Plate heat exchanger with high and low non-equivalent heat transfer areas

Abstract

The utility model relates to a plate heat exchanger with high and low non-equivalent heat transfer areas, and belongs to the field of plate heat exchangers. The heat exchange plate is divided into a medium inlet area, a medium middle area, a medium outlet area, a medium inlet near-end area and a medium inlet middle-end area which serve as high flow resistance areas, and the medium inlet far-end area serves as a low flow resistance area. The medium middle area is a high-resistance area; the medium outlet area is divided into a medium outlet near-end area, a medium outlet middle-end area and a medium outlet far-end area, and the medium outlet near-end area and the medium outlet middle-end area serve as high-flow-resistance areas; and the medium outlet far-end area is a low flow resistance area. The high flow resistance design is adopted in the area with the short medium flow path, the low flow resistance design is adopted in the area with the long medium flow path, and therefore media are evenly laid on the heat exchange plates between the corner holes and the medium middle area, the flow speed and flow of the media are averaged, circulation dead zones are reduced, and the overall heat transfer efficiency is improved.

Description

Technical Field

[0001] The utility model relates to a brazing plate heat exchanger, belonging to the technical field of heat exchangers. Background Art

[0002] Brazed plate heat exchanger plates are thin metal sheets with corrugations, corner holes, and flanges pressed into them. They serve as the heat transfer element of the heat exchanger. The corrugations not only enhance heat transfer but also increase the strength and rigidity of the plates, thereby improving the pressure-bearing capacity of the brazed plate heat exchanger. Furthermore, by promoting turbulent flow, they can reduce the formation of sediment or dirt.

[0003] The corrugation of plate heat exchangers can be divided into herringbone corrugation, oblique corrugation, horizontal straight corrugation, spherical corrugation, vertical corrugation, etc. According to the geometric shape, the main parameters for measuring the performance of corrugated plates are heat transfer efficiency, fluid resistance, distribution and diffusion capacity, and pressure bearing capacity.

[0004] When the angle between the medium flow direction and the plate corrugation is greater than 60°, the plate corrugation is at a large angle, and the medium flows with high turbulence, high heat transfer efficiency, and high pressure drop.

[0005] When the angle between the medium flow direction and the plate corrugation is 40-60°, the plate corrugation is at a medium angle, and the medium flows with medium turbulence, medium heat exchange efficiency, and medium pressure drop.

[0006] When the angle between the medium flow direction and the plate corrugation is less than 40°, the plate corrugation is at a small angle, and the medium flows with low turbulence, low heat transfer efficiency and low pressure drop.

[0007] Different areas of a plate heat exchanger have different requirements for plate corrugation. For example, the media inlet area requires the corrugation to distribute the media throughout the heat exchange plate, the intermediate area requires high heat transfer efficiency, and the media outlet area requires uniform collection of the media at the outlet. Therefore, using the same plate corrugation pattern cannot meet the requirements of each area. Summary of the Invention

[0008] The technical problem to be solved by the present invention is to provide a plate heat exchanger with high and low unequal heat transfer areas in response to the above-mentioned existing technology, divide the heat exchange plate into areas according to the flow characteristics of the medium, and set different plate corrugation angles in different areas according to the flow direction of the medium and the heat exchange requirements.

[0009] The technical solution adopted by the present invention to solve the above-mentioned problem is: a plate heat exchanger with high and low unequal heat transfer areas, including a front plate and a rear plate, a plurality of heat exchange plates and copper foils stacked in sequence are provided between the front plate and the rear plate, the heat exchange plates are brazed to form a flow channel for medium circulation, the medium inlet area and the medium outlet area are respectively provided with corner holes, and the heat exchange surface of the heat exchange plate is divided into a medium inlet area, a medium middle area, and a medium outlet area in the direction of the vertical center line, characterized in that:

[0010] The medium inlet area is divided into a proximal area of ​​the medium inlet, a middle area of ​​the medium inlet, and a distal area of ​​the medium inlet. The distal area of ​​the medium inlet is divided into a distal transverse area of ​​the medium inlet, a distal rounded corner area of ​​the medium inlet, and a distal vertical area of ​​the medium inlet. The angle A1 between the plate corrugation and the vertical centerline in the proximal area of ​​the medium inlet and the middle area of ​​the medium inlet is greater than 60°, indicating a high flow resistance area; the angle A2 between the plate corrugation and the transverse centerline of the lower corner hole in the distal transverse area of ​​the medium inlet is less than 30°, indicating a low flow resistance area; the angle A3 between the plate corrugation and the vertical centerline in the distal vertical area of ​​the medium inlet is less than 40°, indicating a low flow resistance area;

[0011] The angle A4 between the plate corrugation and the vertical centerline in the middle area of ​​the medium is greater than 60°, which is a high resistance area;

[0012] The medium outlet area is divided into a proximal area of ​​the medium outlet, a middle area of ​​the medium outlet, and a distal area of ​​the medium outlet, wherein the distal area of ​​the medium outlet is divided into a distal transverse area of ​​the medium outlet, a distal rounded corner area of ​​the medium outlet, and a distal vertical area of ​​the medium outlet. The angle A5 between the plate corrugation and the vertical center line in the proximal area of ​​the medium outlet and the middle area of ​​the medium outlet is greater than 60°, which is a high flow resistance area; the angle A6 between the plate corrugation and the transverse center line of the upper corner hole in the distal transverse area of ​​the medium outlet is less than 30°, which is a low flow resistance area; the angle A7 between the plate corrugation and the vertical center line in the distal vertical area of ​​the medium outlet is less than 40°, which is a low flow resistance area.

[0013] As one of the preferred embodiments of the present application, the media inlet proximal region and the media inlet middle region are respectively composed of multiple parallel oblique corrugations, and the oblique corrugations in the two regions are connected and are both located above the horizontal center line of the lower corner hole.

[0014] As one of the preferred embodiments of the present application, the media outlet proximal region and the media outlet middle region are respectively composed of multiple parallel oblique corrugations, and the oblique corrugations in the two regions are connected and are both located below the horizontal center line of the upper corner hole.

[0015] As one of the preferred embodiments of the present application, the distal transverse region of the medium inlet is composed of a plurality of parallel oblique corrugations and is located below the transverse centerline of the lower corner hole.

[0016] As one of the preferred embodiments of the present application, the distal transverse region of the medium outlet is composed of a plurality of parallel oblique corrugations, which are located above the transverse centerline of the upper corner hole.

[0017] As one of the preferred embodiments of the present application, the fillet area at the distal end of the medium inlet is composed of multiple non-parallel oblique corrugations, located between the corner hole and the fillet of the heat exchange plate where the corner hole is located, and the angle B between the center lines of adjacent oblique corrugations is equal, and the angle B is 9-11°; the intersection of the extension line of the center line of the oblique corrugation and the fillet of the heat exchange plate and the connecting line of the center of the corner hole respectively forms an angle of less than 40° with the corresponding center line of the oblique corrugation, and the fillet area at the distal end of the medium inlet is a low flow resistance area.

[0018] As one of the preferred embodiments of the present application, the fillet area at the distal end of the medium outlet is composed of multiple non-parallel oblique corrugations, located between the corner hole and the fillet of the heat exchange plate where the corner hole is located, and the angle D between the center lines of adjacent oblique corrugations is equal, and the angle D is 9-11°; the intersection of the extension line of the center line of the oblique corrugation and the fillet of the heat exchange plate and the connecting line of the center of the corner hole respectively forms an angle of less than 40° with the corresponding center line of the oblique corrugation; the fillet area at the distal end of the medium inlet is a low flow resistance area.

[0019] Compared with the prior art, the advantages of the present invention are: this application mainly focuses on the circulation characteristics of the medium on the heat exchange plate, and divides the medium inlet area into the medium inlet proximal area, the medium inlet middle area, and the medium inlet distal area. These three areas are mainly divided according to the circulation distance of the medium. The medium inlet proximal area and the medium inlet middle area with a shorter circulation distance are redesigned as a high flow resistance circulation structure, and the medium inlet distal area with a longer circulation distance is designed as a low flow resistance circulation structure, thereby achieving the average of the medium flow rate and flow from the inlet corner hole to the middle area of ​​the medium, which helps to improve the heat transfer efficiency. The design of the medium outlet area is also based on the same principle. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 This is a front view of a plate heat exchanger in an embodiment of the present utility model;

[0021] Figure 2 This is a side view of a plate heat exchanger in an embodiment of the present utility model;

[0022] Figure 3 for Figure 2 The middle AA cross-sectional view shows the entire area of ​​the heat exchange plate;

[0023] Figure 4 Schematic diagram of the medium flow direction of the heat exchange plate in the embodiment of the present utility model;

[0024] Figure 5 The corrugated structure of the medium inlet area of ​​the heat exchange plate in the embodiment of the present utility model;

[0025] Figure 6 The corrugated structure of the medium outlet area of ​​the heat exchange plate in the embodiment of the present utility model;

[0026] Figure 7 Schematic diagram of the angle B between the center lines of adjacent oblique corrugations in the rounded corner area R5 at the far end of the medium inlet in an embodiment of the present invention;

[0027] Figure 8 Schematic diagram of the angles formed by the intersection of the extended line of the center line of the oblique corrugation in the fillet area R5 at the far end of the medium inlet, the fillet of the heat exchange plate, the connecting line of the center of the corner hole, and the corresponding center line of the oblique corrugation in the embodiment of the present invention;

[0028] Figure 9 Schematic diagram of the angle D between the center lines of adjacent oblique corrugations in the rounded corner area S5 at the distal end of the medium outlet in an embodiment of the present invention;

[0029] Figure 10 Schematic diagram of the angles formed by the intersection of the extended line of the center line of the oblique corrugation in the fillet area S5 at the far end of the medium outlet, the fillet of the heat exchange plate, the connecting line of the center of the corner hole, and the corresponding center line of the oblique corrugation in the embodiment of the present invention;

[0030] In the figure, 1 is the front end plate, 2 is the rear end plate, 3 is the heat exchange plate, 4 is the medium inlet area, 5 is the medium middle area, 6 is the medium outlet area, 7 is the corner hole, the vertical center line y, the horizontal center line x, the horizontal center line x'' of the lower corner hole, the horizontal center line x' of the upper corner hole, the proximal area R1 of the medium inlet, the middle area R2 of the medium inlet, the distal transverse area R3 of the medium inlet, the distal rounded corner area R5 of the medium inlet, the distal vertical area R4 of the medium inlet, the proximal area S1 of the medium outlet, the middle area S2 of the medium outlet, the distal transverse area S3 of the medium outlet, the distal rounded corner area S5 of the medium outlet, and the distal vertical area S4 of the medium outlet. DETAILED DESCRIPTION

[0031] The present invention is further described in detail below in conjunction with the accompanying drawings. The embodiments described are exemplary and intended to explain the present invention, but should not be construed as limiting the present invention. The textual descriptions in the embodiments correspond to the accompanying drawings, and the descriptions of the directions are also based on the descriptions of the accompanying drawings, and should not be construed as limiting the scope of protection of the present invention.

[0032] like Figure 1As shown, a plate heat exchanger with high and low unequal heat transfer areas in this embodiment includes a front end plate 1 and a rear end plate 2. A plurality of heat exchange plates 3 and copper foils are provided between the front end plate 1 and the rear end plate 2. The heat exchange plates 3 are brazed to form a flow channel for medium circulation. The heat exchange plate 3 is rectangular and has four rounded corners. The heat exchange plate 3 has four corner holes 7, which are respectively located at the four rounded corners of the heat exchange plate 3. The heat exchange plate 3 is divided into a medium inlet area 4, a medium middle area 5, and a medium outlet area 6. The medium inlet corner holes are located in the medium inlet area, the medium outlet corner holes are located in the medium outlet area, and the medium middle area is located between the medium inlet area and the medium outlet area.

[0033] The media inlet region 4 is divided into the media inlet proximal region R1, the media inlet mid-region R2, and the media inlet distal region. The distal region is further divided into the media inlet distal transverse region R3, the media inlet distal transverse region R4, and the media inlet distal rounded corner region R5. The media inlet proximal region R1 and the media inlet mid-region R2 are each composed of multiple parallel oblique corrugations. The oblique corrugations in these two regions are connected and located above the transverse centerline x'' of the lower corner hole. The angle A1 between the oblique corrugations and the vertical centerline y is greater than 60°, indicating a high-efficiency, high-flow resistance region. The media inlet distal transverse region R3 is composed of multiple parallel oblique corrugations and located below the transverse centerline x'' of the lower corner hole. The angle A2 between the oblique corrugations and the transverse centerline x'' of the lower corner hole is less than 30°, indicating a low-efficiency, low-flow resistance region. The vertical area R4 at the far end of the medium inlet is composed of multiple parallel oblique corrugations and is located above the horizontal center line x'' of the lower corner hole. The angle A3 between the oblique corrugations and the vertical center line y is less than 40°, which is a low-efficiency and low-flow resistance area.

[0034] The angle between the oblique corrugations in the middle area 5 of the medium and the vertical center line y is greater than 60°, which is a high-efficiency heat exchange area.

[0035] The media outlet area 6 is divided into a proximal media outlet area S1, a mid-media outlet area S2, and a distal media outlet area. The distal media outlet area is further divided into a distal transverse media outlet area S3, a distal rounded corner area S5, and a distal vertical media outlet area S4. The proximal media outlet area S1 and the mid-media outlet area S2 each consist of multiple parallel oblique corrugations. The oblique corrugations in these two areas are connected and located below the transverse centerline x' of the upper corner hole. The angle A5 between the oblique corrugations and the vertical centerline is greater than 60°, indicating a high-efficiency, high-flow resistance area. The distal transverse media outlet area S3, composed of multiple parallel oblique corrugations, lies above the transverse centerline x' of the upper corner hole. The angle A6 between the oblique corrugations and the transverse centerline x' is less than 30°, indicating a low-efficiency, low-flow resistance area. The vertical area S4 at the far end of the medium outlet is composed of multiple parallel oblique corrugations and is located below the horizontal centerline x' of the upper corner hole. The angle A7 between the oblique corrugations and the vertical centerline y is less than 40°, which is a low-efficiency and low-flow resistance area.

[0036] The far-end rounded corner area R5 of the medium inlet is composed of multiple non-parallel oblique corrugations, located between the corner hole 7 and the rounded corner of the plate, and is radial. Figure 7 As shown, the included angle B between the center lines of adjacent oblique corrugations is equal, and the included angle B is between 9-11°.

[0037] like Figure 8 As shown, the intersection of the extension line of the oblique corrugation center line and the rounded corner of the plate and the center connection line of the corner hole respectively form an angle C1-C7 with the corresponding oblique corrugation center line. The angle C1-C7 is less than 40°, and this area is a low-efficiency and low-flow resistance area.

[0038] The far end rounded corner area S5 of the medium outlet is composed of multiple non-parallel oblique corrugations, located between the corner hole 7 and the rounded corner of the plate, and is radial. Figure 9 As shown, the included angle D between the center lines of adjacent oblique corrugations is equal and is between 9-11°. Figure 10 As shown, the intersection of the extension line of the oblique corrugation center line and the rounded corner of the plate and the center connection line of the corner hole respectively form an angle E1-E7 with the corresponding oblique corrugation center line. The angle E1-E7 is less than 40°, and this area is a low-efficiency and low-flow resistance area.

[0039] In a plate heat exchanger with this structure, the media flow path length is shortest in the areas near the media inlet and in the middle of the media inlet, resulting in greater flow resistance. The media flow path is longer and less resistive in the area distal to the media inlet. This ensures that the media is evenly distributed across the heat exchange plates as it passes through the media inlet and enters the middle area, averaging the media flow rate and flow rate, reducing dead zones, and ultimately improving overall heat transfer efficiency.

[0040] The media flow path length near the outlet and in the middle of the outlet is shorter, resulting in greater flow resistance. The media flow path in the distal outlet is longer, resulting in less flow resistance. This allows the media to flow evenly through these three areas and into the plate corner holes, averaging the media flow velocity and flow rate, reducing dead zones, and ultimately improving overall heat transfer efficiency.

[0041] In addition to the above embodiments, the present invention also includes other implementation methods. Any technical solutions formed by equivalent transformation or equivalent replacement should fall within the scope of protection of the claims of the present invention.

Claims

1. A plate heat exchanger with high and low unequal heat transfer areas, comprising a front plate and a rear plate, with a plurality of sequentially spaced and stacked heat exchange plates and copper foil disposed between the front and rear plates. The heat exchange plates are brazed to form flow channels for medium circulation, with corner holes provided in the medium inlet and outlet regions, respectively. The heat exchange surface of the heat exchange plates is divided into a medium inlet region, a medium intermediate region, and a medium outlet region along the vertical centerline. The characteristics of the plate heat exchanger are: The medium inlet area is divided into a proximal area of ​​the medium inlet, a middle area of ​​the medium inlet, and a distal area of ​​the medium inlet. The distal area of ​​the medium inlet is divided into a distal transverse area of ​​the medium inlet, a distal rounded corner area of ​​the medium inlet, and a distal vertical area of ​​the medium inlet. The angle A1 between the plate corrugation and the vertical centerline in the proximal area of ​​the medium inlet and the middle area of ​​the medium inlet is greater than 60°, indicating a high flow resistance area; the angle A2 between the plate corrugation and the transverse centerline of the lower corner hole in the distal transverse area of ​​the medium inlet is less than 30°, indicating a low flow resistance area; the angle A3 between the plate corrugation and the vertical centerline in the distal vertical area of ​​the medium inlet is less than 40°, indicating a low flow resistance area; The angle A4 between the plate corrugation and the vertical centerline in the middle area of ​​the medium is greater than 60°, which is a high resistance area; The medium outlet area is divided into a proximal area of ​​the medium outlet, a middle area of ​​the medium outlet, and a distal area of ​​the medium outlet, wherein the distal area of ​​the medium outlet is divided into a distal transverse area of ​​the medium outlet, a distal rounded corner area of ​​the medium outlet, and a distal vertical area of ​​the medium outlet. The angle A5 between the plate corrugation and the vertical center line in the proximal area of ​​the medium outlet and the middle area of ​​the medium outlet is greater than 60°, which is a high flow resistance area; the angle A6 between the plate corrugation and the transverse center line of the upper corner hole in the distal transverse area of ​​the medium outlet is less than 30°, which is a low flow resistance area; the angle A7 between the plate corrugation and the vertical center line in the distal vertical area of ​​the medium outlet is less than 40°, which is a low flow resistance area.

2. The plate heat exchanger according to claim 1, characterized in that: The media inlet proximal region and the media inlet middle region are respectively composed of a plurality of parallel oblique corrugations. The oblique corrugations in the two regions are connected and are both located above the horizontal center line of the lower corner hole.

3. The plate heat exchanger according to claim 1, characterized in that: The media outlet proximal region and the media outlet middle region are respectively composed of a plurality of parallel oblique corrugations. The oblique corrugations in the two regions are connected and are both located below the horizontal center line of the upper corner hole.

4. The plate heat exchanger according to claim 1, characterized in that: The transverse area at the distal end of the medium inlet is composed of a plurality of parallel oblique corrugations and is located below the transverse center line of the lower corner hole.

5. The plate heat exchanger according to claim 1, characterized in that: The transverse area at the distal end of the medium outlet is composed of a plurality of parallel oblique corrugations and is located above the transverse center line of the upper corner hole.

6. The plate heat exchanger according to claim 1, characterized in that: The fillet area at the far end of the medium inlet is composed of multiple non-parallel oblique corrugations, located between the corner hole and the fillet of the heat exchange plate where the corner hole is located. The angle B between the center lines of adjacent oblique corrugations is equal, and the angle B is 9-11°; the intersection of the extension line of the center line of the oblique corrugation and the fillet of the heat exchange plate and the connecting line of the center of the corner hole respectively forms an angle of less than 40° with the corresponding center line of the oblique corrugation. The fillet area at the far end of the medium inlet is a low flow resistance area.

7. The plate heat exchanger according to claim 1, characterized in that: The rounded corner area at the far end of the medium outlet is composed of multiple non-parallel oblique corrugations, located between the corner hole and the rounded corner of the heat exchange plate where the corner hole is located. The angle D between the center lines of adjacent oblique corrugations is equal, and the angle D is 9-11°; the intersection of the extended line of the oblique corrugation center line and the rounded corner of the heat exchange plate and the connecting line of the center of the corner hole respectively forms an angle of less than 40° with the corresponding oblique corrugation center line; the rounded corner area at the far end of the medium inlet is a low flow resistance area.

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