CN106197095B - Heat exchanger - Google Patents
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- CN106197095B CN106197095B CN201510233528.8A CN201510233528A CN106197095B CN 106197095 B CN106197095 B CN 106197095B CN 201510233528 A CN201510233528 A CN 201510233528A CN 106197095 B CN106197095 B CN 106197095B
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Abstract
The invention discloses a heat exchanger, which improves the fluidity of fluid in the middle part by forming at least one third flow channel near a bending part with more welding points in a main heat exchange area, prevents larger welding points from being formed at the bending part, ensures that the fluid is more uniformly distributed in the heat exchanger, improves the heat exchange performance of the heat exchanger, and can realize miniaturization of the heat exchanger.
Description
Technical Field
The invention relates to the technical field of heat exchange, in particular to a plate type heat exchanger.
Background
A plate heat exchanger is defined as a heat exchanger in which the heat transfer element consists of flow-through plates, which are the core components thereof, of the usual plate types: chevron corrugations, horizontal flat corrugations, spherical corrugations, oblique corrugations, vertical corrugations, and the like, with chevron corrugated sheets being the most widely used. In order to enhance the heat exchange effect of the plate heat exchanger, people continuously research and develop and improve the structure of the circulating plate.
Compared with the traditional heat exchanger, the plate type heat exchanger has a very compact structure; the aluminum alloy is made of multi-purpose aluminum alloy materials, and is very light; and meanwhile, the plate heat exchanger has high efficiency due to the high heat conductivity of the circulating plate. Therefore, the plate heat exchanger has strong adaptability and can be used for heat exchange among various fluids and phase change heat exchange with aggregation change; different heat exchange working conditions such as counter flow, cross flow, multi-flow and multi-pass flow can be adapted through the arrangement and combination of the flow channels; the heat exchange requirement of large-scale equipment can be met through the combination of series connection, parallel connection and series-parallel connection among the units.
At present, plate heat exchangers are widely applied to the fields of air separation plants, petrochemical industry, refrigeration and low-temperature fields, automobile and aviation industry and the like.
With the increasing use requirements of heat exchangers, the heat exchange performance of plate heat exchangers needs to be further enhanced. The plate heat exchanger is required to be structurally optimized to obtain the plate heat exchanger with higher processing qualified rate, lower production cost and stronger heat exchange performance.
However, the phenomenon of uneven distribution of fluid in an internal channel commonly exists in the existing plate heat exchanger, so that the effective heat exchange area of the plate is reduced, namely the utilization rate of the plate is lower.
Therefore, how to effectively solve the problem of uneven distribution of the fluid in the internal channel of the heat exchanger is a technical problem which needs to be solved urgently in the field.
Disclosure of Invention
In order to solve the technical problems in the prior art, the invention provides a heat exchanger which can effectively solve the technical problems.
The invention provides a heat exchanger, which comprises a heat exchanger core body, wherein the heat exchanger core body comprises a plurality of first circulation plates and a plurality of second circulation plates which are arranged at intervals in a stacking mode, a first circulation channel and a second circulation channel which are arranged at intervals are formed between each first circulation plate and each second circulation plate, at least two first orifices and at least two second orifices are respectively arranged on the first circulation plates and the second circulation plates, the middle parts of the first circulation plates and the second circulation plates are main heat exchange areas, each main heat exchange area comprises a plate plane and a plurality of herringbone corrugated bulges which are distributed at certain intervals, each herringbone corrugated bulge protrudes out of the plate plane at certain intervals, pits are formed in corresponding areas on the back surfaces of the plates, and each herringbone corrugated bulge comprises at least one bending part;
on the heat exchanger core, at least one of the chevron corrugated protrusions of the second flow plate is not in contact with a plate plane on the opposite face of two adjacent first flow plates near a bend, at least one of the chevron corrugated protrusions of the second flow plate is opposite a dimple on the opposite face of the first flow plate near a bend, and a third flow channel is formed between at least one of the bends of adjacent first and second flow plates.
The chevron corrugation lobes of at least 2/3 of the second flow-through plate are opposite to the dimples on the opposite face of the adjacent first flow-through plate near the bend, and the remaining chevron corrugation lobes of the second flow-through plate are in contact with the plate flat on the opposite face of the adjacent first flow-through plate near the bend to form weld points.
The first circulation plate and the second circulation plate are plates with the same shape and structure, and on the heat exchanger core, the first circulation plate is rotated 180 degrees relative to the second circulation plate;
the plate sheet comprises a plate plane and a flanging surrounding the plate plane, the first hole is positioned at two corners of the plate plane, and bosses protruding out of the plate plane by a certain height are respectively formed at the other two corners of the plate plane: the first boss and the second boss are provided with pits which are recessed from the plane of the plate for a certain distance at corresponding positions on the reverse side of the plate, and the second hole is formed on the boss;
at least one side of the upper side area and the lower side area of the main heat exchange area of the first circulation plate and/or the second circulation plate is provided with a flow guide area, the flow guide area is positioned between two adjacent first orifices and second orifices, and the flow guide area is provided with at least one special-shaped bulge; the edge of the boss adjacent to the special-shaped protrusion keeps a certain distance with the end part of the special-shaped protrusion, the minimum distance between the edge of the boss adjacent to the special-shaped protrusion and the end part of the special-shaped protrusion is d1, the edge of the boss adjacent to the special-shaped protrusion keeps a certain distance with the end part of the herringbone corrugated protrusion, the minimum distance between the edge of the boss adjacent to the special-shaped protrusion and the end part of the herringbone corrugated protrusion is d2, d2 is larger than or equal to 1mm and smaller than or equal to d1, and a long and narrow flow channel is formed on the edge of the boss adjacent to the special-shaped protrusion;
the aspect ratio of the first flow plate to the second flow plate is not more than 3 and not more than 0.6.
The plate comprises a second area and a third area which are positioned at the upper side and the lower side of the plate, and further comprises a first area positioned between the second area and the third area, wherein the first area is the main heat exchange area, and the second area and the third area are the flow guide areas; the second area is provided with at least one first special-shaped bulge which protrudes out of the plate plane for a certain distance, and the third area is provided with at least one second special-shaped bulge which protrudes out of the plate plane for a certain distance;
the edge of the first boss adjacent to the second region is respectively kept at a certain distance from the first special-shaped bulge and the corrugated bulge to form a long and narrow first flow passage;
the edge of the second boss adjacent to the third area keeps a certain distance with the second special-shaped bulge and the corrugated bulge respectively to form a long and narrow second flow passage.
The included angle of the special-shaped bulge is larger than that of the corrugated bulge, and the included angle of the special-shaped bulge is offset towards a certain angle of the first orifice side relative to the included angle of the corrugated bulge;
and by taking a vertical line passing through the vertex of the special-shaped convex included angle as a boundary, the special-shaped convex included angle is divided into an included angle a1 close to the second orifice and an included angle a2 close to the first orifice, a2 is not less than a1, and a2 is not more than 90.
The second area comprises a plurality of special-shaped bulges, included angles are formed on the special-shaped bulges and the corrugated bulges respectively, the included angles of the special-shaped bulges are larger than those of the corrugated bulges, and the included angles of the special-shaped bulges are offset towards a certain angle of the first orifice side relative to the included angles of the corrugated bulges;
and a vertical line passing through the vertex of the special-shaped protrusion included angle is taken as a boundary, the special-shaped protrusion included angle is divided into an included angle a1 close to the second orifice and an included angle a2 close to the first orifice, the closer the special-shaped protrusion is to the first area, the smaller the included angle of the special-shaped protrusion is, in the direction towards the first area, the same a1 is on each special-shaped protrusion, and the a2 is gradually decreased.
The third area is provided with at least one second special-shaped protrusion protruding from the plate plane for a certain distance, the height of the second special-shaped protrusion is approximately the same as that of the second boss, and the end part of the second special-shaped protrusion keeps a certain distance with the edge of the first hole and the second boss which are adjacent to each other.
The convex included angle of the second special-shaped is larger than the convex included angle of the corrugation, and the convex included angle of the second special-shaped is offset towards a certain angle of the first orifice side relative to the convex included angle of the corrugation.
And the included angle of the second special-shaped protrusion is divided into an included angle a3 close to the second hole opening and an included angle a4 close to the first hole opening by taking a vertical line passing through the vertex of the included angle of the second special-shaped protrusion as a boundary, and the included angle a4 is greater than or equal to the included angle a3, and the included angle a4 is greater than or equal to 90 degrees and is greater than or equal to a3+90 degrees.
The third region comprises a plurality of the second shaped protrusions, and the angle of the included angle a3 on each of the second shaped protrusions is the same in the direction toward the first region, and the angle of the included angle a4 increases. .
According to the heat exchanger provided by the invention, the at least one third flow channel is formed near the bent part with more welding points in the main heat exchange area, so that the fluidity of the fluid in the middle part is improved, the larger welding points are prevented from being formed at the bent part, the fluid is uniformly distributed in the heat exchanger, the heat exchange performance of the heat exchanger is improved, and the heat exchanger can be miniaturized.
Drawings
Fig. 1 is a schematic perspective view of a heat exchanger according to an embodiment of the present invention.
Fig. 2 is a schematic view of a plate structure in the heat exchanger core of the heat exchanger shown in fig. 1.
Fig. 3 is a partial schematic view of the plate shown in fig. 2.
Fig. 4 is another partial schematic view of the plate shown in fig. 2.
Fig. 5 is a further partial schematic view of the plate of fig. 2.
Figure 6 is a schematic cross-sectional view at a-a of two adjacent panels of figure 2 after assembly.
Fig. 7 is a schematic view of the fluid flow path on the plate shown in fig. 2.
Fig. 8 is a perspective schematic view of two adjacent panels of fig. 2 after assembly.
Detailed Description
The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.
Fig. 1 is a schematic perspective view of an embodiment of a heat exchanger according to the present invention, as shown in fig. 1, in the embodiment, the heat exchanger includes a heat exchanger core 6, an end plate 5, and a first external connection pipe 1, a second external connection pipe 2, a third external connection pipe 3, and a fourth external connection pipe 4.
The heat exchanger core 6 comprises a plurality of first circulation plates and a plurality of second circulation plates which are arranged in a stacked mode at intervals, a first circulation channel and a second circulation channel which are arranged at intervals are formed between each first circulation plate and each second circulation plate, and the first circulation channel and the second circulation channel are not communicated with each other. The heat exchanger core 6 is formed by installing a plurality of first circulation plates and a plurality of second circulation plates which are arranged at intervals in a stacked mode in a matched mode. Further, in order to increase the turbulence performance of the fluid in the first flow channel and the second flow channel, the first flow channel and the second flow channel adopt a concave-convex structure formed with corrugations or dimples.
Further, in order to reduce the cost, the first flow plate and the second flow plate are the plate pieces 20 with the same shape and structure, and when the plate pieces are stacked, the first flow plate is rotated 180 degrees relative to the second flow plate for stacking. For ease of understanding, the following description will be made only with reference to the plate 20.
As shown in the drawings, the plate 20 includes a plate plane 21 and a flange 22 surrounding the plate plane, two first openings 26 are formed at two corners of the plate plane 21, and bosses protruding from the plate plane 21 by a certain height are respectively formed at the other two corners of the plate plane 21: the first boss 281 and the second boss 282, correspondingly, form a recess recessed from the plate plane by a certain distance on the reverse side of the plate 20. A second aperture 27 is formed in each boss. Wherein the direction in which the projection projects from the plate plane 21 is opposite to the direction in which the flange 22 projects from the plate plane 21. The side of the plate with the boss is defined as the front side, and the other side is the back side.
The plate 20 further comprises a second area 24 and a third area 25 on the upper and lower sides of the plate 20, and a first area 23 in the middle of the plate 20, wherein the second area 24 and the third area 25 are located between the first aperture 26 and the second aperture 27, and the first area 23 is located between the second area 24 and the third area 25. The first zone is a main heat exchange zone, and the second zone and the third zone can be flow guide zones.
The first region 23 is formed with a plurality of corrugated protrusions 231 projecting a distance from the plane 21 of the plate and, correspondingly, recesses recessed a distance from the plane of the plate are formed in the opposite side of the plate 20. Further, the corrugated protrusion 231 is a herringbone corrugated protrusion including a curved portion 232, wherein two herringbone edges of the herringbone corrugated protrusion 231 form an included angle Y. To improve the heat exchange performance of the heat exchanger, the chevron-shaped corrugated protrusion 231 extends to the intersection of the plate plane 21 and the flange 22, thereby providing a larger heat exchange area between two adjacent plates 20 and allowing a uniform flow of fluid at the edge portions of the plates. The chevron-shaped corrugated protrusions 231 are arranged at a predetermined distance from each other, and plate planes 21 through which fluid flows are formed between the chevron-shaped corrugated protrusions 231.
Further, the width d4 of each chevron-shaped corrugated protrusion 231 on the first region 23 is substantially the same, and the height of the protrusion of the corrugated protrusion 231 from the plate plane 21 is the same as the height of the protrusion of the boss 28 from the plate plane 21.
As shown in fig. 8, when two adjacent plates are stacked together, a fluid channel for fluid to flow is formed between the adjacent plates 20, the fluid channel includes a plate plane of the first region 23 on the front surface of the plate 20 and a concave pit on the back surface, and the contact position of the corrugated protrusion on the first region 23 and the plate plane of the back surface of the adjacent plate 20 can be fixed by welding to form a welding spot.
As shown in fig. 3 and 4, at least one first profile-shaped protrusion 241 protruding from the plate plane 21 by a certain distance is formed on the second region 24, and correspondingly, a recess recessed from the plate plane by a certain distance is formed on the other side of the plate 20. Further, the height of the first shaped protrusion 241 protruding from the plate plane 21 is substantially the same as the height of the first boss 281 protruding from the plate plane 21.
The first shaped protrusion 241 is located between the first porthole 26 and the second porthole 27 on the same side of the plate 20, and the ends of the first shaped protrusion 241 are at a distance from the edges of the first porthole 26 and the first boss 281, respectively, so that a part of the fluid can flow from the first porthole 26 to the area at the edge of the first boss 281, guided by the first shaped protrusion 241.
Specifically, the first irregular protrusion 241 includes at least two protrusions, each of which may be linear or curved, and the protrusions are connected to form the first irregular protrusion 241. The first shaped protrusion 241 composed of the protrusions may be fitted approximately by two straight lines to form an included angle X, which is defined as the included angle X of the first shaped protrusion 241. And the included angle X of the first special-shaped protrusion 241 is located on the bending portion thereof, and the included angle X is larger than the included angle Y of the herringbone corrugated protrusion 231 on the bending portion, the opening orientation of the included angle X is substantially the same as the opening orientation of the included angle Y, and the included angle X has a certain angle offset towards the first orifice 26 side relative to the included angle Y. In this way, the fluid flowing out of the first holes 26 can flow more smoothly through the plate plane 21 between the first special-shaped protrusions 241 to the plate plane area near the edge of the boss 28, so as to improve the distribution uniformity of the fluid and improve the heat exchange performance of the heat exchanger.
Moreover, the two ends of the first special-shaped protrusion 241 are respectively located at the two sides of the bending part 232, which is more beneficial to guiding the fluid to be evenly distributed.
Further, the included angle X of the first shaped protrusion 241 may be divided into two parts by a perpendicular line passing through the vertex of the included angle X, the included angle a1 is close to the second orifice 27, the included angle a2 is close to the first orifice, the included angle a2 is greater than or equal to the included angle a1, and the included angle a2 is less than or equal to 90 °. Therefore, the flow guiding performance of the first special-shaped protrusion 241 can be improved, fluid can smoothly flow to the area near the edge of the boss 28, the fluid is uniformly distributed, and the heat exchange performance of the heat exchanger is improved. Furthermore, the perpendicular line passing through the top point of the included angle X also passes through the top point of the included angle Y, and further, the perpendicular line passing through the top point of the included angle X is located near the central part of the plate 20, so that the heat exchange area of the heat exchanger is reasonably distributed, and the heat exchange performance of the heat exchanger is better.
Further, the second region 24 includes at least two first shaped protrusions 241, and the included angle on the first shaped protrusion 241 is smaller as it is closer to the first region 23. Further, the second region 24 includes a plurality of first shaped protrusions 241, the included angle a1 on each first shaped protrusion 241 has the same angle, the included angle a2 decreases in the direction toward the first region 23, and the included angle a2 away from the first region 23 may be greater than 90 °.
In order to make the fluid passing through the second region 24 smoothly flow to the first region 23 along the region near the edge of the first boss 281, at least a certain distance d1 is kept between the edge of the first boss 281 and the end of the first irregular protrusion 241 on the second region 24, and a plate plane 21 for the fluid flow is formed between the edge of the first boss 281 and the second region 24, wherein d1 is defined as the minimum distance value between the edge of the first boss 281 and the end of the first irregular protrusion 241 on the second region 24. Further, at least a certain distance d2 is kept between the edge of the first boss 281 and the herringbone corrugated protrusions 231 on the first region 23, so that a plate plane 21 for fluid flow is formed between the edge of the first boss 281 and the first region 23, wherein d2 is defined as the minimum distance value between the edge of the first boss 281 and the herringbone corrugated protrusions 231 on the first region 23 adjacent to the first boss 281, and d2 is greater than or equal to 1 mm. Further, since a part of the fluid passing through the second region 24 flows directly to the first region 23 and the other part flows to the first flow channel 211, the minimum distance d1 is made to be greater than the minimum distance d2, and the fluid flows smoothly, specifically, 1 mm. ltoreq. d 2. ltoreq. d 1. Thus, an elongated first channel 211 for fluid flowing is formed at the edge of the first boss 281, and a portion of the fluid after passing through the second region 24 can flow along the first channel 211, so that the fluid can flow from the first porthole 26 side to the second porthole 27 side, and the fluid can be prevented from flowing between two adjacent plates 20, so that the fluid can be more uniformly distributed and the fluid flow resistance is smaller, thereby improving the heat exchange performance of the heat exchanger.
As shown in fig. 5, at least one second shaped projection 251 is formed on the third area 25 at a distance from the plate plane 21, and correspondingly, a recess is formed on the other side of the plate 20 at a distance from the plate plane. Further, the height of the second shaped projection 251 projecting from the plate plane 21 is substantially the same as the height of the boss projecting from the plate plane 21.
The second shaped projection 251 is located between the first aperture 26 and the second aperture 27 on the same side of the plate 20, and is disposed opposite the first shaped projection 241. When two adjacent plates are stacked, the intersection between the second region 24 and the third region 25 allows fluid to flow from the plate plane on the front side of one plate 20 to the dimples on the back side of the adjacent plate 20, or from the dimples on the back side of one plate 20 to the plate plane on the front side of the adjacent plate 20.
And the ends of the second shaped protrusion 251 are spaced apart from the edges of the first and second ports 26 and 282, respectively, and the ends of the second shaped protrusion 251 are positioned at both sides of the bent portion 232, respectively, so that a portion of the fluid can flow from the edge of the second port 282 to the first port 26, guided by the second shaped protrusion 251.
Specifically, the second shaped protrusion 251 is also formed with an included angle Z, wherein the definition of the included angle Z is similar to that of the included angle X, and detailed description thereof is omitted. Moreover, the included angle Z of the second shaped projection 251 is larger than the included angle Y of the herringbone-shaped corrugated projection 231 at the bent portion, and the opening direction of the included angle Z is approximately opposite to the opening direction of the herringbone-shaped corrugated projection 231. Thus, the fluid from the plate plane area near the edge of the second protrusion 282 can flow to the first port 26 more smoothly through the plate plane 21 between the second shaped protrusions 251, thereby improving the distribution uniformity of the fluid and improving the heat exchange performance of the heat exchanger.
Further, the included angle Z of the second shaped projection 251 can also be divided into two parts by a perpendicular line passing through the vertex of the included angle Z, the included angle a3 is close to the second orifice 27, the included angle a4 is close to the first orifice, the included angle a4 is greater than or equal to the included angle a3, and the included angle a4 is greater than or equal to 90 degrees and is less than or equal to a3+90 degrees. Thus, the flow guiding performance of the second shaped projection 251 can be improved, so that the fluid can smoothly flow from the area near the edge of the second boss 282 to the first orifice 26, the fluid is uniformly distributed, and the heat exchange performance of the heat exchanger is improved.
Further, the third area 25 comprises at least two second shaped protrusions 251, and the included angle on the second shaped protrusions 251 decreases closer to the first area 23. Further, the third area 25 comprises a plurality of second shaped protrusions 251, the angle of the included angle a3 on each second shaped protrusion 251 is the same, and the angle of the included angle a4 increases in the direction toward the first area 23.
Similarly to the second area 24, at least a distance is kept between the edge of the second boss 282 and the end of the second shaped projection 251 on the third area 25, so that a plate plane 21 for fluid flow is formed between the edge of the second boss 282 and the third area 25.
Further, at least a distance d3 is maintained between the edge of the second boss 282 and the chevron-shaped corrugated protrusion 231 on the first region 23, so that a plate plane 21 for fluid flow is formed between the edge of the second boss 282 and the first region 23, where d3 is the minimum distance between the edge of the second boss 282 and the edge of the chevron-shaped corrugated protrusion adjacent to the second boss 282 on the first region 23. Thus, an elongated second flow channel 212 for fluid flowing is formed at the edge region of the second protrusion 282, and after passing through the first region 23, the fluid can flow along the second flow channel 212, so that the fluid flows from the second port 27 side to the first port 26 side under the guidance of the third region, so that the fluid can be more uniformly distributed and the flow resistance is lower, thereby improving the heat exchange performance of the heat exchanger.
Further, d3 is substantially the same as d2, and 1 mm. ltoreq. d 3. ltoreq. d 4. Thus, when the fluid flows from the first port 26 on one side to the first port 26 on the other side, especially when the two first ports 26 are located on the same side of the plate 20 (referred to as a single-side flow heat exchanger for short), by the arrangement of d1, d2 and d3, a better flow guiding effect can be achieved in the flowing process of the fluid, especially in the flowing-in and flowing-out stages, so that the fluid can be uniformly distributed on two sides of the plate, and the heat exchange performance of the heat exchanger is improved.
Because the fluid can be relatively evenly distributed in the plate sheet, the heat exchange performance of the heat exchanger is correspondingly improved, and the heat exchanger can be miniaturized. Particularly, in the single-side-flow heat exchanger, because the second area 24 and the third area 25 with the flow guiding function are arranged, the fluid can be uniformly distributed on both sides of the plate, so that the width of the heat exchanger can be increased, and the uniform distribution of the fluid on the plate can still be realized, specifically, the length-width ratio L/W of the plate can be less than or equal to 3 and more than or equal to 0.6, wherein the length and the width of the plate refer to the length and the width of the part without the flanging 22. Here, the side of the plate where the two first orifices or the two second orifices are located is defined as the length side of the plate, and the side of the plate where the first orifices and the second orifices are located is defined as the width side of the plate.
As shown in fig. 8, when two plates are stacked, a fluid passage for flowing a fluid is formed between the adjacent plates 20, the plate plane of the first region 23 on the front surface of the plate 20 and the concave pit on the back surface are formed as the fluid passage, and a welding point 235 is formed at the contact position of the corrugated protrusion on the first region 23 on the front surface of the plate 20 and the plate plane on the back surface of the adjacent plate by welding. At the weld 235, the fluid cannot flow and the weld can act as a spoiler.
In the prior art, due to the bent portion 232 in the herringbone corrugated protrusion 231 in the first region of the plate 20, when two plates 20 are stacked together, the welding point 235 generally existing at the bent portion 232 is large, so that the fluid flow at the bent portion 232 is low, even no fluid passes through, and thus the fluid flow is unevenly distributed, and the heat exchange performance of the heat exchanger is reduced.
As shown in fig. 6 and 7, in the present embodiment, when the first plate 201 and the second plate 202 are stacked together, in the first region 23, at least one corrugated protrusion 231 on the second plate 202 is not in contact with the plate plane on the opposite surface of the first plate 201 in the vicinity of the bent portion 232, that is, at least one peak 234 of the bent portion 232 on the first region 23 of the first plate 201 meets a peak 234 of the bent portion 232 on the first region 23 of the second plate 202, so that at least one third flow channel 236 is formed between the bent portions on the first regions 23 of the first plate 201 and the second plate 202. Therefore, the fluidity of the fluid in the middle part is improved, the formation of larger welding spots in the bending part is prevented, the fluid is uniformly distributed in the heat exchanger, and the heat exchange performance of the heat exchanger is improved.
Further, the peak 234 of the bend 232 of at least 2/3 on the first region 23 of the first panel 201 meets the peak 234 of the bend 232 on the first region 23 of the second panel 202, and the at least 1/3 corrugated protrusion 231 on the second panel 202 makes planar contact with the panel on the opposite side of the first panel 201 near the bend 232 may form a spot weld. Therefore, the problem that the flow area of the fluid is reduced due to the fact that a large welding point is formed near the bending portion can be prevented, the problem that the fluid forms a large flow rate near the bending portion can be prevented, the turbulence performance of the bending portion is improved, and therefore the heat exchange performance of the heat exchanger is improved.
The foregoing is illustrative of the present invention and is not to be construed as limiting thereof in any way. Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can now make numerous changes and modifications to the disclosed embodiments, and equivalents thereof, without departing from the scope of the invention as set forth in the claims below. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present invention are still within the scope of the protection of the technical solution of the present invention, unless the contents of the technical solution of the present invention are departed.
Claims (10)
1. A heat exchanger comprises a heat exchanger core body, wherein the heat exchanger core body comprises a plurality of first circulation plates and a plurality of second circulation plates which are arranged at intervals in a stacked mode, a first circulation channel and a second circulation channel which are arranged at intervals are formed between each first circulation plate and each second circulation plate, at least two first orifices and at least two second orifices are arranged on each first circulation plate and each second circulation plate respectively, the middle parts of the first circulation plates and the second circulation plates are main heat exchange areas, the heat exchanger core body is characterized in that each main heat exchange area comprises a plate plane and a plurality of herringbone corrugated bulges which are arranged at intervals, the herringbone corrugated bulges protrude out of the plate plane at intervals, pits are formed in corresponding areas on the reverse sides of the plates, and the herringbone corrugated bulges comprise at least one bending part;
on the heat exchanger core, at least one of the chevron corrugated protrusions of the second flow plate is not in contact with a plate plane on the opposite face of two adjacent first flow plates near a bend, at least one of the chevron corrugated protrusions of the second flow plate is opposite a dimple on the opposite face of the first flow plate near a bend, and a third flow channel is formed between at least one of the bends of adjacent first and second flow plates.
2. The heat exchanger of claim 1, wherein the chevron corrugation lobes of at least 2/3 of the second flow plate oppose dimples on the opposite face of the adjacent first flow plate adjacent bends, and the remaining chevron corrugation lobes of the second flow plate contact plate flats on the opposite face of the adjacent first flow plate adjacent bends to form welds.
3. The heat exchanger of claim 2, wherein the first and second flow plates are plates of the same shape configuration, the first flow plate being rotated 180 ° relative to the second flow plate on the heat exchanger core;
the plate sheet comprises a plate plane and a flanging surrounding the plate plane, the first hole is positioned at two corners of the plate plane, and bosses protruding out of the plate plane by a certain height are respectively formed at the other two corners of the plate plane: the first boss and the second boss are provided with pits which are recessed from the plane of the plate for a certain distance at corresponding positions on the reverse side of the plate, and the second hole is formed on the boss;
at least one side of the upper side area and the lower side area of the main heat exchange area of the first circulation plate and/or the second circulation plate is provided with a flow guide area, the flow guide area is positioned between two adjacent first orifices and second orifices, and the flow guide area is provided with at least one special-shaped bulge; the edge of the boss adjacent to the special-shaped protrusion keeps a certain distance with the end part of the special-shaped protrusion, the minimum distance between the edge of the boss adjacent to the special-shaped protrusion and the end part of the special-shaped protrusion is d1, the edge of the boss adjacent to the special-shaped protrusion keeps a certain distance with the end part of the herringbone corrugated protrusion, the minimum distance between the edge of the boss adjacent to the special-shaped protrusion and the end part of the herringbone corrugated protrusion is d2, d2 is larger than or equal to 1mm and smaller than or equal to d1, and a long and narrow flow channel is formed on the edge of the boss adjacent to the special-shaped protrusion;
the aspect ratio of the first flow plate to the second flow plate is not more than 3 and not more than 0.6;
the special-shaped bulge comprises at least two bulge parts, wherein each bulge part is linear or curved, and the bulge parts are connected to form the special-shaped bulge.
4. The heat exchanger of claim 3, wherein the plate comprises a second area and a third area on the upper side and the lower side of the plate, and further comprises a first area between the second area and the third area, wherein the first area is the main heat exchange area, and the second area and the third area are the flow guide areas; the second area is provided with at least one first special-shaped bulge which protrudes out of the plate plane for a certain distance, and the third area is provided with at least one second special-shaped bulge which protrudes out of the plate plane for a certain distance;
the edge of the first boss adjacent to the second region is respectively kept at a certain distance from the first special-shaped bulge and the corrugated bulge to form a long and narrow first flow passage;
the edge of the second boss adjacent to the third area keeps a certain distance with the second special-shaped bulge and the corrugated bulge respectively to form a long and narrow second flow passage;
the first special-shaped bulge comprises at least two bulge parts, wherein each bulge part is linear or curved, and the bulge parts are connected to form the first special-shaped bulge;
the second special-shaped bulge comprises at least two bulges, wherein each bulge is linear or curved, and the bulges are connected to form the second special-shaped bulge.
5. The heat exchanger according to claim 4, wherein the first shaped protrusion and the corrugated protrusion are respectively formed with an included angle, the included angle of the first shaped protrusion is larger than the included angle of the corrugated protrusion, and the included angle of the first shaped protrusion has an angular offset toward the first orifice side with respect to the included angle of the corrugated protrusion;
and the included angle of the first special-shaped protrusion is divided into an included angle a1 close to the second orifice and an included angle a2 close to the first orifice by taking a vertical line passing through the vertex of the included angle of the first special-shaped protrusion as a boundary, wherein a2 is more than or equal to a1, and a2 is less than or equal to 90.
6. The heat exchanger of claim 4, wherein the second region comprises a plurality of the first shaped protrusions, the first shaped protrusions and the corrugated protrusions are respectively formed with an included angle, the included angle of the first shaped protrusions is larger than the included angle of the corrugated protrusions, and the included angle of the first shaped protrusions has an angular offset towards the first orifice side relative to the included angle of the corrugated protrusions;
and the included angle of the first special-shaped protrusion is divided into an included angle a1 close to the second orifice and an included angle a2 close to the first orifice, the included angle of the first special-shaped protrusion is smaller as the first special-shaped protrusion is closer to the first area, and in the direction towards the first area, each a1 on each first special-shaped protrusion is the same, and the a2 is gradually reduced.
7. The heat exchanger according to any one of claims 4 to 6, wherein the second shaped protrusion has a height substantially the same as the height of the second boss, and ends of the second shaped protrusion are respectively kept at a distance from the edges of the adjacent first porthole and second boss.
8. The heat exchanger of claim 7, wherein the included angle of the second shaped protrusion is greater than the included angle of the corrugated protrusion, and the included angle of the second shaped protrusion has an angular offset towards the first orifice side relative to the included angle of the corrugated protrusion.
9. The heat exchanger of claim 8, wherein the included angle of the second shaped projection is divided into an included angle a3 proximate the second port and an included angle a4 proximate the first port, and the included angle a4 is equal to or greater than the included angle a3, and 90 ° ≦ a4 ≦ a3+90 °, bounded by a perpendicular passing through the apex of the included angle of the second shaped projection.
10. The heat exchanger of claim 8, wherein the included angle of the second shaped projection is divided into an included angle a3 proximate the second port and an included angle a4 proximate the first port, bounded by a perpendicular passing through the apex of the included angle of the second shaped projection; the third region comprises a plurality of the second shaped protrusions, and the angle of the included angle a3 on each of the second shaped protrusions is the same in the direction toward the first region, and the angle of the included angle a4 increases.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510233528.8A CN106197095B (en) | 2015-05-08 | 2015-05-08 | Heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510233528.8A CN106197095B (en) | 2015-05-08 | 2015-05-08 | Heat exchanger |
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| Publication Number | Publication Date |
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| CN106197095A CN106197095A (en) | 2016-12-07 |
| CN106197095B true CN106197095B (en) | 2020-03-06 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510233528.8A Active CN106197095B (en) | 2015-05-08 | 2015-05-08 | Heat exchanger |
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| CN (1) | CN106197095B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108662939A (en) * | 2018-06-07 | 2018-10-16 | 上海加冷松芝汽车空调股份有限公司 | A kind of corrugated plating and heat exchanger |
| CN110514039A (en) * | 2019-01-18 | 2019-11-29 | 四川赛特制冷设备有限公司 | A kind of new energy heat exchanger |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1151207A (en) * | 1994-06-20 | 1997-06-04 | 平板公司 | Three-circuit stacked plate heat exchanger |
| CN201163159Y (en) * | 2008-01-18 | 2008-12-10 | 江阴博格机械制冷技术有限公司 | Brazing sheet type heat exchanger |
| CN103471450A (en) * | 2013-09-25 | 2013-12-25 | 缪志先 | Box-shaped laminated heat exchanger provided with mounting holes |
| CN104296586A (en) * | 2013-07-15 | 2015-01-21 | 杭州三花研究院有限公司 | Heat exchanger sheet, heat exchanger heat exchange unit and heat exchanger |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3331950B2 (en) * | 1998-02-27 | 2002-10-07 | ダイキン工業株式会社 | Plate heat exchanger |
-
2015
- 2015-05-08 CN CN201510233528.8A patent/CN106197095B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1151207A (en) * | 1994-06-20 | 1997-06-04 | 平板公司 | Three-circuit stacked plate heat exchanger |
| CN201163159Y (en) * | 2008-01-18 | 2008-12-10 | 江阴博格机械制冷技术有限公司 | Brazing sheet type heat exchanger |
| CN104296586A (en) * | 2013-07-15 | 2015-01-21 | 杭州三花研究院有限公司 | Heat exchanger sheet, heat exchanger heat exchange unit and heat exchanger |
| CN103471450A (en) * | 2013-09-25 | 2013-12-25 | 缪志先 | Box-shaped laminated heat exchanger provided with mounting holes |
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| CN106197095A (en) | 2016-12-07 |
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