Plate heat exchanger with high and low non-equivalent heat transfer areas
By dividing different areas on the brazed plate heat exchanger and designing appropriate plate corrugation angles, the problem of unbalanced heat transfer efficiency and fluid resistance in the prior art is solved, and the uniformity of the medium flow rate and flow rate and heat transfer are achieved. Improved performance.
Patent Information
- Application Number
- CN202411397064.X
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-10-09
- Publication Date
- 2025-02-18
AI Technical Summary
The existing brazed plate heat exchangers have different requirements for plate corrugation in different areas, which cannot meet the requirements of medium circulation characteristics, resulting in uneven heat transfer efficiency and fluid resistance.
By dividing different areas on the heat exchange plate, different plate corrugation angles are set according to the medium flow direction and heat exchange requirements, including the medium inlet area and outlet area, and are designed as high flow resistance and low flow resistance areas respectively to achieve the dielectric flow rate and Uniformity of flow.
Through area division and corrugation angle design, the uniformity of the medium flow rate and flow rate is achieved, the overall heat transfer efficiency is improved, and the flow dead zone is reduced.
Smart Images
Figure CN119468755A_ABST
Abstract
Description
Technical Field
[0001] The invention relates to a brazed plate heat exchanger and belongs to the technical field of heat exchangers. Background Art
[0002] The brazed plate heat exchanger plate is a metal sheet with corrugations, corner holes and flanges, which is the heat transfer element of the heat exchanger. The corrugations can not only enhance heat transfer, but also increase the strength and rigidity of the sheet, thereby improving the pressure bearing capacity of the brazed plate heat exchanger, and because the fluid is turbulent, it can reduce the formation of sediment or dirt.
[0003] The corrugation form of plate heat exchanger can be divided into herringbone corrugation, oblique corrugation, horizontal straight corrugation, spherical corrugation, vertical corrugation, etc. According to the geometric shape, the main parameters to measure the performance of corrugated plate 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 exchange 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 exchange efficiency and low pressure drop.
[0007] In a plate heat exchanger, different areas have different requirements for plate corrugation. For example, in the medium inlet area, the plate corrugation is required to spread the medium all over the heat exchange plate, the medium middle area is required to have high heat transfer efficiency, and the medium outlet area is required to collect the medium evenly at the outlet. Therefore, the same plate corrugation form 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 prior art, 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 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, comprising a front plate and a rear plate, a plurality of heat exchange plates and copper foils stacked in sequence are arranged 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: 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, wherein 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 center line in the proximal area of the medium inlet and the middle area of the medium inlet is greater than 60°, which is a high flow resistance area; the angle A2 between the plate corrugation and the transverse center line of the lower corner hole in the distal transverse area of the medium inlet is less than 30°, which is a low flow resistance area; the angle A3 between the plate corrugation and the vertical center line in the distal vertical area of the medium inlet is less than 40°, which is 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 lateral area of the medium outlet, a distal rounded corner area of the medium outlet, and a distal vertical area of the medium outlet. An 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; an angle A6 between the plate corrugation and the horizontal center line of the upper corner hole in the distal lateral area of the medium outlet is less than 30°, which is a low flow resistance area; an 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.
[0010] 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 a plurality of parallel oblique corrugations, the oblique corrugations in the two regions are connected, and both are located above the horizontal center line of the lower corner hole.
[0011] 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 a plurality of parallel oblique corrugations, the oblique corrugations in the two regions are connected, and both are located below the horizontal center line of the upper corner hole.
[0012] As one of the preferred embodiments of the present application, the lateral region at the distal end of the medium inlet is composed of a plurality of parallel oblique corrugations and is located below the lateral center line of the lower corner hole.
[0013] As one of the preferred embodiments of the present application, the lateral region at the distal end of the medium outlet is composed of a plurality of parallel oblique corrugations, which are located above the lateral center line of the upper corner hole.
[0014] As one of the preferred embodiments of the present application, the fillet area at the far end of the medium inlet is composed of a plurality of non-parallel oblique corrugations, which are located between the corner hole and the fillet of the heat exchange plate where the corner hole is located, and the center lines of adjacent oblique corrugations have an equal included angle B of 9-11°; the connecting line of the intersection of the extended line of the center line of the oblique corrugation and the fillet of the heat exchange plate and the center of the corner hole respectively forms an angle less than 40° with the corresponding center line of the oblique corrugation, and the fillet area at the far end of the medium inlet is a low flow resistance area.
[0015] As one of the preferred embodiments of the present application, the fillet area at the far end of the medium outlet is composed of a plurality of non-parallel oblique corrugations, which are located between the corner hole and the fillet of the heat exchange plate where the corner hole is located, and the center lines of adjacent oblique corrugations have an equal included angle D of 9-11°; the connecting line of the intersection of the extended line of the center line of the oblique corrugation and the fillet of the heat exchange plate and the center of the corner hole respectively forms an angle 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.
[0016] Compared with the prior art, the advantages of the present invention are as follows: the present application mainly focuses on the flow characteristics of the medium on the heat exchange plate, and divides the medium inlet area into a proximal area of the medium inlet, a middle area of the medium inlet, and a distal area of the medium inlet. The three areas are mainly divided according to the flow distance of the medium. The proximal area of the medium inlet and the middle area of the medium inlet with a shorter flow distance are redesigned as a flow structure with a high flow resistance, and the distal area of the medium inlet with a longer flow distance is designed as a flow structure with a low flow resistance, thereby achieving the average of the medium flow velocity and flow rate from the inlet corner hole to the middle area of the medium, which is helpful 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
[0017] Figure 1 This is a front view of a plate heat exchanger in an embodiment of the present invention; Figure 2 A side view of a plate heat exchanger in an embodiment of the present invention; Figure 3 for Figure 2 The middle AA section view shows the whole area of the heat exchange plate; Figure 4 Schematic diagram of medium flow direction of heat exchange plates in an embodiment of the present invention; Figure 5 The corrugated structure of the medium inlet area of the heat exchange plate in the embodiment of the present invention; Figure 6 The corrugated structure of the medium outlet area of the heat exchange plate in the embodiment of the present invention; 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; Figure 8 Schematic diagram of the angles formed by the extension line of the center line of the oblique corrugation in the fillet area R5 at the far end of the medium inlet in the embodiment of the present invention, the intersection of the fillet of the heat exchange plate and the connecting line of the center of the corner hole and the corresponding center line of the oblique corrugation; Fig. 9 Schematic diagram of the angle D between the center lines of adjacent oblique corrugations in the rounded corner area S5 at the far end of the medium outlet in an embodiment of the present invention; Fig.10 Schematic diagram of the angles formed by the extension line of the center line of the oblique corrugation in the fillet area S5 at the far end of the medium outlet in the embodiment of the present invention, the intersection of the fillet of the heat exchange plate and the connecting line of the center of the corner hole and the corresponding center line of the oblique corrugation; 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 lateral area R3 of the distal end of the medium inlet, the rounded area R5 of the distal end of the medium inlet, the vertical area R4 of the distal end of the medium inlet, the proximal area S1 of the medium outlet, the middle area S2 of the medium outlet, the lateral area S3 of the distal end of the medium outlet, the rounded area S5 of the distal end of the medium outlet, and the vertical area S4 of the distal end of the medium outlet. DETAILED DESCRIPTION
[0018] The present invention is further described in detail below in conjunction with the accompanying drawings. The embodiments are exemplary and are intended to be used to explain the present invention, but should not be understood as limiting the present invention. The text description in this embodiment corresponds to the accompanying drawings, and the description of the orientation is also based on the description of the accompanying drawings, which should not be understood as limiting the scope of protection of the present invention.
[0019] like Figure 1 As 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 stacked in sequence are arranged 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, and the four corner holes 7 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 hole is located in the medium inlet area, the medium outlet corner hole is located in the medium outlet area, and the medium middle area is located between the medium inlet area and the medium outlet area.
[0020] The medium inlet area 4 is divided into the medium inlet proximal area R1, the medium inlet middle area R2, and the medium inlet distal area, wherein the medium inlet distal area is divided into the medium inlet distal transverse area R3, the medium inlet distal transverse area R4, and the medium inlet distal rounded area R5. The medium inlet proximal area R1 and the medium inlet middle area R2 are respectively composed of a plurality of parallel oblique corrugations, the oblique corrugations of the two areas are connected, and both are located above the horizontal center line x'' of the lower corner hole, and the angle A1 between the oblique corrugation and the vertical center line y is greater than 60°, which is a high efficiency and high flow resistance area. The medium inlet distal transverse area R3 is composed of a plurality of parallel oblique corrugations, located below the horizontal center line x'' of the lower corner hole, and the angle A2 between the oblique corrugation and the horizontal center line x'' of the lower corner hole is less than 30°, which is a low efficiency and low flow resistance area. The vertical region 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 region.
[0021] The angle between the oblique corrugation 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.
[0022] The medium outlet area 6 is divided into the medium outlet proximal area S1, the medium outlet middle area S2, and the medium outlet distal area, wherein the medium outlet distal area is divided into the medium outlet distal transverse area S3, the medium outlet distal rounded area S5, and the medium outlet distal vertical area S4. Among them, the medium outlet proximal area S1 and the medium outlet middle area S2 are respectively composed of a plurality of parallel oblique corrugations, the oblique corrugations of the two areas are connected, and both are located below the horizontal center line x' of the upper corner hole, and the angle A5 between the oblique corrugation and the vertical center line is greater than 60°, which is a high-efficiency and high-flow resistance area. The medium outlet distal transverse area S3 is composed of a plurality of parallel oblique corrugations, located above the horizontal center line x' of the upper corner hole, and the angle A6 between the oblique corrugation and the horizontal center line x' of the upper corner hole is less than 30°, which is a low-efficiency and 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 center line x' of the upper corner hole. The angle A7 between the oblique corrugations and the vertical center line y is less than 40°, which is a low efficiency and low flow resistance area.
[0023] The far-end rounded corner area R5 of the medium inlet is composed of a plurality of non-parallel oblique corrugations, which are located between the corner hole 7 and the rounded corner of the plate and are 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°.
[0024] like Figure 8 As shown, the intersection of the extension line of the oblique corrugation centerline and the fillet of the plate and the center connection line of the corner hole respectively form an angle C1-C7 with the corresponding oblique corrugation centerline, and the angle C1-C7 is less than 40°, and this area is a low efficiency and low flow resistance area.
[0025] The far-end rounded corner area S5 of the medium outlet is composed of a plurality of non-parallel oblique corrugations, located between the corner hole 7 and the rounded corner of the plate, and is radial. Fig. 9 As shown, the included angle D of the center lines of adjacent oblique corrugations is equal, and the included angle D is between 9-11°. Fig.10 As shown, the intersection of the extension line of the oblique corrugation centerline and the fillet of the plate and the center connection line of the corner hole respectively form an angle E1-E7 with the corresponding oblique corrugation centerline, and the angle E1-E7 is less than 40°, and this area is a low efficiency and low flow resistance area.
[0026] In the plate heat exchanger with the above structure, the medium flow length in the medium inlet near-end area and the medium inlet middle-end area is the shortest, and the flow resistance is relatively large. The medium flow length in the medium inlet far-end area is long, and the flow resistance is relatively small. As a result, the medium passes through the medium inlet area and is evenly spread on the heat exchange plate when entering the medium middle area, averaging the medium flow velocity and flow rate, reducing the circulation dead zone, and thus improving the overall heat transfer efficiency.
[0027] The medium flow length in the near-end area and the middle-end area of the medium outlet is short, and the flow resistance is large. The medium flow in the far-end area of the medium outlet is long, and the flow resistance is small. As a result, the medium passes through the three areas and enters the corner holes of the plate evenly, averaging the medium flow velocity and flow, reducing the circulation dead zone, and thus improving the overall heat transfer efficiency.
[0028] In addition to the above embodiments, the present invention also includes other implementation modes. Any technical solutions formed by equivalent transformation or equivalent replacement should fall within the protection scope 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, a plurality of heat exchange plates and copper foils stacked in sequence are arranged 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: 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, wherein 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 center line in the proximal area of the medium inlet and the middle area of the medium inlet is greater than 60°, which is a high flow resistance area; the angle A2 between the plate corrugation and the transverse center line of the lower corner hole in the distal transverse area of the medium inlet is less than 30°, which is a low flow resistance area; the angle A3 between the plate corrugation and the vertical center line in the distal vertical area of the medium inlet is less than 40°, which is 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 lateral area of the medium outlet, a distal rounded corner area of the medium outlet, and a distal vertical area of the medium outlet. An 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; an angle A6 between the plate corrugation and the horizontal center line of the upper corner hole in the distal lateral area of the medium outlet is less than 30°, which is a low flow resistance area; an 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 far 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 far 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 a plurality of non-parallel oblique corrugations, which are located between the corner hole and the fillet of the heat exchange plate where the corner hole is located. The center lines of adjacent oblique corrugations have an equal included angle B, which is 9-11°. The connecting line of the intersection of the extended line of the center line of the oblique corrugation and the fillet of the heat exchange plate and the center of the corner hole respectively forms an included 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 fillet area at the far end of the medium outlet is composed of a plurality of non-parallel oblique corrugations, which are located between the corner hole and the fillet of the heat exchange plate where the corner hole is located. The center lines of adjacent oblique corrugations have an equal included angle D, which is 9-11°; the intersection of the extended 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 form an included 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.