CN210400103U - Plate-fin heat exchanger - Google Patents
Plate-fin heat exchanger Download PDFInfo
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- CN210400103U CN210400103U CN201921461743.3U CN201921461743U CN210400103U CN 210400103 U CN210400103 U CN 210400103U CN 201921461743 U CN201921461743 U CN 201921461743U CN 210400103 U CN210400103 U CN 210400103U
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Abstract
The utility model relates to a plate-fin heat exchanger. The utility model provides a plate-fin heat exchanger, adopt the mode that increases strip of paper used for sealing width in near the region of the summit of heat exchanger core, increase the area of brazing between strip of paper used for sealing and the baffle, and then welding strength has been increased, thereby the technical problem of the microcrack of the welding seam structure that near the regional stress concentration phenomenon in summit of having overcome the heat exchanger core probably caused, and further the anti fatigue failure ability of welding seam structure has been increased, thereby the emergence of the phenomenon of sealed not tight appears easily in the welding seam structure of having avoided forming between strip of paper used for sealing near the summit of plate-fin heat exchanger core and the baffle. The sealing strip width is increased to increase the brazing area, and the sealing failure problem caused by welding defects caused by bending deformation of the sealing strip or the partition plate due to thermal stress can be prevented, so that the sealing yield of the plate-fin heat exchanger is improved, the reliability of the plate-fin heat exchanger is improved, and the service life of the plate-fin heat exchanger is prolonged.
Description
Technical Field
The utility model relates to a heat exchange equipment especially relates to a plate-fin heat exchanger.
Background
The plate-fin heat exchanger has the advantages of compact structure, low cost, high heat exchange efficiency and the like, and is widely applied to the industries of energy, chemical engineering, aerospace and the like.
The plate-fin heat exchanger core is one of the core components of the plate-fin heat exchanger. The plate-fin heat exchanger core is formed by stacking and brazing fins, partition plates and sealing strips layer by layer according to a specific arrangement mode.
In the prior art, the core body of the plate-fin heat exchanger is mostly rectangular; the sealing strip with the conventional design is adopted to seal and isolate a cold and hot fluid channel, and the phenomenon of poor sealing is easy to occur in a welding seam structure formed between the sealing strip and the partition plate which are positioned near the top point of the plate-fin heat exchanger core. The sealing strip with the conventional design is adopted, so that the sealing strip and the partition plate are small in welding area and low in welding strength, the sealing strip is influenced by the geometric shape of the heat exchanger, and the stress concentration phenomenon of the area near the top point of the core body of the heat exchanger is most obvious; under the action of cyclic load, microcracks are likely to form on grains with the largest stress of the welding seam structure, then the microcracks develop into macrocracks, and then the macrocracks continue to expand to cause fatigue failure of the welding seam structure, so that the phenomenon that the welding seam structure formed between the seal strip near the top point of the plate-fin heat exchanger core and the partition plate is easy to have poor sealing is caused, and finally the plate-fin heat exchanger fails.
SUMMERY OF THE UTILITY MODEL
In the prior art, a rectangular plate-fin heat exchanger adopts a seal of a conventional design to seal and isolate a cold and hot fluid channel, and a welding seam structure formed between the seal and a partition plate in an area near the top point of a core body of the plate-fin heat exchanger is easy to have the phenomenon of poor sealing.
In order to solve the technical problem, the utility model provides a technical scheme does:
the utility model provides a plate-fin heat exchanger, which comprises a heat exchanger core body; the heat exchanger core is in a cuboid shape; the heat exchanger core comprises a plurality of fluid channels which are stacked step by step from top to bottom; the fluid channel comprises a channel wall formed by brazing a partition plate and a seal; the width of the seal extending along the thickness direction of the side wall of the channel wall is the width of the seal; the fluid channel is specifically a hot fluid channel or a cold fluid channel; the extension directions of the hot fluid channel and the cold fluid channel are mutually perpendicular; the hot fluid channel and the cold fluid channel are stacked at intervals;
the plurality of thermal fluid channels positioned in the middle of the heat exchanger core are intermediate thermal fluid channels; the hot fluid channels positioned above and below the middle layer hot fluid channel are end layer hot fluid channels; the seal widths of the intermediate layer thermal fluid channels are all equal and less than the seal widths of the end layer thermal fluid channels;
the plurality of cold fluid channels positioned in the middle of the heat exchanger core are middle-layer cold fluid channels; the cold fluid channels above and below the middle layer cold fluid channel are end layer cold fluid channels; the seal widths of the middle layer cold fluid channels are all equal and smaller than the seal widths of the end layer cold fluid channels.
The plate-fin heat exchanger provided by the utility model preferably has the ratio of the length of the inlet cross section of the fluid channel to the width of the seal strip less than 80: 1.
The plate-fin heat exchanger provided by the utility model preferably has the seal width of the end layer hot fluid channel in inverse proportion to the shortest distance from the end layer hot fluid channel to the center of the heat exchanger core body; alternatively, the seal width of the end cold layer fluid channel is inversely proportional to the shortest distance of the end cold layer fluid channel to the center of the heat exchanger core.
The plate-fin heat exchanger provided by the utility model preferably has the seal width of the end layer hot fluid channel in inverse proportion to the shortest distance from the end layer hot fluid channel to the center of the heat exchanger core body; the seal width of the end cold layer fluid channel is inversely proportional to the shortest distance of the end cold layer fluid channel to the center of the heat exchanger core.
The utility model provides a plate-fin heat exchanger, preferably, a plurality of the tip layer hot-fluid passageways that are closest to the summit of the plate-fin heat exchanger are equal-width tip layer hot-fluid passageways; the seal widths of the thermal fluid channels of the equal-width end layers are equal and larger than those of the other thermal fluid channels; the end-layer thermal fluid channel positioned between all the equal-width end-layer thermal fluid channels and the middle-layer thermal fluid channel is a stepped end-layer thermal fluid channel; the seal width of the stepped end layer thermal fluid channel is inversely proportional to the shortest distance of the stepped end layer thermal fluid channel to the center of the heat exchanger core; or the end laminar cooling fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end laminar cooling fluid channels; the seal widths of the cold fluid channels of the equal-width end layers are equal and larger than those of other cold fluid channels; the end layer cold fluid channels positioned between all the equal-width end layer cold fluid channels and the middle layer cold fluid channel are stepped end layer cold fluid channels; the seal width of the stepped end cold layer fluid channel is inversely proportional to the shortest distance from the stepped end cold layer fluid channel to the center of the heat exchanger core.
The utility model provides a plate-fin heat exchanger, preferably, a plurality of the tip layer hot-fluid passageways that are closest to the summit of the plate-fin heat exchanger are equal-width tip layer hot-fluid passageways; the seal widths of the thermal fluid channels of the equal-width end layers are equal and larger than those of the other thermal fluid channels; the end-layer thermal fluid channel positioned between all the equal-width end-layer thermal fluid channels and the middle-layer thermal fluid channel is a stepped end-layer thermal fluid channel; the seal width of the stepped end layer thermal fluid channel is inversely proportional to the shortest distance of the stepped end layer thermal fluid channel to the center of the heat exchanger core; the end laminar cooling fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end laminar cooling fluid channels; the seal widths of the cold fluid channels of the equal-width end layers are equal and larger than those of other cold fluid channels; the end layer cold fluid channels positioned between all the equal-width end layer cold fluid channels and the middle layer cold fluid channel are stepped end layer cold fluid channels; the seal width of the stepped end cold layer fluid channel is inversely proportional to the shortest distance from the stepped end cold layer fluid channel to the center of the heat exchanger core.
The utility model provides a plate-fin heat exchanger, preferably, the top surface and the bottom surface of heat exchanger core the baffle thickness of baffle is greater than the inside of plate-fin heat exchanger core the baffle thickness of baffle.
The plate-fin heat exchanger provided by the utility model preferably has fins welded in the fluid channel for increasing the heat exchange area; two sides of the fin are arranged close to the seal; the seal includes a plurality of projections in contact with the fins.
The utility model provides a plate-fin heat exchanger, preferably, the cross sectional shape of convex part is triangle-shaped, quadrangle or arc.
The utility model provides a plate-fin heat exchanger, preferably, the strip of paper used for sealing include three convex parts of the same shape; any two convex parts are connected through a U-shaped groove.
The utility model has the advantages of or beneficial effect:
the utility model provides a plate-fin heat exchanger, because the mode that increases strip of paper used for sealing width is adopted near the summit of heat exchanger core (being the relevant position of tip layer hot-fluid passage and tip layer cold fluid passage), increase the area of brazing between strip of paper used for sealing and baffle, and then welding strength has been increased, thereby the technical problem of the microcrack of the welding seam structure that near the summit regional stress concentration phenomenon of heat exchanger core probably caused has been overcome, and the anti fatigue failure ability of welding seam structure has further been increased, thereby the emergence of the phenomenon of sealed untight appears easily in the welding seam structure of having avoided forming between near the summit of plate-fin heat exchanger core and the baffle. In addition, the sealing strip width is increased to increase the brazing area, so that the sealing failure problem caused by welding defects caused by bending deformation of the sealing strip or the clapboard due to thermal stress can be prevented. Adopt the utility model provides a plate-fin heat exchanger has improved plate-fin heat exchanger's leakproofness yield, has increased plate-fin heat exchanger's reliability, has prolonged plate-fin heat exchanger's life.
Drawings
The invention and its features, aspects and advantages will become more apparent from a reading of the following detailed description of non-limiting embodiments with reference to the attached drawings. Like reference symbols in the various drawings indicate like elements. The drawings are not intended to be drawn to scale, emphasis instead being placed upon illustrating the principles of the invention.
Fig. 1 is a front view of a heat exchanger core of a plate-fin heat exchanger according to embodiment 1 of the present invention;
fig. 2 is a side view of a heat exchanger core of a plate fin heat exchanger according to embodiment 1 of the present invention;
fig. 3 is a top view of a heat exchanger core of a plate fin heat exchanger according to embodiment 1 of the present invention;
FIG. 4 is a partial enlarged view of area A of FIG. 1;
fig. 5 is a schematic perspective view of a seal according to embodiment 1 of the present invention.
Detailed Description
In the following, the technical solutions in the embodiments of the present invention are clearly and completely described with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative efforts belong to the protection scope of the present invention.
Example 1
In the prior art, a rectangular plate-fin heat exchanger adopts a seal of a conventional design to seal and isolate a cold and hot fluid channel, and a welding seam structure formed between the seal and a partition plate in an area near the top point of a core body of the plate-fin heat exchanger is easy to have the phenomenon of poor sealing.
The embodiment provides a plate-fin heat exchanger, which comprises a heat exchanger core; as shown in fig. 1-3, the heat exchanger core is in a cuboid shape; the heat exchanger core comprises a plurality of fluid channels 1 which are stacked step by step from top to bottom; the fluid channel 1 can be divided into a hot fluid channel 101 or a cold fluid channel 102; the extension directions of the hot fluid channel 101 and the cold fluid channel 102 are perpendicular to each other; the hot fluid channel 101 and the cold fluid channel 102 are stacked at intervals;
as shown in fig. 4, the fluid passage 1 includes a passage wall formed by brazing a partition plate 11 and a seal 12; the width of the seal 12 extending in the thickness direction of the side wall of the passage wall is the seal width; as shown in fig. 1 and 4, the hot fluid channel 101 has a seal width W, and as shown in fig. 2, the cold fluid channel 102 has a seal width D. As shown in fig. 1 and 4, the plurality of thermal fluid channels 101 located in the middle of the heat exchanger core are intermediate thermal fluid channels; a plurality of thermal fluid channels 101 above and below the intermediate layer thermal fluid channel are end layer thermal fluid channels; the widths of the seals of the intermediate layer thermal fluid channel are equal and smaller than those of the seals of the end layer thermal fluid channel;
as shown in fig. 2, the plurality of cold fluid channels 102 located in the middle of the heat exchanger core are middle layer cold fluid channels; a plurality of cold fluid channels 102 located above and below the middle layer cold fluid channel are end layer cold fluid channels; the seal widths of the middle layer cold fluid channels are equal and smaller than those of the end layer cold fluid channels.
The utility model provides a plate-fin heat exchanger, because the mode that increases strip of paper used for sealing width is adopted near the summit of heat exchanger core (being the relevant position of tip layer hot-fluid passage and tip layer cold-fluid passage), increase the area of brazing between strip of paper used for sealing 12 and baffle 11, and then welding strength has been increased, thereby overcome near summit regional stress concentration phenomenon of heat exchanger core and probably caused the technical problem of the microcrack of welding seam structure, and further increased the anti fatigue failure ability of welding seam structure, thereby the emergence of sealed not tight phenomenon appears easily in the welding seam structure of having avoided forming between near summit of plate-fin heat exchanger core and the baffle. In addition, the sealing strip width is increased to increase the brazing area, so that the sealing failure problem caused by welding defects caused by bending deformation of the sealing strip or the clapboard due to thermal stress can be prevented. Adopt the utility model provides a plate-fin heat exchanger has improved plate-fin heat exchanger's leakproofness yield, has increased plate-fin heat exchanger's reliability, has prolonged plate-fin heat exchanger's life.
As mentioned above, too narrow a seal width may cause poor sealing of the plate fin heat exchanger, and the ratio of the seal width to the length of the inlet cross section of the fluid passage is optimized for good sealing effect. In the plate fin heat exchanger provided in this embodiment, the ratio of the length of the inlet cross section of the fluid channel 1 to the width of the seal is preferably less than 80: 1. Taking the thermal fluid channel 101 as an example, as shown in fig. 1, the length of the inlet cross section of the thermal fluid channel 101 is L; the width of the seal of the thermal fluid channel 101 is W; L/W < 80; for example, in this embodiment, L/W is 930mm/12mm 77.5. Through optimizing the ratio of the seal width to the length of the inlet section of the fluid channel, the result shows that when the ratio of the length of the inlet section of the fluid channel 1 to the seal width is less than 80:1, the sealing yield of the plate-fin heat exchanger is not lower than 99.8%, and compared with the prior art, the sealing yield of the plate-fin heat exchanger is greatly improved. In addition, because the width of the seal is increased, the seal 12 has a better supporting effect on the fins 13 installed in the fluid channel 1, so that the plate-fin heat exchanger adopting the embodiment can be suitable for various fin designs, and the situation that the fins are deformed due to insufficient supporting force and even the fluid channel is blocked can be effectively avoided.
Because the stress is closely related to the shape or position, the stress applied to the weld structure between the seal and the partition in the hot fluid channel or the cold fluid channel at different positions is different, and a better sealing effect is achieved by using the minimum material of the seal 12. The plate-fin heat exchanger provided in this embodiment preferably has the following features: the seal width of the end layer hot fluid channel is inversely proportional to the shortest distance from the end layer hot fluid channel to the center of the heat exchanger core; scheme II: the seal width of the end cold fluid channel is inversely proportional to the shortest distance of the end cold fluid channel to the center of the heat exchanger core. The third scheme is as follows: the seal width of the end layer hot fluid channel is inversely proportional to the shortest distance from the end layer hot fluid channel to the center of the heat exchanger core; and the seal width of the end cold layer fluid channel is inversely proportional to the shortest distance from the end cold layer fluid channel to the center of the heat exchanger core. According to the stress distribution rule in the cuboid structure, the stress action of the central part of the cuboid is minimum, and the stress action of each part in the extension direction from the central part of the cuboid to each vertex of the cuboid is gradually increased; therefore, the seal width of the plate-fin heat exchanger provided by the embodiment is reasonably designed according to the specific conditions of the stresses applied to different positions of the core body of the plate-fin heat exchanger, so that the better sealing effect can be achieved by using the least material of the seal 12. The seal widths of the end layer fluid channels (i.e., the end layer hot fluid channel and the end layer cold fluid channel) of the hot fluid channel 101 and the cold fluid channel 102 can be designed according to actual needs, so as to simplify production.
The stress action closest to the vertex area is most significant, and in order to further enhance the welding strength of the welding seam structure between the partition board closest to the vertex area and the seal, the plate-fin heat exchanger provided by the embodiment preferably has the following steps: the end-layer thermal fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end-layer thermal fluid channels; the seal widths of the thermal fluid channels of the equal-width end layers are equal and larger than those of other thermal fluid channels; the end-layer thermal fluid channel positioned between all the end-layer thermal fluid channels with the same width and the middle-layer thermal fluid channel is a stepped end-layer thermal fluid channel; the width of the seal of the hot fluid channel of the step end layer is inversely proportional to the shortest distance from the hot fluid channel of the step end layer to the center of the heat exchanger core; scheme II: the end laminar cooling fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end laminar cooling fluid channels; the seal widths of the laminar and cold fluid channels at the equal-width end parts are equal and are greater than those of other cold fluid channels; the end cold fluid channel between all the equal-width end cold fluid channels and the middle cold fluid channel is a stepped end cold fluid channel; the seal width of the stepped end cold fluid channel is inversely proportional to the shortest distance from the stepped end cold fluid channel to the center of the heat exchanger core. The third scheme is as follows: the end-layer thermal fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end-layer thermal fluid channels; the seal widths of the thermal fluid channels of the equal-width end layers are equal and larger than those of other thermal fluid channels; the end-layer thermal fluid channel positioned between all the end-layer thermal fluid channels with the same width and the middle-layer thermal fluid channel is a stepped end-layer thermal fluid channel; the width of the seal of the hot fluid channel of the step end layer is inversely proportional to the shortest distance from the hot fluid channel of the step end layer to the center of the heat exchanger core; moreover, a plurality of end laminar cooling fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end laminar cooling fluid channels; the seal widths of the laminar and cold fluid channels at the equal-width end parts are equal and are greater than those of other cold fluid channels; the end cold fluid channel between all the equal-width end cold fluid channels and the middle cold fluid channel is a stepped end cold fluid channel; the seal width of the stepped end cold fluid channel is inversely proportional to the shortest distance from the stepped end cold fluid channel to the center of the heat exchanger core. The end layer fluid channels (the end layer hot fluid channel and/or the end layer cold fluid channel) closest to the vertex of the plate-fin heat exchanger are designed into equal-width end layer fluid channels (equal-width end layer hot fluid channels and/or equal-width end layer cold fluid channels) with equal seal widths, the seal width of the area is set to be longest, the stress of the upper surface and the lower surface of the partition plate and the brazing surface of the seal are more uniform, the partition plate is stacked in a multilayer mode, the brazing strength near the vertex of the plate-fin heat exchanger is further increased, and therefore the stress action closest to the vertex area is sufficiently overcome. The seal width of the stepped end layer fluid channel (the stepped end hot layer fluid channel and/or the stepped end cold layer fluid channel) is reasonably designed according to the specific conditions of the stress borne by different positions of the plate-fin heat exchanger core, so that the better sealing effect can be achieved by using the minimum material of the seal 12. The seal widths of the end layer fluid channels (i.e., the end layer hot fluid channel and the end layer cold fluid channel) of the hot fluid channel 101 and the cold fluid channel 102 can be designed according to actual needs, so as to simplify production.
In order to reduce the deformation of the plate-fin heat exchanger, the plate-fin heat exchanger provided in this embodiment preferably has a partition thickness of the partitions on the top surface and the bottom surface of the heat exchanger core, which is greater than the partition thickness of the partitions inside the plate-fin heat exchanger core, as shown in fig. 4. The thickness of the partition plates of the top surface and the bottom surface of the heat exchanger core body is increased, so that the strength of the partition plates can be increased, the deformation is reduced, and the service life of the plate-fin heat exchanger is prolonged.
In order to improve the heat exchange effect and reduce the production cost of the plate-fin heat exchanger, in the plate-fin heat exchanger provided by the embodiment, preferably, fins 13 for increasing the heat exchange area are welded in the fluid channel 1; the two sides of the fin 13 are arranged next to the seal 12; the seal 12 includes a number of protrusions 121 that contact the fins. The cross-sectional shape of the convex portion 121 is a triangle, a quadrangle, or a circular arc, see fig. 4. Compared with the common cuboid seal, the seal 12 with the plurality of convex parts 121 is adopted, so that the raw materials consumed by the seal 12 can be reduced on the premise of not influencing the sealing effect, and the production cost of the plate-fin heat exchanger is reduced. In addition, the arrangement of the convex portion 121 has a positioning function for the fin 13, and the relative position of the fin 12 on the partition plate 11 can be effectively fixed, which is particularly important for the assembly positioning of the partition plate 11, the seal 12 and the fin 13 of the brazing front plate-fin heat exchanger. The seal 12 with the triangular, quadrangular or circular arc-shaped cross section can be produced by adopting a corresponding die, the production and the processing of the seal are convenient, the cost is low, and the seal can meet the requirement of mass production.
In order to further reduce the raw material consumption of the seal, the plate fin heat exchanger provided in this embodiment, preferably, as shown in fig. 5, the plate fin heat exchanger provided in this embodiment, preferably, the seal includes three circular arc-shaped protrusions 121 having the same shape; any two convex parts 121 are connected through a U-shaped groove 122. The circular arc-shaped convex parts 121 with the same shape as the three circular arc-shaped convex parts can better support the fins 13 in the vertical direction of the seal 12, and can better meet the requirement of the plate-fin heat exchanger on the strength of the seal; in addition, the relative position of the fin 13 on the partition plate 11 can be better fixed. The provision of two U-shaped slots 122 can significantly reduce the raw material cost of the seal 12. The raised strips 121 and the U-shaped grooves 122 are both designed to be arc-shaped, so that stress concentration can be effectively avoided, and deformation of the sealing strip in a high-temperature atmosphere during brazing treatment is avoided, thereby being beneficial to improving the sealing yield of the plate-fin heat exchanger. The seal 12 used in the plate-fin heat exchanger provided by the embodiment can be produced in batches through a mold, and has good commercial value.
The above only is the preferred embodiment of the present invention, not limiting the scope of the present invention, all the equivalent structural changes made by the contents of the specification and the drawings, or the direct or indirect application in other related technical fields, are included in the same way in the protection scope of the present invention.
Claims (10)
1. A plate-fin heat exchanger is characterized by comprising a heat exchanger core body; the heat exchanger core is in a cuboid shape; the heat exchanger core comprises a plurality of fluid channels which are stacked step by step from top to bottom; the fluid channel comprises a channel wall formed by brazing a partition plate and a seal; the width of the seal extending along the thickness direction of the side wall of the channel wall is the width of the seal; the fluid channel is specifically a hot fluid channel or a cold fluid channel; the extension directions of the hot fluid channel and the cold fluid channel are mutually perpendicular; the hot fluid channel and the cold fluid channel are stacked at intervals;
the plurality of thermal fluid channels positioned in the middle of the heat exchanger core are intermediate thermal fluid channels; the hot fluid channels positioned above and below the middle layer hot fluid channel are end layer hot fluid channels; the seal widths of the intermediate layer thermal fluid channels are all equal and less than the seal widths of the end layer thermal fluid channels;
the plurality of cold fluid channels positioned in the middle of the heat exchanger core are middle-layer cold fluid channels; the cold fluid channels above and below the middle layer cold fluid channel are end layer cold fluid channels; the seal widths of the middle layer cold fluid channels are all equal and smaller than the seal widths of the end layer cold fluid channels.
2. The plate fin heat exchanger of claim 1, wherein a ratio of a length of an inlet cross-section of the fluid channel to the seal width is less than 80: 1.
3. The plate fin heat exchanger of claim 1, wherein the seal width of the end layer thermal fluid channel is inversely proportional to the shortest distance of the end layer thermal fluid channel to the center of the heat exchanger core; alternatively, the seal width of the end cold layer fluid channel is inversely proportional to the shortest distance of the end cold layer fluid channel to the center of the heat exchanger core.
4. The plate fin heat exchanger of claim 1, wherein the seal width of the end layer thermal fluid channel is inversely proportional to the shortest distance of the end layer thermal fluid channel to the center of the heat exchanger core; the seal width of the end cold layer fluid channel is inversely proportional to the shortest distance of the end cold layer fluid channel to the center of the heat exchanger core.
5. The plate fin heat exchanger of claim 1, wherein a number of the end layer thermal fluid channels closest to the apex of the plate fin heat exchanger are equal width end layer thermal fluid channels; the seal widths of the thermal fluid channels of the equal-width end layers are equal and larger than those of the other thermal fluid channels; the end-layer thermal fluid channel positioned between all the equal-width end-layer thermal fluid channels and the middle-layer thermal fluid channel is a stepped end-layer thermal fluid channel; the seal width of the stepped end layer thermal fluid channel is inversely proportional to the shortest distance of the stepped end layer thermal fluid channel to the center of the heat exchanger core; or the end laminar cooling fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end laminar cooling fluid channels; the seal widths of the cold fluid channels of the equal-width end layers are equal and larger than those of other cold fluid channels; the end layer cold fluid channels positioned between all the equal-width end layer cold fluid channels and the middle layer cold fluid channel are stepped end layer cold fluid channels; the seal width of the stepped end cold layer fluid channel is inversely proportional to the shortest distance from the stepped end cold layer fluid channel to the center of the heat exchanger core.
6. The plate fin heat exchanger of claim 1, wherein a number of the end layer thermal fluid channels closest to the apex of the plate fin heat exchanger are equal width end layer thermal fluid channels; the seal widths of the thermal fluid channels of the equal-width end layers are equal and larger than those of the other thermal fluid channels; the end-layer thermal fluid channel positioned between all the equal-width end-layer thermal fluid channels and the middle-layer thermal fluid channel is a stepped end-layer thermal fluid channel; the seal width of the stepped end layer thermal fluid channel is inversely proportional to the shortest distance of the stepped end layer thermal fluid channel to the center of the heat exchanger core; the end laminar cooling fluid channels closest to the top point of the plate-fin heat exchanger are equal-width end laminar cooling fluid channels; the seal widths of the cold fluid channels of the equal-width end layers are equal and larger than those of other cold fluid channels; the end layer cold fluid channels positioned between all the equal-width end layer cold fluid channels and the middle layer cold fluid channel are stepped end layer cold fluid channels; the seal width of the stepped end cold layer fluid channel is inversely proportional to the shortest distance from the stepped end cold layer fluid channel to the center of the heat exchanger core.
7. The plate fin heat exchanger of claim 1, wherein the top and bottom surfaces of the heat exchanger core have a spacer thickness of the spacer that is greater than a spacer thickness of the spacer on the interior of the plate fin heat exchanger core.
8. The plate fin heat exchanger of claim 1, wherein fins for increasing heat exchange area are welded in the fluid channel; two sides of the fin are arranged close to the seal; the seal includes a plurality of projections in contact with the fins.
9. The plate fin heat exchanger of claim 8, wherein the cross-sectional shape of the protrusion is triangular, quadrilateral or circular arc.
10. The plate fin heat exchanger of claim 9, wherein the seal includes three convex portions of the same circular arc shape; any two convex parts are connected through a U-shaped groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921461743.3U CN210400103U (en) | 2019-09-04 | 2019-09-04 | Plate-fin heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921461743.3U CN210400103U (en) | 2019-09-04 | 2019-09-04 | Plate-fin heat exchanger |
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| Publication Number | Publication Date |
|---|---|
| CN210400103U true CN210400103U (en) | 2020-04-24 |
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| CN201921461743.3U Active CN210400103U (en) | 2019-09-04 | 2019-09-04 | Plate-fin heat exchanger |
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| CN (1) | CN210400103U (en) |
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- 2019-09-04 CN CN201921461743.3U patent/CN210400103U/en active Active
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