hole 103, the first flow-through area 123 is an area where a gap between the outer wall of the draft tube 12 and the inner side of the first hole 103 is located, and the second flow-through area 124 is an area where the first hole 103 is located between the first blocking portion and the second side plate of the plate heat exchanger 100.

The fixed connection between the second matching portion 126 and the first matching portion 114 may include various manners, for example, an integrally connected fixing manner and a separately assembled fixing manner, that is, the whole matching member 11 and the whole honeycomb duct 12 may be mutually independent components, and are integrated into a whole during assembly to form an integrated component, the second matching portion 126 and the first matching portion 114 are fixed by welding or the like, and the two do not displace relative to each other, specifically, the first matching portion 114 further has a third port 113, and at the third port 113, the outer walls of the first matching portion 114 and the second matching portion 126 are sealed and welded to enable the first cavity 110 to be isolated from the outside of the plate heat exchanger 100 at the third port 113. Or the integrated member may be formed integrally, for example, by a metal casting process, or the integrated member may be formed integrally by an injection molding process, so that the second matching portion 126 and the first matching portion 114 are integrally connected, and they may be fixedly connected.

Of course, similar to the first flow channel, the second flow channel may also implement two return flows in the interplate passages corresponding to the second flow channel by using similar structural and positional relationships of the fitting 11, the flow guide tube 12 and the first blocking portion 13 for the fluid flowing in the second flow channel, for example, the ethylene glycol aqueous solution used as the coolant; or still adopt the flow mode of a return stroke, the utility model discloses do not do the specific restriction to the flow mode of fluid in the second flow path.

Further, plate heat exchanger 100 still includes first sideboard 21 and second sideboard 22, the thickness of first sideboard 21 and second sideboard 22 all is greater than the thickness of slab 101, first sideboard 21 can be including welding bottom plate and reinforcing plate as an organic whole, or first sideboard 21 adopts the monoblock sideboard that thickness is thicker, the thickness of first sideboard 21 is thicker can improve the welding strength between the outer wall of first sideboard 21 and fitting piece 11, it is fixed as an organic whole through the welding between first sideboard 21 and second sideboard 22 and the many slabs 101, wherein the welding can be the brazing, thereby be favorable to improving the intensity and the reliability of plate heat exchanger 100. The first side plate 21 has a first plate hole 211, a second plate hole 212, and a third plate hole 213, the first plate hole 211 and the first porthole 103 are coaxially disposed or eccentrically disposed, both ends of the second porthole 104 are sealed by the first side plate 21 and the second side plate 22, that is, the fluid flowing in the second porthole 104 cannot be directly communicated with the outside of the plate heat exchanger 100 through the first side plate 21 or the second side plate 22, and the second plate hole 212 and the third plate hole 213 are coaxially disposed or eccentrically disposed with the portholes formed by the other two corner holes of the plurality of plates 101.

The plate heat exchanger 100 further includes a first extension pipe 23 and a second extension pipe 24, the first extension pipe 23 is communicated with the second flow passage through the second plate hole 212, and the second extension pipe 24 is communicated with the second flow passage through the third plate hole 213. Three plate holes are formed in the first side plate 21, one plate hole is matched with the matching piece 11 to be fixed, and the other two plate holes are matched with the first external connecting pipe 23 and the second external connecting pipe 24 to be fixed. The first and

second extension pipes

23 and 24 are located at one side of the plate heat exchanger 100 in the width direction. Or the first external connecting pipe 23 and the second external connecting pipe 24 are arranged diagonally, as shown in fig. 4, so that the fluid, such as the refrigerant, is optimally distributed by adopting an oblique angle convection mode on the basis of two return strokes of the first flow channel, and a sufficient heat exchange effect can be achieved, as shown in fig. 4, the refrigerant flows into the plate heat exchanger from the fourth port 121, flows out of the plate heat exchanger from the second port 112, and of course, the refrigerant can also flow into the plate heat exchanger from the second port 112 and flows out of the plate heat exchanger from the fourth port 121. The first external connection pipe 23, the second external connection pipe 24, and the fitting member 11 and the flow guide pipe 12 integrated as an integral assembly may be disposed on the same side of the plate heat exchanger 100, or may be disposed on different sides based on the installation requirement of the plate heat exchanger 100, for example, the first external connection pipe 23 and the second external connection pipe 24 are disposed on one side of the plate heat exchanger 100, and the fitting member 11 and the flow guide pipe 12 integrated as an integral assembly are disposed on the other side of the plate heat exchanger 100 opposite to each other.

Referring to fig. 5, the first blocking portion 13 includes a baffle portion 130 and a through hole 131, the baffle portion 130 is located at the periphery of the through hole 131, the first blocking portion 13 includes a flange portion 125 raised along the edge of the baffle portion 130, the draft tube 12 extends into the through hole 131, the flange portion 125' of the first blocking portion 13 is fixed to the outer wall of the draft tube 12 in a sealing manner, the draft tube 12 is pressed into the through hole 131 during manufacturing, a tube expanding process can be used to expand the diameter of the draft tube 12, a gap between the draft tube 12 and the baffle portion 130 is eliminated or reduced, the sealing performance is improved, or the flange portion 125 and the outer wall of the draft tube 12 are directly welded in a sealing manner, and the like.

Referring to the structural schematic of the fitting 11 shown in fig. 6, the fitting 11 includes a first fitting portion 114 located at the periphery of the first cavity 110, the first fitting portion 114 includes a first body 115 and a protruding portion 116 connected to the first body 115 and extending in the lamination direction of the plate 101, the protruding portion 116 includes a first boss 1161 and a second boss 1162 connected to each other, the first boss 1161 is closer to the first hole 103 than the second boss 1162, the first port 111 is located at an end of the first boss 1161 away from the first body 115, and the first port 111 is located at a bottom side of the protruding portion 116 in the view direction illustrated in fig. 6. The protrusion 116 has a first notch 117, and in a direction perpendicular to the lamination direction of the plates 101, fig. 6 is indicated by a solid line with a double arrow, the direction is approximately a horizontal direction, the first notch 117 is adjacent to the first boss 1161, and the first notch 117 is farther from the flow guide tube 12 than the first boss 1161, and the existence of the first notch 117 makes the outer wall of the protrusion 116 have a step shape. At first breach 117, first sideboard 21 and boss 116's outer wall welded fastening, first body 115 passes through second boss 1162 and first sideboard 21 looks interval, like this, can realize fixedly through boss 116 and first sideboard 21 between plate heat exchanger 100's heat exchange core part and the fitting piece 11, and direct contact is not between first body 115 and the first sideboard 21, be favorable to reducing the pressure that first body 115 gives plate heat exchanger 100's heat exchange core part, and then be favorable to reducing fitting piece 11 to the influence of fluid flow resistance in plate heat exchanger 100 passageway between the board, can improve plate heat exchanger 100's heat transfer effect.

Referring to fig. 7, for the mating member 11, the mating member 11 may be an integrally formed component, the first body 115 includes a first top surface 1151, a first bottom surface (not shown) and a first side surface 1152, the first side panel includes a panel surface 210, the panel surface 210 is substantially planar, the panel surface 210 is an end surface of the first side panel away from the panel, the first top surface 1151 and the first bottom surface are a set of opposing end surfaces that are parallel or substantially parallel to the panel surface 210 of the first side panel 21, and the first top surface 1151 is further away from the panel 101 than the first bottom surface. In fig. 7, first top surface 1151 is the uppermost end surface of mating member 11, a gap exists between the first bottom surface and plate surface 210 of first side plate 21, first side surface 1152 is connected to first top surface 1151, first side surface 1152 may be, as shown in fig. 7, an end surface perpendicular or substantially perpendicular to first side plate 21, first side surface 1152 may also be an inclined end surface, first top surface 1151 of mating member 11 may be substantially rectangular, and correspondingly, the first side surface may also be correspondingly rectangular, or first top surface 1151 may be substantially oval or elliptical-like, and the first side surface may correspondingly be an arc-shaped surface, and the specific shape of mating member 11 is not particularly limited in this application. Third port 113 is located first top surface 1151, third port 113 and first port 111 set up coaxially or set up eccentrically, second port 112 is located first side 1152, thus, because honeycomb duct 12 needs to realize sealing connection with fitting piece 11 in third port 113 department, that is corresponding, fourth port 121 is close to first top surface 1151 and sets up, thus, fourth port 121 and second port 112 set up towards different directions, facilitate processing and manufacturing, the volume of fitting piece 11 also can further reduce, and fourth port 121 and second port 112 set up towards different directions, can reduce mutual interference when making port and pipe connection, be favorable to optimizing plate heat exchanger 100's installation space.

Similar to the structure illustrated in fig. 7, referring to fig. 8, the second port 112 and the third port 113 are also located on the first top surface 1151, the first chamber 110 includes a first sub-chamber 1101 and a second sub-chamber 1102 communicating with each other, the first sub-chamber 1101 communicates with the first duct 103 through the first port 111, and the second sub-chamber 1102 extends obliquely from the second port 112 to the first sub-chamber 1101. The fitting 11 of rectangular structure is relatively better to be processed, first sub-chamber 1101 and the sub-chamber 1102 of second accessible manufacturing of technology modes such as machining, first sub-chamber 1101 and the sub-chamber 1102 of second can have the passageway central line that is straight line relatively promptly, make things convenient for manufacturing, and the sub-chamber 1102 of second extends to first sub-chamber 1101 from the relative slope of second port 112, and fluid flow is smooth and easy in second sub-chamber 1102, and flow path is shorter, is favorable to reducing flow resistance, improves heat transfer performance.

Of course, the fitting 11 may also be formed by splicing through a zero component, as shown in fig. 9, 10, and 11, the fitting 11 includes an upper housing 33 and a lower housing 44 manufactured by press forming or machining, and the like, the upper housing 33 includes a first sub-portion 331 and a second sub-portion 332 connected to each other, the first sub-portion 331 is farther from the plate 101 than the second sub-portion 332, the fitting 11 further includes a first channel 333 and a second channel 334 penetrating through the first sub-portion 331, a third port 113 is formed at an end of the first channel 333 far from the second sub-portion 332, and a second port 112 is formed at an end of the second channel 334 far from the second sub-portion 332. The fitting 11 further includes a third channel 335 penetrating through the second sub-portion 332, and on a plane perpendicular to the stacking direction of the plate 101, projections of the first channel 333 and the second channel 334 are located within a projection range of the third channel 335, so that machining of the upper housing is facilitated.

Lower housing 44 includes protruding portion 116 and third sub-portion 441 connected to protruding portion 116, third sub-portion 441 is farther from sheet 101 than protruding portion 116, fitting member 11 further includes fourth channel 442 passing through third sub-portion 441, fourth channel 442 is communicated with the cavity surrounded by protruding portion 116, the inner diameter of fourth channel 442 is greater than or equal to the inner diameter of protruding portion 116, and first through hole 333, fourth channel 442, and protruding portion 116 are coaxially or eccentrically disposed. The lower housing 44 further has a first groove 443 extending from the fourth channel 442 in a direction perpendicular to the stacking direction of the sheets 101, the first groove 443 is communicated with the fourth channel 442, a projection of the first groove 443 at least partially coincides with a projection of the second channel 334 on a plane perpendicular to the stacking direction of the sheets 101, so that when the upper housing 33 and the lower housing 44 are joined, the first groove 443 is communicated with the second through hole 334 through the third channel 335, and fluid can flow into the third channel 335 through the first groove 443 and then into the second channel 334, or flow into the third channel 335 through the second channel 334 and then into the first groove 443, wherein the upper housing 33 and the lower housing 44 are fixed by welding on opposite sides between the second sub-portion 332 and the third sub-portion 441, and the upper housing 33 and the lower housing 44 are welded as a single piece.

Referring to fig. 9, an installation structure of the draft tube 12 and the fitting 11 is shown, in which the draft tube 12 includes a second fitting portion 126 located at the periphery of the second chamber 120, and in the stacking direction of the plate 101, the second fitting portion 126 includes a second body 127 and a third boss 129, in the stacking direction of the plate 101, a fourth port 121 and a fifth port 122 are respectively formed at two ends of the second body 127, the fourth port 121 is farther from the plate 101 than the fifth port 122, preferably, the outer diameter of the portion of the second body 127 close to the fourth port 121 is larger than the outer diameter of the portion of the second body 127 close to the fifth port 122, and the outer diameter of the portion of the second body 127 close to the fourth port 121 matches the inner diameter of the first passage 333, so as to facilitate welding of the fitting 11 with the draft tube 12 at the first passage 333.

The third bosses 129 are connected to the second body 127 and extend in a direction substantially perpendicular to the direction in which the sheets 101 are stacked. The second fitting portion 126 has a second notch 1261, the second notch 1261 is adjacent to the third boss 129 in the stacking direction of the plate pieces 101, the second notch 1261 is closer to the plate piece 101 than the third boss 129, and the outer wall of the first fitting portion 114 and the outer wall of the second fitting portion 126 are hermetically welded at the second notch 1261.

By sealing the outer walls of the first matching part 114 and the second matching part 126 at the second notch 1261, the first cavity 110 cannot be communicated with the outside of the plate heat exchanger 100 through the third port 113, and the sealing area of the first matching part 114 and the second matching part 126 is large, so that the sealing reliability can be improved, furthermore, because the third boss 129 and the second matching part 126 protrude out of the end surface, far away from the plate 101, of the first body 115, when the electronic expansion valve is installed with a throttling component such as an electronic expansion valve, the electronic expansion valve can be sleeved on the periphery of the third boss 129, and the electronic expansion valve can be directly installed through mechanical connection and other modes.

Based on the structure of the plate heat exchanger 100 described above, in an embodiment, referring to fig. 12, the plate heat exchanger 100 is used as an evaporator, and accordingly, the first flow passage is used for flowing refrigerant, the second flow passage is used for flowing coolant, the fourth port 121 is used as a refrigerant inlet, the second port 112 is used as a refrigerant outlet, the number of channels of the first plate-to-plate channels 1021 is greater than that of the second plate-to-plate channels 1022, and when the plate structure of the plate heat exchanger 100 is basically similar in channel size and structure, the height H1 of the heat exchange section formed by the first plate-to-plate channels 1021 is greater than the height H2 of the heat exchange section formed by the second plate-to-plate channels 1022, referring to fig. 12, that is, along the stacking direction of the plates 101.

When the plate heat exchanger 100 is used as an evaporator, a gas-liquid two-phase refrigerant enters the second chamber 120 from the fourth port 121, flows out of the second chamber 120 from the fifth port 122, enters the second flow area 124, passes through the second plate passages 1022, enters the second port 104, enters the first flow area 123 through the first plate passages 1021, enters the first chamber 110 through the first port 111, and finally flows out of the plate heat exchanger 100 from the second port 112 in a gas-phase or gas-liquid two-phase state, a flow direction of a heat exchange section formed by the first plate passages 1021 is a direction from the second port 104 to the first port 103, and a flow direction of a heat exchange section formed by the second plate passages 1022 is a direction from the first port 103 to the second port 104. The flow paths of the refrigerants are increased due to the design of the two return paths, the gas-liquid two-phase refrigerants flowing in the first flow channel exchange heat with the secondary refrigerants flowing in the second flow channel, the specific gravity of the gas-liquid two-phase refrigerants is gradually increased when the gas-liquid two-phase refrigerants exchange heat in the first flow channel, the number of the channels of the first interplate channels 1021 is larger than that of the channels of the second interplate channels 1022, on one hand, the number of the channels of the heat exchange section formed by the second interplate channels 1022 is small, and the problem of uneven distribution of the refrigerants in each channel is solved. On the other hand, the proportion of the first inter-plate channel 1021 to the total inter-plate channels is large, so that large pressure drop loss is avoided, the refrigerant with increased gaseous specific gravity can flow out of the plate heat exchanger 100 quickly, the heat exchange coefficient of the refrigerant is improved, and the heat exchange effect of the plate heat exchanger 100 is finally improved.

In another embodiment, referring to fig. 13, the plate heat exchanger 100 is used as an evaporator, and accordingly, the first flow channel is used for flowing a refrigerant, the second flow channel is used for flowing a secondary refrigerant, the second port 112 is used as a refrigerant inlet, the fourth port 121 is used as a refrigerant outlet, the number of channels of the first plate-to-plate channels 1021 is smaller than that of the second plate-to-plate channels 1022, and when the plate structure of the plate heat exchanger 100 is basically similar in channel size and structure, referring to fig. 13, that is, along the stacking direction of the plates 101, the height H1 of the heat exchange section formed by the first plate-to-plate channels 1021 is smaller than the height H2 of the heat exchange section formed by the second plate-to-plate channels 1022.

When the plate heat exchanger 100 is used as an evaporator, a gas-liquid two-phase refrigerant enters the first cavity 110 from the second port 112, then flows out of the first cavity 110 from the first port 111, enters the first circulation area 123, then passes through the first plate passages 1021, enters the second port 104, then enters the second circulation area 124 through the second plate passages 1022, then enters the second cavity 120 through the fifth port 122, and finally flows out of the plate heat exchanger 100 from the fourth port 121 in a gas-phase or gas-liquid two-phase state, a flow direction of a heat exchange section formed by the first plate passages 1021 is a direction from the first port passage 103 to the second port passage 104, and a flow direction of a heat exchange section formed by the second plate passages 1022 is a direction from the second port passage 104 to the first port passage 103. The flow paths of the refrigerants are increased due to the design of the two return paths, the gas-liquid two-phase refrigerants flowing in the first flow channel exchange heat with the secondary refrigerants flowing in the second flow channel, when the gas-liquid two-phase refrigerants exchange heat in the first flow channel, the specific gravity of the gaseous refrigerants is gradually increased, the number of the channels of the second interplate channels 1022 is larger than that of the channels of the first interplate channels 1021, on one hand, the number of the channels of the heat exchange section formed by the first interplate channels 1021 is small, and the problem of uneven distribution of the refrigerants in each channel is solved. On the other hand, the second interplate passages 1022 occupy a larger proportion of the total interplate passages, so that there is no large pressure drop loss, which is beneficial for the refrigerant with increased gaseous specific gravity to flow out of the plate heat exchanger 100 quickly, improving the heat exchange coefficient of the refrigerant, and finally improving the heat exchange effect of the plate heat exchanger 100.

In yet another embodiment, referring to fig. 14, the plate heat exchanger 100 is used as a condenser, the first flow channel is used for flowing refrigerant, the second flow channel is used for flowing coolant, the fourth port 121 is used as a refrigerant inlet, the second port 112 is used as a refrigerant outlet, the number of channels of the first plate-to-plate channels 1021 is smaller than that of the second plate-to-plate channels 1022, and when the size and the structure of the channels formed by the plate structure of the plate heat exchanger 100 are substantially similar, as shown in fig. 14, the height H1 of the heat exchange section formed by the first plate-to-plate channels 1021 is smaller than the height H2 of the heat exchange section formed by the second plate-to-plate channels 1022.

When the plate heat exchanger 100 is used as a condenser, a single-phase gaseous refrigerant enters the second chamber 120 from the fourth port 121, then flows out of the second chamber 120 from the fifth port 122 and enters the second flow area 124, then passes through the second plate passages 1022, enters the second port channel 104, then enters the first flow area 124 through the first plate passages 1021, then enters the first chamber 110 through the first port 111, and finally flows out of the plate heat exchanger 100 from the second port 112 in a single-phase liquid state, a flow direction of a heat exchange section formed by the refrigerant in the first plate passages 1021 is a direction pointing from the second port channel 104 to the first port channel 103, and a flow direction of a heat exchange section formed by the refrigerant in the second plate passages 1022 is a direction pointing from the first port channel 103 to the second port channel 104. The gaseous refrigerant enters from the fourth port 121, flows in the first flow channel, exchanges heat with the secondary refrigerant flowing in the second flow channel, and is condensed into a liquid state, the flow path of the refrigerant is increased due to the design of the two return paths, and in order to ensure that the refrigerant still has a good supercooling degree at the outlet, i.e., the second port 112, of the plate heat exchanger 100 with a smaller size, the number of the second interplate passages 1022 is greater than that of the first interplate passages 1021, which is beneficial to the flow distribution of the refrigerant and achieves a good heat exchange effect.

In yet another embodiment, referring to fig. 15, the plate heat exchanger 100 is used as a condenser, the first flow channel is used for flowing a refrigerant, the second flow channel is used for flowing a coolant, the second port 112 is used as a refrigerant inlet, the fourth port 121 is used as a refrigerant outlet, the number of channels of the first plate-to-plate channels 1021 is greater than that of the second plate-to-plate channels 1022, and when the plate structure of the plate heat exchanger 100 is basically similar in channel size and structure, as shown in fig. 14, the height H1 of the heat exchange section formed by the first plate-to-plate channels 1021 is greater than the height H2 of the heat exchange section formed by the second plate-to-plate channels 1022.

When the plate heat exchanger 100 is used as a condenser, a single-phase gaseous refrigerant enters the first chamber 110 from the second port 112, flows out of the first chamber 110 from the first port 111, enters the first flow area 123, passes through the first plate passages 1021, enters the second port 104, passes through the second plate passages 1022, enters the second flow area 124, passes through the fifth port 122, enters the second chamber 120, and finally flows out of the plate heat exchanger 100 from the fourth port 121 in a single-phase liquid state, a flow direction of a heat exchange section formed by the refrigerant in the first plate passages 1021 is a direction from the first port 103 to the second port 104, and a flow direction of a heat exchange section formed by the refrigerant in the second plate passages 1022 is a direction from the second port 104 to the first port 103. Gaseous refrigerant enters from the second port 112, flows in the first flow channel, exchanges heat with secondary refrigerant flowing in the second flow channel and condenses into a liquid state, the flow path of the refrigerant is increased due to the design of the two return paths, and in order to enable the refrigerant to still have a good supercooling degree at the outlet, namely the second port 112, of the plate heat exchanger 100 with a small size, the number of the first plate-to-plate channels 1021 is larger than that of the second plate-to-plate channels 1022, so that the flow distribution of the refrigerant is facilitated, and a good heat exchange effect is achieved.

It is right above the utility model provides a plate heat exchanger has carried out the detailed introduction. The principles and embodiments of the present invention have been explained herein using specific examples, and the above descriptions of the embodiments are only used to help understand the core concepts of the present invention. It should be noted that, for those skilled in the art, without departing from the principle of the present invention, the present invention can be further modified and modified, and such modifications and modifications also fall within the protection scope of the appended claims.

Claims

1. A plate heat exchanger comprises a plurality of plates, wherein the plates are stacked to form a first flow channel and a second flow channel which are not communicated, and the first flow channel comprises an inter-plate channel, a first pore channel formed by one corner hole of each plate and a second pore channel formed by the other corner hole of each plate;

2. The plate heat exchanger according to claim 1, further comprising a first side plate having a first plate hole, a second plate hole, and a third plate hole, wherein the first plate hole is coaxially or eccentrically disposed with respect to the first porthole, both ends of the second porthole are sealed by the first side plate and the second side plate, and the second plate hole and the third plate hole are coaxially or eccentrically disposed with respect to portholes formed by the other two corner holes of the plurality of plates, respectively; the plate heat exchanger further comprises a first external connecting pipe and a second external connecting pipe, the first external connecting pipe is communicated with the second flow channel through the second plate hole, and the second external connecting pipe is communicated with the second flow channel through the third plate hole.

3. A plate heat exchanger according to claim 2, wherein the first and second extension tubes are located at one side in the width direction of the plate heat exchanger; or the first external connecting pipe and the second external connecting pipe are arranged diagonally.

4. The plate heat exchanger of claim 2, wherein the first mating portion further defines a third port at which the first mating portion is sealingly welded to an outer wall of the second mating portion such that the first chamber is isolated from an exterior of the plate heat exchanger at the third port.

5. The plate heat exchanger according to claim 2, wherein the first fitting portion includes a first body and a boss connected to the first body and extending in the plate stacking direction, the boss includes a first boss and a second boss connected to each other, the first boss is closer to the first hole passage than the second boss, the first port is located at an end of the first boss away from the first body, the boss has a first notch, the first notch is adjacent to the first boss and is farther from the flow guide pipe than the first boss, the first edge plate is welded to an outer wall of the boss at the first notch, and the first body is spaced from the first edge plate by the second boss.

6. The plate heat exchanger according to claim 4, wherein the second fitting portion includes a second body and a third boss along the plate stacking direction, both ends of the second body form the fourth port and the fifth port, respectively, along the plate stacking direction, the fourth port is farther from the plate than the fifth port, and the third boss is connected to the second body and extends in a direction substantially perpendicular to the plate stacking direction; the second matching part is provided with a second notch, the second notch is adjacent to the third boss along the lamination direction of the plate, the second notch is closer to the plate than the third boss, and the first matching part is in sealing welding with the outer wall of the second matching part through the second notch at the third port.

7. The plate heat exchanger according to claim 4 or 6, wherein the mating member is an integrally formed component, the first body includes a first top surface, a first bottom surface and a first side surface, the first top surface and the first bottom surface are a set of opposing end surfaces parallel or substantially parallel to the plate surface of the first side plate, the first top surface is farther away from the plate than the first bottom surface, the first side surface connects the first top surface and the first bottom surface, the third port is located at the first top surface, and the third port is located coaxially or eccentrically with the first port;

the second port is located at the first side; or the second port is also located on the first top surface, the first cavity comprises a first sub-cavity and a second sub-cavity which are communicated, the first sub-cavity is communicated with the first hole passage through the first port, and the second sub-cavity extends from the second port to the first sub-cavity in an inclined mode.

8. A plate heat exchanger according to claim 4 or 6, wherein the fitting comprises an upper housing and a lower housing, the upper housing comprising a first subsection and a second subsection connected, the first subsection being further from the plate than the second subsection, the fitting further comprising a first channel and a second channel through the first subsection, an end of the first channel remote from the second subsection forming the third port, an end of the second channel remote from the second subsection forming the second port; the fitting piece further comprises a third channel penetrating through the second sub-portion, and projections of the first channel and the second channel are located in a projection range of the third channel on a plane perpendicular to the stacking direction of the plates;

the lower shell comprises a convex part and a third sub-part connected with the convex part, the third sub-part is far away from the plate sheet than the convex part, the fitting piece further comprises a fourth channel penetrating through the third sub-part, the inner diameter of the fourth channel is larger than or equal to that of the convex part, and the first channel, the fourth channel and the convex part are coaxially or eccentrically arranged; the lower shell is also provided with a first groove extending from the fourth channel to a direction perpendicular to the stacking direction of the plates, the projection of the first groove is at least partially overlapped with the projection of the second channel on a plane perpendicular to the stacking direction of the plates, and the upper shell and the lower shell are fixed through opposite side surfaces between the second sub-portion and the third sub-portion in a welding mode.

9. A plate heat exchanger according to any one of claims 1-6, wherein the plate heat exchanger is an evaporator and the first flow channel is for circulation of a refrigerant; the fourth port is used as an inlet of the refrigerant, the second port is used as an outlet of the refrigerant, and the number of channels of the first interplate channels is larger than that of the second interplate channels;

or, the second port serves as an inlet of the refrigerant, the fourth port serves as an outlet of the refrigerant, and the number of channels of the first plate-to-plate channels is smaller than that of the second plate-to-plate channels.

10. A plate heat exchanger according to any one of claims 1-6, wherein the plate heat exchanger is a condenser and the first flow channel is for circulation of a refrigerant; the fourth port is used as an inlet of the refrigerant, the second port is used as an outlet of the refrigerant, and the number of channels of the first plate-to-plate channels is smaller than that of the second plate-to-plate channels;

or, the second port serves as an inlet of the refrigerant, the fourth port serves as an outlet of the refrigerant, and the number of channels of the first plate-to-plate channels is greater than that of the second plate-to-plate channels.