A plate heat exchanger

Abstract

The present invention discloses a plate heat exchanger. The first flow channel includes an inter-plate channel, a first orifice and a second orifice; the fitting includes a first cavity, a first port, a second port and a third port; the diversion tube includes a second cavity, a fourth port and a fifth port; the fitting is fixedly connected to the diversion tube; the diversion tube penetrates through the first cavity and extends into the first orifice; the first blocking portion extends from one of the plates into the first orifice and seals with the diversion tube; the inter-plate channel is divided into a first inter-plate channel and a second inter-plate channel by the plates; the first blocking portion divides the outer part of the diversion tube into a first flow area and a second flow area, the first flow area communicates with the second orifice through the first inter-plate channel, and the first flow area communicates with the first cavity; the second flow area communicates with the second orifice through the second inter-plate channel, and the second flow area communicates with the second cavity. The present invention is beneficial to saving the installation space required by the plate heat exchanger and improving the heat exchange performance of the plate heat exchanger.

Description

Technical Field

[0001] The present invention relates to the technical field of heat exchange, and particularly to a plate heat exchanger. Background Art

[0002] The plate heat exchanger can be applied to fields such as air conditioners and automotive battery cooling. The plate heat exchanger is formed by stacking multiple plate sheets. Two mutually isolated working fluids flow inside the plate heat exchanger. The two working fluids include a refrigerant and a coolant, and the two perform heat exchange inside the plate heat exchanger. Usually, the refrigerant enters the plate heat exchanger mostly from one side of the plate heat exchanger and then leaves from the other side of the plate heat exchanger. Corresponding connecting pipelines are required on both sides of the plate heat exchanger, resulting in a relatively large installation space required for the plate heat exchanger. Summary of the Invention

[0003] The present invention improves the structure of the plate heat exchanger, which is beneficial to saving the installation space required for the plate heat exchanger.

[0004] An embodiment of the present application provides a plate heat exchanger, including multiple plate sheets. The multiple plate sheets are stacked to form a non-connected first flow channel and a second flow channel. The first flow channel includes an inter-plate channel, a first hole formed by a corner hole of the multiple plate sheets, and a second hole formed by another corner hole of the multiple plate sheets;

[0005] The plate heat exchanger further includes an integrated part and a first blocking part; the integrated part includes a fitting part and a diversion pipe. The fitting part includes a first cavity and a first fitting part located outside 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 hole through the first port, and the first cavity is communicated with the outside of the plate heat exchanger through the second port; the diversion pipe includes a second cavity and a second fitting part located outside the second cavity. The second fitting part is provided with a fourth port and a fifth port. The second fitting part is fixedly connected with the first fitting part, and the second fitting part penetrates through the first cavity and extends into the first hole through the first port. The second cavity is communicated with the outside of the plate heat exchanger through the fourth port; the second cavity is communicated with the first hole through the fifth port; in the first hole, the first blocking part extends into the first hole from the edge of the corner hole of one of the multiple plate sheets, and the first blocking part is hermetically connected with the second fitting part; the inter-plate channel is separated into a first inter-plate channel and a second inter-plate channel by the one plate sheet, and the first inter-plate channel is closer to the fitting part than the second inter-plate channel;

[0006] The outer diameter of the part of the second mating portion located in the first duct is smaller than the inner diameter of the first duct. In the first duct, the first blocking portion divides the outer region of the diversion tube into a first flow region and a second flow region. The first flow region communicates with the second duct through the first inter-plate channel, and the first flow region communicates with the first chamber through the first port. The second flow region communicates with the second duct through the second inter-plate channel, and the second flow region communicates with the second chamber through the fifth port.

[0007] By improving the structure of the plate heat exchanger in the present application, the communication between the second port and the fourth port of the plate heat exchanger is realized through the first chamber, the first flow region, the first inter-plate channel, the second duct, the second inter-plate channel, the second flow region, and the second chamber. Furthermore, one of the second port and the fourth port is used as the inlet, and the other is used as the outlet. Moreover, the integrated part is arranged close to the first duct. Correspondingly, the second port and the fourth port are also concentrated and arranged close to the first duct, which is beneficial to optimizing the installation space of the plate heat exchanger. Brief Description of the Drawings

[0008] Figure 1 is a three-dimensional structure schematic diagram of the plate heat exchanger of the present invention;

[0009] Figure 2 of the present invention Figure 1 is a schematic cross-sectional view of the plate heat exchanger shown;

[0010] Figure 3 of the present invention Figure 1 is an exploded view of the plate heat exchanger shown;

[0011] Figure 4 is a schematic diagram of the plate heat exchanger of the present invention making diagonal convection;

[0012] Figure 5 is a schematic diagram of the fixing method of the diversion tube and the first blocking portion of the plate heat exchanger of the present invention;

[0013] Figure 6 is an enlarged schematic diagram of the structure of the fixing method of the fitting and the first side plate of the plate heat exchanger of the present invention;

[0014] Figure 7 is another schematic cross-sectional structure diagram of the plate heat exchanger of the present invention;

[0015] Figure 8 is yet another schematic cross-sectional structure diagram of the plate heat exchanger of the present invention;

[0016] Figure 9 of the present invention Figure 1 is a schematic diagram of the fixing method of the fitting in the plate heat exchanger;

[0017] Figure 10For Figure 9 Schematic diagram of the upper shell structure of the plate heat exchanger;

[0018] Figure 11 For Figure 9 Schematic diagram of the lower shell structure of the plate heat exchanger;

[0019] Figure 12 Schematic diagram of a flow path of the plate heat exchanger of the present invention as an evaporator;

[0020] Figure 13 Another schematic diagram of a flow path of the plate heat exchanger of the present invention as an evaporator;

[0021] Figure 14 Schematic diagram of a flow path of the plate heat exchanger of the present invention as a condenser;

[0022] Figure 15 Another schematic diagram of a flow path of the plate heat exchanger of the present invention as a condenser. Detailed implementation manners

[0023] The plate heat exchanger provided by the present invention optimizes the inlets and outlets of fluids in the plate heat exchanger and cooperates with the two-pass flow channel design in the plate heat exchanger, which is beneficial to optimizing the installation space of the plate heat exchanger and improving the heat exchange effect of the plate heat exchanger. To enable those skilled in the art to better understand the technical solution of the present invention, the present invention will be further described in detail below with reference to the drawings and specific embodiments.

[0024] As Figure 1 , shown in FIGS. 2 and 3, the plate heat exchanger 100 includes a plurality of plate sheets 101. The plate sheets 101 are generally rectangular in shape. Each of the four corners of each plate sheet 101 has a corner hole. The corner holes of the plurality of plate sheets 101 are aligned to form four channels. The plurality of plate sheets 101 are stacked to form a non-connected first flow channel and a second flow channel. The first flow channel includes an inter-plate channel 102, a first channel 103 formed by a corner hole of the plurality of plate sheets 101, and a second channel 104 formed by another corner hole of the plurality of plate sheets 101. The two sides of most of the plate sheets are respectively part of the first flow channel and part of the second flow channel. For the first flow channel, it also includes two of the four channels, that is, the first channel 103 and the second channel 104. The first channel 103 and the second channel 104 are connected through the inter-plate channel 102. Correspondingly, the second flow channel includes the remaining two channels, and these two channels are also connected. Usually, different fluids flow through the first flow channel and the second flow channel respectively. For example, a refrigerant flows through the first flow channel, and a secondary refrigerant flows through the second flow channel.

[0025] The plate heat exchanger 100 further includes an integrated component and a first blocking portion 13. The integrated component includes a mating part 11 and a diversion pipe 12. The mating part 11 includes a first cavity 110 and a first mating portion 114 located outside the first cavity 110. The first mating portion 114 is provided with a first port 111 and a second port 112. The first cavity 110 communicates with the first channel 103 through the first port 111, and the communication between the first cavity 110 and the first channel 103 is a direct communication, that is, one side of the first port 111 is the first cavity 110, and the other side is the first channel 103. The first cavity 110 communicates with the outside of the plate heat exchanger 100 through the second port 112, and the communication between the first cavity 110 and the outside of the plate heat exchanger 100 is also a direct communication, that is, one side of the second port 112 is the first cavity, and the other side is the outside of the plate heat exchanger 100.

[0026] The diversion pipe 12 includes a second cavity 120 and a second mating portion 126 located outside the second cavity 120. The second mating portion 126 is provided with a fourth port 121 and a fifth port 122. The second mating portion 126 is fixedly connected to the first mating portion 114. The second cavity 120 communicates with the outside of the plate heat exchanger 100 through the fourth port 121. The communication between the second cavity 120 and the outside of the plate heat exchanger 100 is also a direct communication, that is, one side of the fourth port 121 is the second cavity 120, and the other side is the outside of the plate heat exchanger 100. Along the stacking direction of the plate 101, reference can be made to Figure 2 the direction indicated by the solid line with double arrows in Figure 2 which the direction is substantially vertical. The second mating portion 126 penetrates through the first cavity 110 and extends into the first channel 103 through the first port 111. The second cavity 120 communicates with the first channel 103 through the fifth port 122, that is, one end of the diversion pipe 12 including the fifth port 122 is located in the first channel 103.

[0027] The second mating portion 126 of the diversion tube 12 penetrates through the first chamber 110. The diversion tube 12 is at least partially located in the first chamber 110. One end of the diversion tube 12 extends into the first duct, and the other end faces the outside of the plate heat exchanger 100. The second mating portion 126 of the diversion tube 12 is fixedly connected in a mating manner with the first mating portion 114 of the mating member 11. The first chamber 110 of the mating member 11 communicates with the first duct 103 through the first port 111. In this way, the first mating portion 114 and the first duct 103 are located on both sides of the first port 111. A part of the second chamber 120 of the diversion tube 12 is located in the first chamber 110. The mating member 11 is equivalent to being sleeved outside the diversion tube 12. Both the first chamber 110 and the second chamber 120 communicate with the first duct 103, which is beneficial to reducing the overall volume of the integrated component, and the entire integrated component is arranged close to the first duct 103. The second port 112 and the fourth port 121 are also concentrated and arranged close to the first duct 103. In this way, the plate heat exchanger 100 can save some space at the position corresponding to the second duct 104, which is beneficial to optimizing the installation space of the entire plate heat exchanger 100. The inlets and outlets of fluids such as refrigerants are integrated together, and the first duct 103 simultaneously realizes the inlet and outlet of the refrigerant. Compared with the first duct 103 being used as the inlet channel, and the second duct 104 being used as the outlet channel, it is beneficial to the integrated installation of the plate heat exchanger 100 with other components, meeting the requirements of system compactness. Moreover, for the mating member 11, the structure of the first mating portion 114 is simple, which is convenient for processing and manufacturing, and is beneficial to reducing the overall volume of the mating member 11.

[0028] In the first duct 103, the first blocking portion 13 extends from the edge of the corner hole of one of the plurality of plate sheets 101 into the first duct 103, and the first blocking portion 13 is hermetically connected to the second mating portion 126; the inter-plate channel 102 is divided into a first inter-plate channel 1021 and a second inter-plate channel 1022 by this one plate sheet. The first inter-plate channel 1021 is closer to the mating member 11 than the second inter-plate channel 1022. The first inter-plate channel 1021 may be the inter-plate channel formed between the uppermost plate sheet and this one plate sheet. The uppermost plate sheet refers to the plate sheet closest to the mating member 11. Correspondingly, the second inter-plate channel 1022 may be the inter-plate channel formed between the lowermost plate sheet and this one plate sheet. The lowermost plate sheet refers to the plate sheet farthest from the mating member 11.

[0029] When the first blocking portion 13 can be manufactured at the corner hole position of one of the plate sheets 101, a small hole can be separately punched at the corresponding corner hole position, that is, at the corner hole position, it is not completely punched according to the corner hole size, and the remaining part of the plate sheet structure can form the first blocking portion 13. The diameter of the punched small hole matches the outer diameter of the part of the second mating portion 126 located in the first duct 103. The first blocking portion 13 can also be a separate component, and it can be fixed integrally with the plate sheet 101 at the corresponding corner hole position by welding or other means.

[0030] The first blocking portion 13 extends into the first channel 103 through the edge of the corner hole of one of the sheet members 101, and the first blocking portion 13 is disposed substantially parallel to the sheet member 101. Along the stacking direction of the sheet members 101, the first inter-sheet channel 1021 is relatively close to the fitting 11, and the second inter-sheet channel 1022 is relatively far from the fitting 11. The fluid flow direction in the first inter-sheet channel 1021 is opposite to the fluid flow direction in the second inter-sheet channel 1022. The fluid realizes one return journey in the first inter-sheet channel 1021 and another return journey in the second inter-sheet channel 1022. In this way, when the volume of the plate heat exchanger 100 is relatively small, the fluid flow path can be effectively increased, ensuring good heat exchange performance of the plate heat exchanger. At the same time, compared with the entire inter-sheet channel, the setting of the two return journeys is beneficial to the distribution of the fluid. Especially for the gas-liquid two-phase refrigerant, it is beneficial to improve the problem of uneven gas-liquid distribution of the refrigerant in the plate heat exchanger.

[0031] The outer diameter L1 of the portion of the second fitting portion 126 located in the first channel 103 is smaller than the inner diameter L2 of the first channel 103. In the first channel 103, the first blocking portion 13 divides the outer region of the guide pipe 12 into a first flow region 123 and a second flow region 124. The first flow region 123 communicates with the second channel 104 through the first inter-sheet channel 1021, and the first flow region 123 communicates with the first cavity 110 through the first port 111. The second flow region 124 communicates with the second channel 104 through the second inter-sheet channel 1022, and the second flow region 124 communicates with the second cavity 120 through the fifth port 122.

[0032] The first flow region 123 and the second flow region 124 are arranged adjacent to each other, and the first flow region 123 is closer to the fitting 11 than the second flow region 124. In the first channel 103, the first flow region 123 is the region where the gap is located between the outer wall of the guide pipe 12 and the inner side of the first channel 103, and the second flow region 124 is the region of the first channel 103 located between the first blocking portion and the second side plate of the plate heat exchanger 100.

[0033] The fixed connection between the second mating part 126 and the first mating part 114 can include various ways, such as integral connection and split assembly fixation. That is to say, the whole of the fitting 11 and the whole of the diversion pipe 12 can be independent components and be integrated into one body during assembly to form an integrated part. The second mating part 126 and the first mating part 114 are fixed by means such as welding, and they will not displace relative to each other. Specifically, the first mating part 114 is also provided with a third port 113. At the third port 113, the outer walls of the first mating part 114 and the second mating part 126 are sealed and welded so that the first cavity 110 is isolated from the outside of the plate heat exchanger 100 at the third port 113. Or the integrated part can be integrally formed, such as by metal casting process, or the integrated part can be integrally formed by injection molding process, etc. In this way, the second mating part 126 and the first mating part 114 are themselves integrally connected components and can be fixedly connected.

[0034] Of course, for the fluid flowing in the second flow channel, such as the ethylene glycol aqueous solution used as a coolant, similar to the first flow channel, the second flow channel can also achieve a two-return flow mode in the plate channel corresponding to the second flow channel through the structural position relationship of similar fitting 11, diversion pipe 12 and first blocking part 13; or still adopt a one-return flow mode. The present invention does not specifically limit the flow mode of the fluid in the second flow channel.

[0035] Furthermore, the plate heat exchanger 100 further includes a first side plate 21 and a second side plate 22. The thicknesses of the first side plate 21 and the second side plate 22 are both greater than the thickness of the plate 101. The first side plate 21 can include a bottom plate and a reinforcing plate welded together, or the first side plate 21 is a thick integral side plate. The relatively thick thickness of the first side plate 21 can improve the welding strength between the first side plate 21 and the outer wall of the fitting 11. The first side plate 21 and the second side plate 22 are fixedly connected to the multiple plates 101 by welding. The welding can be brazing, which is beneficial to improving the strength and reliability of the 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 is coaxially or eccentrically arranged with the first hole 103. Both ends of the second hole 104 are sealed by the first side plate 21 and the second side plate 22, that is, the fluid flowing in the second hole 104 cannot directly communicate with the outside of the plate heat exchanger 100 through the first side plate 21 or the second side plate 22. The second plate hole 212 and the third plate hole 213 are coaxially or eccentrically arranged with the holes formed by the other two corner holes of the multiple plates 101 respectively.

[0036] The plate heat exchanger 100 also includes a first external tube 23 and a second external tube 24. The first external tube 23 is connected to the second flow channel through the second plate hole 212, and the second external tube 24 is connected to the second flow channel through the third plate hole 213. Three plate holes are provided on the first side plate 21, one plate hole is fixed with the fitting 11, and the other two plate holes are fixed with the first external tube 23 and the second external tube 24 respectively. The first external tube 23 and the second external tube 24 are located on one side of the width direction of the plate heat exchanger 100. Alternatively, the first external tube 23 and the second external tube 24 are arranged diagonally, which can be referred to Figure 4 As shown, in this way, the fluid such as refrigerant uses an oblique convection method to optimize the distribution effect on the basis of two returns in the first flow channel, so as to achieve a sufficient heat exchange effect. Figure 4 It is illustrated that the refrigerant flows into the plate heat exchanger from the fourth port 121 and flows out of the plate heat exchanger from the second port 112. Of course, the refrigerant can also flow into the plate heat exchanger from the second port 112 and flow out of the plate heat exchanger from the fourth port 121. The first external pipe 23, the second external pipe 24, and the matching piece 11 and the guide pipe 12 integrated into an integral component can be arranged on the same side of the plate heat exchanger 100, or on different sides based on the installation requirements of the plate heat exchanger 100. For example, the first external pipe 23 and the second external pipe 24 are located on one side of the plate heat exchanger 100, and the matching piece 11 and the guide pipe 12 integrated into an integral component are located on the other side opposite to the plate heat exchanger 100.

[0037] refer to Figure 5 As shown, 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 guide tube 12 extends into the through hole 131, and the flange portion 125' of the first blocking portion 13 is sealed and fixed to the outer wall of the guide tube 12. During manufacturing, the guide tube 12 is pressed into the through hole 131, and an expansion process can be used to expand the diameter of the guide tube 12, thereby eliminating or reducing the gap between the guide tube 12 and the baffle portion 130, thereby improving the sealing performance, or sealing welding can be directly performed on the flange portion 125 and the outer wall of the guide tube 12, etc.

[0038] refer to Figure 6 The structure of the mating piece 11 shown is schematically shown. The mating piece 11 includes a first mating portion 114 located at the periphery of the first cavity 110. The first mating portion 114 includes a first body 115 and a protrusion 116 connected to the first body 115 and extending along the stacking direction of the plate 101. The protrusion 116 includes a first boss 1161 and a second boss 1162 connected to each other. The first boss 1161 is closer to the first channel 103 than the second boss 1162. The first port 111 is located at the end of the first boss 1161 away from the first body 115. Figure 6In terms of the schematic view direction, the first port 111 is located on the bottom side of the protrusion 116. The protrusion 116 has a first notch 117. In a direction perpendicular to the stacking direction of the sheet 101, Figure 6 As shown by the solid line with double arrows, this direction is generally horizontal. The first notch 117 is adjacent to the first boss 1161, and the first notch 117 is farther from the diversion pipe 12 than the first boss 1161. The existence of the first notch 117 makes the outer wall of the protrusion 116 in a stepped shape. At the first notch 117, the first side plate 21 is welded and fixed to the outer wall of the protrusion 116. The first body 115 is spaced from the first side plate 21 through the second boss 1162. In this way, the heat exchange core part of the plate heat exchanger 100 and the fitting 11 can be fixed through the protrusion 116 and the first side plate 21, and the first body 115 and the first side plate 21 do not directly contact each other, which is beneficial to reducing the pressure of the first body 115 on the heat exchange core part of the plate heat exchanger 100, and further beneficial to reducing the influence of the fitting 11 on the flow resistance of the fluid in the plate heat exchanger 100 in the inter-plate channel, and can improve the heat exchange effect of the plate heat exchanger 100.

[0039] Reference Figure 7 As shown, for the fitting 11, the fitting 11 can be an integrally formed part. 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 plate includes a plate surface 210. The plate surface 210 is generally a plane. The plate surface 210 is the end surface of the first side plate away from the sheet. The first top surface 1151 and the first bottom surface are a set of opposite end surfaces parallel or substantially parallel to the plate surface 210 of the first side plate 21. The first top surface 1151 is farther from the sheet 101 than the first bottom surface. In Figure 7 it, the first top surface 1151 is the uppermost end surface of the fitting 11. There is a gap between the first bottom surface and the plate surface 210 of the first side plate 21. The first side surface 1152 is connected to the first top surface 1151. The first side surface 1152 can be as Figure 7The end face shown in the middle is perpendicular or substantially perpendicular to the first side plate 21. The first side face 1152 can also be an inclined end face. The first top face 1151 of the fitting 11 can be substantially rectangular. Correspondingly, the first side face is also correspondingly rectangular, or the first top face 1151 is substantially oval or oval-like, and the first side face is correspondingly an arc face. The specific shape of the fitting 11 is not specifically limited in this application. The third port 113 is located on the first top face 1151. The third port 113 is coaxially or eccentrically arranged with the first port 111. The second port 112 is located on the first side face 1152. In this way, since the diversion pipe 12 needs to be hermetically connected to the fitting 11 at the third port 113, correspondingly, the fourth port 121 is arranged close to the first top face 1151. In this way, the fourth port 121 and the second port 112 are arranged in different directions, which is convenient for processing and manufacturing, and the volume of the fitting 11 can be further reduced. Moreover, the fourth port 121 and the second port 112 are arranged in different directions, so that when the ports are connected to the pipes, mutual interference can be reduced, which is beneficial to optimizing the installation space of the plate heat exchanger 100.

[0040] Similar to Figure 7 the structure shown, refer to Figure 8 As shown, the second port 112 and the third port 113 are also located on the first top face 1151. The first cavity 110 includes a first sub-cavity 1101 and a second sub-cavity 1102 that are connected and communicate with each other. The first sub-cavity 1101 communicates with the first duct 103 through the first port 111, and the second sub-cavity 1102 extends obliquely from the second port 112 towards the first sub-cavity 1101. The rectangular-structured fitting 11 is relatively easy to process. The first sub-cavity 1101 and the second sub-cavity 1102 can be manufactured by machining and other processes, that is, the first sub-cavity 1101 and the second sub-cavity 1102 can have a relatively straight channel center line, which is convenient for processing and manufacturing. Moreover, the second sub-cavity 1102 extends obliquely from the second port 112 towards the first sub-cavity 1101, and the fluid flows smoothly in the second sub-cavity 1102, and the flow path is short, which is beneficial to reducing the flow resistance and improving the heat exchange performance.

[0041] Of course, the fitting 11 can also be formed by splicing parts. Refer to Figure 9 、 Figure 10 、 Figure 11As shown, the fitting 11 includes an upper housing 33 and a lower housing 44 manufactured by stamping, machining or other means. The upper housing 33 includes a first sub - part 331 and a second sub - part 332 connected to each other. The first sub - part 331 is farther from the plate 101 than the second sub - part 332. The fitting 11 further includes a first channel 333 and a second channel 334 passing through the first sub - part 331. One end of the first channel 333 away from the second sub - part 332 forms a third port 113, and one end of the second channel 334 away from the second sub - part 332 forms a second port 112. The fitting 11 further includes a third channel 335 passing through the second sub - part 332. In a plane perpendicular to the stacking direction of the plate 101, the projections of the first channel 333 and the second channel 334 are both within the projection range of the third channel 335, which is convenient for machining the upper housing.

[0042] The lower housing 44 includes a protruding part 116 and a third sub - part 441 connected to the protruding part 116. The third sub - part 441 is farther from the plate 101 than the protruding part 116. The fitting 11 further includes a fourth channel 442 passing through the third sub - part 441. The fourth channel 442 communicates with the cavity surrounded by the protruding part 116. The inner diameter of the fourth channel 442 is greater than or equal to the inner diameter of the protruding part 116. The first through - hole 333, the fourth channel 442, and the protruding part 116 are coaxially arranged or eccentrically arranged. 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 plate 101. The first groove 443 communicates with the fourth channel 442. In a plane perpendicular to the stacking direction of the plate 101, the projection of the first groove 443 and the projection of the second channel 334 at least partially overlap. In this way, when the upper housing 33 and the lower housing 44 are spliced, the first groove 443 communicates with the second through - hole 334 through the third channel 335. Fluids can flow into the third channel 335 through the first groove 443 and then into the second channel 334, or flow from the second channel 334 into the third channel 335 and then into the first groove 443. Among them, the upper housing 33 and the lower housing 44 are fixedly welded through the opposite side surfaces between the second sub - part 332 and the third sub - part 441, and the upper housing 33 and the lower housing 44 are welded into an integral part.

[0043] Reference Figure 9Schematic diagram of the installation structure of the diversion pipe 12 and the fitting 11 shown. The diversion pipe 12 includes a second fitting portion 126 located outside the second cavity 120. Along the stacking direction of the plate 101, the second fitting portion 126 includes a second body 127 and a third boss 129. Along the stacking direction of the plate 101, both ends of the second body 127 form a fourth port 121 and a fifth port 122 respectively. 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 near the fourth port 121 is larger than the outer diameter of the portion of the second body 127 near the fifth port 122. The outer diameter of the portion of the second body 127 near the fourth port 121 matches the inner diameter of the first channel 333, facilitating the welding between the fitting 11 and the diversion pipe 12 at the first channel 333.

[0044] The third boss 129 is connected to the second body 127 and extends in a direction substantially perpendicular to the stacking of the plate 101. The second fitting portion 126 has a second notch 1261. Along the stacking direction of the plate 101, the second notch 1261 is adjacent to the third boss 129, and the second notch 1261 is closer to the plate 101 than the third boss 129. At the second notch 1261, the first fitting portion 114 is hermetically welded to the outer wall of the second fitting portion 126.

[0045] By hermetically sealing the first fitting portion 114 and the outer wall of the second fitting portion 126 at the second notch 1261, the first cavity 110 cannot communicate with the outside of the plate heat exchanger 100 through the third port 113, and the sealing area between the first fitting portion 114 and the second fitting portion 126 is relatively large, which can improve the sealing reliability. Further, due to the third boss 129, the second fitting portion 126 protrudes from the end face of the first body 115 away from the plate 101. When installing with a throttling component such as an electronic expansion valve, the electronic expansion valve can be sleeved on the outer periphery of the third boss 129 and directly installed with the electronic expansion valve through mechanical connection or other means.

[0046] Based on the structure of the plate heat exchanger 100 described above, in one embodiment, refer to Figure 12 , when the plate heat exchanger 100 is used as an evaporator, correspondingly, the first flow channel is for the circulation of the refrigerant, the second flow channel is for the circulation of the coolant, the fourth port 121 is used as the refrigerant inlet, the second port 112 is used as the refrigerant outlet, the number of channels in the first inter-plate channel 1021 is greater than the number of channels in the second inter-plate channel 1022. When the channel sizes and structures formed by the plate structure of the plate heat exchanger 100 are basically similar, reference can be made to Figure 12 shown, that is, along the stacking direction of the plate 101, the height H1 of the heat exchange section formed by the first inter-plate channel 1021 is greater than the height H2 of the heat exchange section formed by the second inter-plate channel 1022.

[0047] When the plate heat exchanger 100 is used as an evaporator, the refrigerant in the gas-liquid two-phase state enters the second chamber 120 from the fourth port 121, and then flows out of the second chamber 120 from the fifth port 122 and enters the second flow area 124. Then, it passes through the second inter-plate channel 1022, enters the second channel 104, then enters the first flow area 123 through the first inter-plate channel 1021, and then enters the first chamber 110 through the first port 111, and finally flows out of the plate heat exchanger 100 in the gas phase or gas-liquid two-phase state from the second port 112. The flow direction of the refrigerant in the heat exchange section formed by the first inter-plate channel 1021 is from the second channel 104 to the first channel 103, and the flow direction of the refrigerant in the heat exchange section formed by the second inter-plate channel 1022 is from the first channel 103 to the second channel 104. The flow path design of the two return trips increases the flow path of the refrigerant. The refrigerant in the gas-liquid two-phase state flowing in the first flow channel exchanges heat with the coolant flowing in the second flow channel. Since the specific gravity of the gaseous refrigerant gradually increases when the gas-liquid two-phase refrigerant exchanges heat in the first flow channel, and the number of channels in the first inter-plate channel 1021 is greater than that in the second inter-plate channel 1022. On the one hand, the number of channels in the heat exchange section formed by the second inter-plate channel 1022 is smaller, which is more conducive to solving the problem of uneven distribution of the refrigerant in each channel. On the other hand, the proportion of the first inter-plate channel 1021 in the total inter-plate channels is larger, so there will be no large pressure drop loss, which is conducive to the rapid outflow of the refrigerant with an increasing gaseous specific gravity from the plate heat exchanger 100, improving the heat transfer coefficient of the refrigerant, and ultimately improving the heat exchange effect of the plate heat exchanger 100.

[0048] In another embodiment, refer to Figure 13 As shown, when the plate heat exchanger 100 is used as an evaporator, correspondingly, the first flow channel is for the circulation of the refrigerant, the second flow channel is for the circulation of the coolant, the second port 112 is used as the inlet of the refrigerant, the fourth port 121 is used as the outlet of the refrigerant, and the number of channels in the first inter-plate channel 1021 is less than that in the second inter-plate channel 1022. When the channel dimensions and structures formed by the plate structure of the plate heat exchanger 100 are basically similar, refer to Figure 13 As shown, along the stacking direction of the plate 101, the height H1 of the heat exchange section formed by the first inter-plate channel 1021 is less than the height H2 of the heat exchange section formed by the second inter-plate channel 1022.

[0049] When the plate heat exchanger 100 is used as an evaporator, the refrigerant in the gas-liquid two-phase state enters the first chamber 110 from the second port 112, then flows out of the first chamber 110 from the first port 111 and enters the first flow region 123, then passes through the first inter-plate channel 1021, enters the second channel 104, then enters the second flow region 124 through the second inter-plate channel 1022, then enters the second chamber 120 through the fifth port 122, and finally flows out of the plate heat exchanger 100 from the fourth port 121 in a gaseous state or a gas-liquid two-phase state. The flow direction of the refrigerant in the heat exchange section formed by the first inter-plate channel 1021 is from the first channel 103 to the second channel 104, and the flow direction of the refrigerant in the heat exchange section formed by the second inter-plate channel 1022 is from the second channel 104 to the first channel 103. The flow path design of the two return trips increases the flow path of the refrigerant. The refrigerant in the gas-liquid two-phase state flowing in the first flow path exchanges heat with the coolant flowing in the second flow path. Since the specific gravity of the gaseous refrigerant gradually increases when the gas-liquid two-phase refrigerant exchanges heat in the first flow path, and the number of channels in the second inter-plate channel 1022 is greater than the number of channels in the first inter-plate channel 1021. On the one hand, the number of channels in the heat exchange section formed by the first inter-plate channel 1021 is small, which is more conducive to solving the problem of uneven distribution of the refrigerant in each channel. On the other hand, the proportion of the second inter-plate channel 1022 in the total inter-plate channels is large, so there will be no large pressure drop loss, which is conducive to the rapid outflow of the refrigerant with an increasing gaseous specific gravity from the plate heat exchanger 100, improving the heat transfer coefficient of the refrigerant, and ultimately improving the heat exchange effect of the plate heat exchanger 100.

[0050] In yet another embodiment, referring to Figure 14 as shown, when the plate heat exchanger 100 is used as a condenser, the first flow path is for the circulation of the refrigerant, the second flow path is for the circulation of the coolant, the fourth port 121 is used as the inlet of the refrigerant, the second port 112 is used as the outlet of the refrigerant, and the number of channels in the first inter-plate channel 1021 is less than the number of channels in the second inter-plate channel 1022. When the channel dimensions and structures formed by the plate structure of the plate heat exchanger 100 are basically similar, reference can be made to Figure 14 as shown. Along the stacking direction of the plate 101, the height H1 of the heat exchange section formed by the first inter-plate channel 1021 is less than the height H2 of the heat exchange section formed by the second inter-plate channel 1022.

[0051] When the plate heat exchanger 100 is used as a condenser, the 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 region 124. Then, it passes through the second inter-plate channel 1022, enters the second orifice 104, then enters the first flow region 124 through the first inter-plate channel 1021, and then enters the first chamber 110 from 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. The flow direction of the refrigerant in the heat exchange section formed by the first inter-plate channel 1021 is from the second orifice 104 towards the first orifice 103, and the flow direction of the refrigerant in the heat exchange section formed by the second inter-plate channel 1022 is from the first orifice 103 towards the second orifice 104. The gaseous refrigerant enters from the fourth port 121 and flows in the first flow path, exchanging heat with the coolant flowing in the second flow path and condensing into a liquid. The flow path design of the two return trips increases the flow path of the refrigerant. And in order to enable the refrigerant to still have a good degree of subcooling at the outlet of the relatively small-sized plate heat exchanger 100, that is, the second port 112, the number of channels in the second inter-plate channel 1022 is greater than the number of channels in the first inter-plate channel 1021, which helps with the flow rate distribution of the refrigerant and achieves a better heat exchange effect.

[0052] In yet another embodiment, referring to Figure 15 as shown, when the plate heat exchanger 100 is used as a condenser, the first flow path is for the flow of the refrigerant, the second flow path is for the flow of the coolant, the second port 112 is used as the inlet of the refrigerant, the fourth port 121 is used as the outlet of the refrigerant, and the number of channels in the first inter-plate channel 1021 is greater than the number of channels in the second inter-plate channel 1022. When the channel dimensions and structures formed by the plate structure of the plate heat exchanger 100 are basically similar, reference can be made to Figure 14 as shown. Along the stacking direction of the plate 101, the height H1 of the heat exchange section formed by the first inter-plate channel 1021 is greater than the height H2 of the heat exchange section formed by the second inter-plate channel 1022.

[0053] When the plate heat exchanger 100 is used as a condenser, the single-phase gaseous refrigerant enters the first chamber 110 from the second port 112, then flows out of the first chamber 110 from the first port 111 and enters the first flow area 123, then passes through the first inter-plate channel 1021, enters the second channel 104, then enters the second flow area 124 through the second inter-plate channel 1022, then enters the second chamber 120 through the fifth port 122, and finally flows out of the plate heat exchanger 100 from the fourth port 121 in a single-phase liquid state. The flow direction of the refrigerant in the heat exchange section formed by the first inter-plate channel 1021 is from the first channel 103 to the second channel 104, and the flow direction of the refrigerant in the heat exchange section formed by the second inter-plate channel 1022 is from the second channel 104 to the first channel 103. The gaseous refrigerant enters from the second port 112 and flows in the first flow path, exchanging heat with the coolant flowing in the second flow path and condensing into a liquid state. The flow path design of the two return trips increases the flow path of the refrigerant. In order to ensure that the refrigerant still has a good degree of subcooling at the outlet of the plate heat exchanger 100 with a small size, that is, the second port 112, the number of channels in the first inter-plate channel 1021 is greater than the number of channels in the second inter-plate channel 1022, which helps with the flow rate distribution of the refrigerant and achieves a better heat exchange effect.

[0054] The above has introduced the plate heat exchanger provided by the present invention in detail. Specific examples are used in this article to elaborate on the principle and implementation manner of the present invention. The description of the above embodiments is only used to help understand the core idea of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the protection scope of the claims of the present invention.

Claims

1. A plate heat exchanger, comprising a plurality of plate sheets, wherein the plurality of plate sheets are stacked to form a first flow channel and a second flow channel that are not connected and communicated with each other. The first flow channel includes an inter-plate channel, a first channel formed by a corner hole of the plurality of plate sheets, and a second channel formed by another corner hole of the plurality of plate sheets. The plate heat exchanger further includes an integrated part and a first blocking part. The integrated part includes a fitting part and a diversion pipe. The fitting part includes a first cavity and a first fitting part located outside 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 channel through the first port, and the first cavity is communicated with the outside of the plate heat exchanger through the second port. The diversion pipe includes a second cavity and a second fitting part located outside the second cavity. The second fitting part is provided with a fourth port and a fifth port. The second fitting part is fixedly connected to the first fitting part, and the second fitting part penetrates through the first cavity and extends into the first channel through the first port. The second cavity is communicated with the outside of the plate heat exchanger through the fourth port. The second cavity is communicated with the first channel through the fifth port. In the first channel, the first blocking part extends into the first channel from the edge of a corner hole of one of the plurality of plate sheets, and the first blocking part is hermetically connected to the second fitting part. The inter-plate channel is separated into a first inter-plate channel and a second inter-plate channel by the one plate sheet. The first inter-plate channel is closer to the fitting part than the second inter-plate channel. The outer diameter of the part of the second fitting part located in the first channel is smaller than the inner diameter of the first channel. In the first channel, the first blocking part divides the outer region of the diversion pipe into a first flow region and a second flow region. The first flow region is communicated with the second channel through the first inter-plate channel, and the first flow region is communicated with the first cavity through the first port. The second flow region is communicated with the second channel through the second inter-plate channel, and the second flow region is communicated with the second cavity through the fifth port. The plate heat exchanger includes a first side plate. The first fitting part includes a first body and a convex part connected to the first body and extending in the plate sheet stacking direction. The convex part includes a first boss and a second boss connected to each other. The first boss is closer to the first channel than the second boss. The first port is located at the end of the first boss away from the first body. The convex part has a first notch. In a direction perpendicular to the plate sheet stacking direction, the first notch is adjacent to the first boss, and the first notch is farther from the diversion pipe than the first boss. At the first notch, the first side plate is welded and fixed to the outer wall of the convex part, and the first body is spaced from the first side plate through the second boss.

2. The plate heat exchanger according to claim 1, characterized in that, The plate heat exchanger further includes a first side plate and a second side plate. The first side plate has a first plate hole, a second plate hole, and a third plate hole. The first plate hole is coaxially or eccentrically arranged with the first duct. Both ends of the second duct are sealed by the first side plate and the second side plate. The second plate hole and the third plate hole are respectively coaxially or eccentrically arranged with the ducts formed by the other two corner holes of the multiple plates. The plate heat exchanger further includes a first external connecting pipe and a second external connecting pipe. The first external connecting pipe communicates with the second flow channel through the second plate hole, and the second external connecting pipe communicates with the second flow channel through the third plate hole.

3. The plate heat exchanger according to claim 2, wherein, The first external connecting pipe and the second external connecting pipe are located on 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 according to any one of claims 1 to 3, characterized in that, The first fitting portion is further provided with a third port. At the third port, the first fitting portion is hermetically welded to the outer wall of the second fitting portion so that the first cavity is isolated from the outside of the plate heat exchanger at the third port.

5. The plate heat exchanger according to claim 4, characterized in that, Along the stacking direction of the plates, the second fitting portion includes a second body and a third boss. Along the stacking direction of the plates, the two ends of the second body respectively form the fourth port and the fifth port. The fourth port is farther from the plates than the fifth port. The third boss is connected to the second body and extends in a direction substantially perpendicular to the stacking direction of the plates. The second fitting portion has a second notch. Along the stacking direction of the plates, the second notch is adjacent to the third boss, and the second notch is closer to the plates than the third boss. At the third port, the first fitting portion is hermetically welded to the outer wall of the second fitting portion through the second notch.

6. The plate heat exchanger according to claim 5, wherein The fitting 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 opposite end surfaces parallel or substantially parallel to the plate surface of the first side plate. The first top surface is farther from the plates than the first bottom surface. The first side surface connects the first top surface and the first bottom surface. The third port is located on the first top surface. The third port is coaxially or eccentrically arranged with the first port. The second port is located on the first side surface; or the second port is also located on the first top surface. The first cavity includes a first sub-cavity and a second sub-cavity that are connected. The first sub-cavity communicates with the first duct through the first port, and the second sub-cavity extends obliquely from the second port towards the first sub-cavity.

7. The plate heat exchanger according to claim 5, wherein, The fitting includes an upper housing and a lower housing. The upper housing includes a first sub - part and a second sub - part connected to each other. The first sub - part is farther from the plate than the second sub - part. The fitting further includes a first channel and a second channel penetrating through the first sub - part. One end of the first channel away from the second sub - part forms the third port, and one end of the second channel away from the second sub - part forms the second port. The fitting also includes a third channel penetrating through the second sub - part. In a plane perpendicular to the lamination direction of the plates, the projections of the first channel and the second channel are both within the projection range of the third channel. The lower housing includes the convex part and a third sub - part connected to the convex part. The third sub - part is farther from the plate than the convex part. The fitting further includes a fourth channel penetrating through the third sub - part. The inner diameter of the fourth channel is greater than or equal to the inner diameter of the convex part. The first channel, the fourth channel, and the convex part are coaxially arranged or eccentrically arranged. The lower housing also has a first groove extending from the fourth channel in a direction perpendicular to the lamination direction of the plates. In a plane perpendicular to the lamination direction of the plates, the projection of the first groove at least partially coincides with the projection of the second channel. The upper housing and the lower housing are fixedly welded through the opposite side surfaces between the second sub - part and the third sub - part.

8. The plate heat exchanger according to claim 7, wherein The plate heat exchanger is an evaporator. The first flow channel is for the circulation of the refrigerant. The fourth port serves as the inlet of the refrigerant, and the second port serves as the outlet of the refrigerant. The number of channels in the first inter - plate channel is greater than the number of channels in the second inter - plate channel. Alternatively, the second port serves as the inlet of the refrigerant, the fourth port serves as the outlet of the refrigerant, and the number of channels in the first inter - plate channel is less than the number of channels in the second inter - plate channel.

9. The plate heat exchanger according to claim 7, characterized in that, The plate heat exchanger is a condenser. The first flow channel is for the circulation of the refrigerant. The fourth port serves as the inlet of the refrigerant, and the second port serves as the outlet of the refrigerant. The number of channels in the first inter - plate channel is less than the number of channels in the second inter - plate channel. Alternatively, the second port serves as the inlet of the refrigerant, the fourth port serves as the outlet of the refrigerant, and the number of channels in the first inter - plate channel is greater than the number of channels in the second inter - plate channel.

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