CN117006869B - Heat exchange plates and heat exchangers - Google Patents
Heat exchange plates and heat exchangersInfo
- Publication number
- CN117006869B CN117006869B CN202311104794.1A CN202311104794A CN117006869B CN 117006869 B CN117006869 B CN 117006869B CN 202311104794 A CN202311104794 A CN 202311104794A CN 117006869 B CN117006869 B CN 117006869B
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- China
- Prior art keywords
- heat exchange
- area
- width
- flow channel
- trough
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The application provides a heat exchange plate and a heat exchanger, wherein the heat exchange plate comprises a plate body, two sides of the plate body in the length direction are respectively provided with a flow guide area, each flow guide area is respectively communicated with a first corner hole, a heat exchange area is communicated between the two flow guide areas, the heat exchange area comprises a heat exchange auxiliary area arranged at a corner and a heat exchange main area communicated with the heat exchange auxiliary area, the width of the heat exchange auxiliary area is smaller than or equal to 1/3 of the width of the heat exchange area, the length of the heat exchange auxiliary area is smaller than or equal to 1/3 of the length of the heat exchange area, a first flow channel is arranged in the heat exchange main area, and at least one heat exchange auxiliary area far from the first corner hole is internally provided with a second flow channel, and the sectional area of the second flow channel is larger than the sectional area of the first flow channel. The heat exchange plate and the heat exchanger provided by the application have the advantages that the structure is simple, the fluid in the heat exchange area is uniformly distributed by adjusting the sectional area of the flow channel of the heat exchange auxiliary area, the heat exchange effect is good, the service life is long, meanwhile, the pressure drop of the heat exchanger is smaller, and the operation energy consumption is saved.
Description
Technical Field
The application relates to the technical field of heat exchange plates, in particular to a heat exchange plate and a heat exchanger.
Background
The gasket plate type heat exchanger is equipment formed by stacking heat exchange plates, and mainly has the functions of realizing heat exchange of cold and hot media and achieving the purpose of energy transfer, in the use process of the heat exchanger, the uniformity of flow distribution of the media directly influences the heat transfer efficiency of the heat exchange plates and the service life of the plates, and the conventional heat exchange plates have different flow distances from corner holes to heat exchange areas, so that the distribution of fluid in the heat exchange areas is uneven, the heat exchange effect is seriously reduced, and the service life is reduced.
In the related art, a variable angle and a cambered raised flow guide strip facing a heat exchange area are arranged in a flow guide area of a plate body, so that fluid is distributed more uniformly, but after the flow guide strip is arranged, the overall flow resistance of a plate sheet is obviously increased, the pressure drop is increased, the pressure drop requirement cannot be met for a plurality of application occasions requiring severe pressure drop, the equipment use energy consumption is increased, the operation cost is increased, and in the other technologies, channels with unequal widths are integrally arranged in the heat exchange area, so that the overall flow distribution is improved, but the targeted flow distribution adjustment cannot be performed according to the actual distribution characteristics of a low flow velocity area, the adjustment width is limited by the number of herringbone corrugated partitions and the length of the blocking broken ribs of the heat exchange area, and the adjustment effect of the flow distribution is not ideal because the flow distribution adjustment cannot be performed according to the uneven degree of the flow in the length direction of the plate body.
Disclosure of Invention
In view of the above, the present application is directed to a heat exchange plate and a heat exchanger for solving the related problems mentioned in the background art.
The application provides a heat exchange plate, which comprises a plate body, wherein two sides of the plate body in the length direction are respectively provided with a flow guide area, each flow guide area is respectively communicated with a first angle hole, a heat exchange area is communicated between the two flow guide areas, each heat exchange area comprises a heat exchange auxiliary area arranged at a corner and a heat exchange main area communicated with the heat exchange auxiliary area, the width of each heat exchange auxiliary area is smaller than or equal to 1/3 of the width of each heat exchange area, the length of each heat exchange auxiliary area is smaller than or equal to 1/3 of the length of each heat exchange area, a first flow passage is arranged in each heat exchange main area, and at least one heat exchange auxiliary area far away from the first angle hole is internally provided with a second flow passage, and the cross section area of each second flow passage is larger than that of each first flow passage.
Further, the first flow channel comprises first wave crests and first wave troughs which are alternately arranged, the second flow channel comprises second wave crests and second wave troughs which are alternately arranged, the width of the first wave crests is equal to that of the first wave troughs, the width of the second wave crests is equal to that of the first wave crests, and the width of the second wave troughs is larger than that of the first wave troughs.
Further, the extending direction of the second flow channel to the outer side of the plate body is a first direction, the length direction of the plate body from the flow guiding area to the heat exchange area is a second direction, the width of the same second trough is gradually reduced along the first direction, and/or the width of a plurality of second troughs is gradually reduced along the second direction.
Further, the maximum width of the same second trough is less than or equal to 1.5 times the minimum width of the second trough.
Further, the included angle between the first flow channel and the length direction of the plate body is beta, the included angle between the second flow channel and the length direction of the plate body is alpha, when the direction from the first angle hole to the second flow channel is in the same direction as the first direction, alpha is smaller than beta, alpha corresponding to a plurality of second flow channels is gradually increased along the second direction, otherwise, alpha is larger than beta, and alpha corresponding to a plurality of second flow channels is gradually decreased along the second direction.
Further, the width of the heat exchange auxiliary area gradually decreases along the second direction.
Further, the shape of the heat exchange auxiliary area is a right triangle, a right trapezoid or an irregular convex quadrangle.
Further, the area of the heat exchange auxiliary area is positively correlated with the width of the heat exchange area, the difference value of the width of the second trough and the first trough is positively correlated with the width of the heat exchange area, the difference value of beta and alpha is positively correlated with the width of the heat exchange area, the area of the heat exchange auxiliary area is negatively correlated with beta, the difference value of the width of the second trough and the first trough is negatively correlated with beta, and the difference value of beta and alpha is negatively correlated with beta.
Further, a third flow passage is arranged in the heat exchange auxiliary area, which is close to the first corner hole, and the sectional area of the third flow passage is equal to the sectional area of the first flow passage.
Further, the first flow channel comprises first wave crests and first wave troughs which are alternately arranged, the third flow channel comprises third wave crests and third wave troughs which are alternately arranged, the width of the first wave crests is equal to that of the first wave troughs, the width of the third wave crests is larger than that of the first wave crests, and the width of the third wave troughs is equal to that of the first wave troughs.
In a second aspect of the application, a heat exchanger is provided comprising a stack of heat exchanger plates as described in the first aspect above.
The heat exchange plate comprises a plate body, two ends of the plate body are provided with flow guide areas, each flow guide area is communicated with a first corner hole, the first corner holes are used for fluid to flow in and out, a heat exchange area is communicated between the two flow guide areas and is used for fluid heat exchange, the heat exchange area comprises a heat exchange auxiliary area arranged at a corner and a heat exchange main area communicated with the heat exchange auxiliary area, the width of the heat exchange auxiliary area is smaller than or equal to 1/3 of the width of the heat exchange area, the length of the heat exchange auxiliary area is smaller than or equal to 1/3 of the length of the heat exchange area, the heat exchange auxiliary area is a region except the heat exchange auxiliary area, namely a region where fluid normally flows in the heat exchange area, the heat exchange main area is internally provided with a first flow channel, and at least one heat exchange auxiliary area far away from the first corner holes is internally provided with a second flow channel.
Drawings
In order to more clearly illustrate the technical solutions of the present application or related art, the drawings that are required to be used in the description of the embodiments or related art will be briefly described below, and it is apparent that the drawings in the following description are only embodiments of the present application, and other drawings may be obtained according to the drawings without inventive effort to those of ordinary skill in the art.
FIG. 1 is a schematic view of a first heat exchanger plate according to an embodiment of the present application;
FIG. 2 is an enlarged schematic view of the structure shown at X in FIG. 1;
FIG. 3 is a schematic cross-sectional view of the first flow path at A-A of FIG. 2;
FIG. 4 is a schematic cross-sectional view of a first combined flow path formed at A-A in FIG. 2;
FIG. 5 is a schematic cross-sectional view of a second flow path at B-B in FIG. 2;
FIG. 6 is a schematic cross-sectional view of a second combined flow path formed at B-B in FIG. 2;
FIG. 7 is a schematic cross-sectional view of the second flow path of FIG. 2 at C-C;
FIG. 8 is a schematic cross-sectional view of a second combined flow path formed at C-C in FIG. 2;
FIG. 9 is a schematic cross-sectional view of the third flow path at D-D of FIG. 1;
FIG. 10 is a schematic cross-sectional view of a third combined flow path formed at D-D in FIG. 1;
FIG. 11 is a schematic cross-sectional view of the third flow path at E-E of FIG. 1;
FIG. 12 is a schematic cross-sectional view of a third combined flow path formed at E-E in FIG. 1;
fig. 13 is a schematic structural view of a second heat exchange plate according to an embodiment of the present application;
fig. 14 is a schematic structural view of a third heat exchange plate according to an embodiment of the present application;
Fig. 15 is an enlarged schematic view of the structure at Y in fig. 14.
Reference numeral 1, a plate body; 2, a flow guiding area, 3, a first angle hole, 4, a second angle hole, 5, a heat exchange area, 5-1, a heat exchange auxiliary area, 5-2, a heat exchange main area, 6, a first runner, 6-1, a first crest, 6-2, a first trough, 7, a second runner, 7-1, a second crest, 7-2, a second trough, 8, a third runner, 8-1, a third crest, 8-2 and a third trough.
Detailed Description
The present application will be further described in detail below with reference to specific embodiments and with reference to the accompanying drawings, in order to make the objects, technical solutions and advantages of the present application more apparent.
It should be noted that unless otherwise defined, technical or scientific terms used in the embodiments of the present application should be given the ordinary meaning as understood by one of ordinary skill in the art to which the present application belongs. The terms "first," "second," and the like, as used in embodiments of the present application, do not denote any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that elements or items preceding the word are included in the element or item listed after the word and equivalents thereof, but does not exclude other elements or items. The terms "connected" or "connected," and the like, are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", etc. are used merely to indicate relative positional relationships, which may also be changed when the absolute position of the object to be described is changed.
The gasket plate type heat exchanger is equipment formed by stacking heat exchange plates, and mainly has the functions of realizing heat exchange of cold and hot media and achieving the purpose of energy transfer, in the use process of the heat exchanger, the uniformity of flow distribution of the media directly influences the heat transfer efficiency of the heat exchange plates and the service life of the plates, and the conventional heat exchange plates have different flow distances from corner holes to heat exchange areas, so that the distribution of fluid in the heat exchange areas is uneven, the heat exchange effect is seriously reduced, and the service life is reduced.
In the process of realizing the application, the distribution of the fluid in the heat exchange area is uneven, so that the plate forms a low flow rate area similar to a triangle in the heat exchange area far away from the corner holes, the larger the width of the plate width is, the larger the diameter of the corner holes is, the smaller the included angle of the flow channel corrugation is, the larger the distance difference between two side flows is, the larger the along-way resistance difference is, the formed low flow rate area is also, the heat exchange effect is seriously reduced, even the plate is partially supercooled or overheated due to the existence of the low flow rate area, the heat transfer effect is poor, the plate is easily partially fouled, the plate is prematurely failed, and the service life is reduced.
The heat exchange plate is improved in the related art, but the influence of flow distribution in a low flow velocity area is ignored, for example, in some technologies, a variable angle and a cambered raised flow guide strip facing the heat exchange area are arranged in the flow guide area of the plate body, so that fluid distribution is more uniform, the flow distribution performance is improved after the flow guide strip is arranged, meanwhile, the flow resistance of the whole plate can be obviously increased, the pressure drop is increased, the product can not meet the pressure drop requirement for a plurality of application occasions requiring severe pressure drop, the energy consumption of equipment is increased, and the operation cost is increased, and in other technologies, channels with unequal widths are arranged on the whole heat exchange area, so that the flow distribution in the low flow velocity area is improved, but the targeted flow distribution adjustment can not be carried out according to the distribution characteristics of the triangular low flow velocity area, the adjusted width is limited by the quantity of herringbone corrugated areas and the length of the block broken ribs of the heat exchange area, and meanwhile, the effect of flow distribution adjustment can not be ideal according to the degree of flow non-uniformity in the length direction of the plate body.
The following describes the technical solution of the present application in detail by specific embodiments in conjunction with fig. 1 to 14.
In some embodiments of the present application, as shown in fig. 1 and 2, a heat exchange plate is provided, and the heat exchange plate comprises a plate body 1, wherein two sides of the plate body 1 along the length direction are respectively provided with a diversion area 2, each diversion area 2 is respectively communicated with a first corner hole 3, a heat exchange area 5 is communicated between two diversion areas 2, the heat exchange area 5 comprises a heat exchange auxiliary area 5-1 arranged at a corner and a heat exchange main area 5-2 communicated with the heat exchange auxiliary area 5-1, the width of the heat exchange auxiliary area 5-1 is smaller than or equal to 1/3 of the width of the heat exchange area 5, the length of the heat exchange auxiliary area 5-1 is smaller than or equal to 1/3 of the length of the heat exchange area 5, a first flow channel 6 is arranged in the heat exchange main area 5-2, and a second flow channel 7 is arranged in the heat exchange auxiliary area 5-1 far from the first corner hole 3, and the cross section area of the second flow channel 7 is larger than the cross section of the first flow channel 6.
The heat exchange plate comprises a plate body 1, as shown in fig. 1, wherein the plate body 1 is a rectangular plate, the specific direction is not limited, the L direction in the drawing represents the length direction of the plate body 1, the W direction represents the width direction of the plate body 1, two ends of the plate body 1 are provided with flow guiding areas 2, each flow guiding area 2 is communicated with a first angle hole 3, the first angle holes 3 are used for fluid to enter and exit, two first angle holes 3 are positioned on the same side of the plate body 1 as shown in the drawing, fluid flows in from the first angle holes 3 above and flows out from the first angle holes 3 below, the two first angle holes 3 can be arranged opposite along the diagonal of the plate body 1, the specific direction is not limited, a second angle hole 4 is arranged outside the flow guiding areas 2, the second angle holes 4 are matched with the first angle holes 3 of the second heat exchange plate to form fluid inlet and outlet ports, a heat exchange area 5 is communicated between the two flow guiding areas 2, the heat exchange area 5 is in a rectangular runner, and the heat exchange area 5 is provided with a herringbone runner for fluid to exchange.
The heat exchange area 5 comprises a heat exchange auxiliary area 5-1 arranged at the corners and a heat exchange main area 5-2 communicated with the heat exchange auxiliary area 5-1, as shown in fig. 1, the heat exchange auxiliary area 5-1 is arranged at four corners of the heat exchange area 5, as shown in fig. 13, the heat exchange auxiliary area 5-1 is arranged at two corners of the heat exchange area 5 and is opposite to each other along the width direction of the plate body 1, the area except the heat exchange auxiliary area 5-1 in the heat exchange area 5 is the heat exchange main area 5-2, the shape of the heat exchange auxiliary area 5-1 is triangular or wedge-shaped, for example, without limitation, the width of the heat exchange auxiliary area 5-1 is smaller than or equal to 1/3 of the width of the heat exchange area 5, for example, the width of the heat exchange auxiliary area 5-1 is equal to 1/3, 1/4 or 1/5 of the length of the heat exchange area 5, etc., without limitation, and the length of the heat exchange auxiliary area 5-1 is smaller than or equal to 1/3, 1/5 of the length of the heat exchange area 5, etc.
Because the path lengths of the fluid from the first corner hole 3 to the heat exchange area 5 through the flow guiding area 2 are different, the fluid flow speed is lower in the area of the heat exchange area 5 far away from the first corner hole 3, namely, the area corresponding to the low flow speed of the fluid in the heat exchange area 5 is arranged far away from the first corner hole 3 or near the second corner hole 4, the heat exchange main area 5-2 is the area where the fluid in the heat exchange area 5 normally flows, as shown in fig. 1, the heat exchange main area 5-2 comprises the area between the two heat exchange auxiliary areas 5-1 along the length direction of the plate body 1, and the fluid also normally flows in the area, and in addition, the heat exchange auxiliary area 5-1 near the first corner hole 3 or far away from the second corner hole 4 is also the area where the fluid in the heat exchange area 5 normally flows because of being near the distance from the first corner hole 3.
The heat exchange main area 5-2 is internally provided with a first flow passage 6, at least one heat exchange auxiliary area 5-1 far away from the first corner hole 3 is internally provided with a second flow passage 7, as shown in fig. 1, the heat exchange auxiliary areas 5-1 at the upper left and lower left in the figure are internally provided with the second flow passage 7, as shown in fig. 13, only the heat exchange auxiliary area 5-1 at the upper left in the figure is internally provided with the second flow passage 7, by arranging the cross section area of the second flow passage 7 to be larger than the cross section area of the first flow passage 6, when fluid flows through the heat exchange auxiliary area 5-1 far away from the first corner hole 3, the flow resistance can be reduced, the flow speed is improved, the flow distribution of the fluid in the whole heat exchange area 5 is more uniform, the heat exchange effect is improved, the local supercooling or overheating of the plate body 1 is improved, the local scale is eliminated, the service life of the plate is prolonged, the flow pressure drop of the whole plate is reduced, the purpose of reducing the product running energy consumption is achieved compared with the design of the channel with the whole heat exchange area 5 which is provided with unequal width, the flow distribution adjustment can be carried out in a targeted mode, the flow distribution is not limited by the number of the heat exchange area and the number of the heat exchange area is not limited by the number of the heat exchange area, the heat exchange area is not limited by the length of the corrugated area, and the corrugated area is not uniform in the flow area is not regulated and the flow can be regulated and the flow is in the uniform.
The heat exchange plate is simple in structure, fluid in the heat exchange area 5 is uniformly distributed by adjusting the sectional area of the flow channel of the heat exchange auxiliary area 5-1, the heat exchange effect is good, the service life is long, meanwhile, the pressure drop of the heat exchanger is smaller, and the operation energy consumption is saved.
In some embodiments, as shown in fig. 2 to 8, the first flow channel 6 includes first peaks 6-1 and first valleys 6-2 alternately arranged, the second flow channel 7 includes second peaks 7-1 and second valleys 7-2 alternately arranged, the first peaks 6-1 have a width equal to the width of the first valleys 6-2, the second peaks 7-1 have a width equal to the width of the first peaks 6-1, and the second valleys 7-2 have a width greater than the width of the first valleys 6-2.
As shown in fig. 2 and 3, the first flow channel 6 includes first peaks 6-1 and first valleys 6-2 alternately arranged, the first peaks 6-1 have a width DA, the first valleys 6-2 have a width DA, and the first peaks 6-1 have a width equal to the width of the first valleys 6-2, i.e., da=da.
As shown in fig. 2 and 5, the second flow channel 7 comprises second wave crests 7-1 and second wave troughs 7-2 which are alternately arranged, the width of the second wave crests 7-1 is DB, the width of the second wave troughs 7-2 is DB, the width of the second wave crests 7-1 is the same as the width of the first wave crests 6-1, namely da=db, the width of the second wave troughs 7-2 is larger than the width of the first wave troughs 6-2, namely DB > DA, so that the cross section area of the second flow channel 7 is ensured to be larger than the cross section area of the first flow channel 6, the flow resistance of the heat exchange auxiliary area 5-1 far away from the first corner hole 3 is further reduced, the pitch of the second flow channel 7 is enabled to be larger than the pitch of the first flow channel 6, if the pitch is designed to be equal, the width of the second wave crests 7-1 is enabled to be smaller than the width of the first wave crests 6-1 under the condition that the increase of the flow channel cross section area is ensured, the pressure bearing effect is reduced, in addition, the width of the first wave crests 6-1 is enabled to be equal to the width of the second wave crests 7-1, the cross section area is enabled to be larger than the width of the second wave crests 7-1, the cross section area is enabled to be equal to the width of the second wave crests 7-1, the heat exchange auxiliary heat exchange area is enabled to be required to be smaller than the heat exchange area 5-plate surface area 5-1, and the heat exchange area is required to be closer to the heat exchange area than the heat exchange area 2 to the main heat exchange area 2 and the heat exchange area 2.
In some embodiments, as shown in fig. 2 to 8, the direction in which the second flow channels 7 extend to the outside of the plate body 1 is a first direction, the length direction of the plate body 1 from the flow guiding region 2 to the heat exchanging region 5 is a second direction, the width of the same second trough 7-2 gradually decreases along the first direction, and/or the width of the plurality of second trough 7-2 gradually decreases along the second direction.
As shown in fig. 2, the Z direction is the first direction, the L1 direction is the second direction, as shown in fig. 5, the cross-section of the second flow channel 7 at B-B in fig. 2 is schematic, the width of the second peak 7-1 is DB, the width of the second trough 7-2 is DB, as shown in fig. 7, the cross-section of the second flow channel 7 at C-C in fig. 2 is schematic, the width of the second peak 7-1 is DC, db=dc, DB < DC, i.e. the width of the same second trough 7-2 is gradually reduced along the first direction, thus forming an open second flow channel 7, so that fluid is easier to flow at C-C, avoiding being abraded and blocked at C-C, ensuring fluid regulation effect, if DB > DC is set, because the cross-sectional area of the flow channel at C-C is large, the fluid flow rate at C-C is high, the abrasion and blocking is extremely easy to cause the regulation effect of the whole flow channel 7 when the solid content of the fluid is high, and the fluid is set up to DB < DC, and the whole flow channel 7 is not affected at the edge of the second flow channel even if DB < B-B is not set at the edge of the second flow channel 1.
As shown in fig. 2, d1 and d2 are the widths of the second trough 7-2, and d2> d1 is set along the direction L1, that is, the widths of the second trough 7-2 are gradually reduced along the second direction, so that the second flow channel 7 forms an open second flow channel 7, and the fluid adjusting effect is ensured, because the wider the width of the second trough 7-2 is set along the direction L2, the larger the flow channel sectional area can be provided, the adjusting effect is increased, and the overall fluid distribution of the heat exchange area 5 is balanced.
In some embodiments, the maximum width of the same said second trough 7-2 is less than or equal to 1.5 times the minimum width of that second trough 7-2.
The maximum width of the second trough 7-2 is dC, the minimum width of the same second trough 7-2 is dB, and the maximum width of the same second trough 7-2 is set to be less than or equal to 1.5 times the minimum width of the second trough 7-2, that is, dB < dC is less than or equal to 1.5dB, for example, dc=1.5 dB, 1.4dB, 1.3dB, 1.2dB, or 1.1dB, or the like, which is not limited specifically, under the condition that the size of the heat exchange auxiliary area 5-1 is fixed, the excessive opening of the single second flow channel 7 can be avoided, the number of the second flow channels 7 is reduced, and the heat exchange effect is further affected.
In some embodiments, as shown in fig. 2 and 15, the angle between the first flow channel 6 and the longitudinal direction of the plate body 1 is β, the angle between the second flow channel 7 and the longitudinal direction of the plate body 1 is α, when the directions from the first angular hole 3 to the second flow channel 7 are in the same direction as the first direction, α is smaller than β, and α corresponding to a plurality of second flow channels gradually increases along the second direction, otherwise α is larger than β, and α corresponding to a plurality of second flow channels gradually decreases along the second direction.
As shown in fig. 1 and 2, the direction P is the direction from the first angular hole 3 to the second flow channel 7, the direction Z is the first direction, the direction P and the direction Z are the same, the same direction is not strictly limited, an error of ±15° is allowed, in fig. 2, α1 and α2 are included angles between the second flow channel 7 and the length direction of the plate body 1, and in the direction L1, α2< α1 is set, that is, α corresponding to a plurality of second flow channels 7 is set to gradually increase along the second direction, so that the width of the same second trough 7-2 along the first direction can be ensured to gradually decrease, and α < β is set, so that fluid is easy to flow in the second flow channel 7, and the adjusting effect is ensured.
As shown in fig. 14 and 15, the direction P is the direction from the first angular hole 3 to the second flow channel 7, the direction Z is the first direction, the direction P intersects with the direction Z and is different, in fig. 15, α1 and α2 are the angles between the second flow channel 7 and the length direction of the plate body 1, and α2> α1 is set along the direction L1, that is, the α corresponding to the plurality of second flow channels 7 is set to gradually decrease along the second direction, so that the width of the same second trough 7-2 along the first direction can be ensured to gradually decrease, and α > β is set to ensure that the area of the second flow channel changes.
In some embodiments, as shown in fig. 2, the heat exchange auxiliary area 5-1 gradually decreases in width along the second direction.
Through simulation and actual test, the low flow velocity region formed by the fluid in the heat exchange region 5 gradually narrows along the L1 direction, the width of the heat exchange auxiliary region 5-1 gradually decreases along the second direction to be matched with the low flow velocity region, the low flow velocity fluid is more suitable for adjustment, the distribution of the fluid in the heat exchange region 5 is uniform, and the heat exchange effect is improved.
In some embodiments, as shown in fig. 2, 13 and 14, the heat exchange auxiliary area 5-1 is in the shape of a right triangle, a right trapezoid or a trapezoid.
As shown in fig. 2, the heat exchange auxiliary area 5-1 is in the shape of an irregular convex quadrilateral, namely the wedge-shaped, and the wedge-shaped is formed by four sides, wherein two sides are right-angle sides of the heat exchange area 5, the other side is the runner edge of the second runner 7, and the other side is a broken rib, and the shape is closer to the actual distribution shape of the low flow velocity area, so that the distribution effect of the exchange fluid is higher.
As shown in fig. 13, the heat exchange auxiliary area 5-1 is in a right trapezoid shape, and the right trapezoid is composed of four sides, two sides are right-angle sides of the heat exchange area 5, and the other two sides are broken ribs, and the shape is relatively close to the actual distribution shape of the low flow velocity area, and is easy to design and manufacture.
As shown in FIG. 14, the heat exchange auxiliary area 5-1 is in the shape of a right triangle, and the right trapezoid is composed of three sides, two of which are right-angle sides of the heat exchange area 5, and the other one is a broken rib.
In some embodiments, the shape of the heat exchange auxiliary area 5-1 may be a fan shape, and the like, which is not particularly limited.
In some embodiments, the area of the auxiliary heat exchange region 5-1 is positively correlated with the width of the heat exchange region 5, the difference in width between the second trough 7-2 and the first trough 6-2 is positively correlated with the width of the heat exchange region 5, the difference between beta and alpha is positively correlated with the width of the heat exchange region 5, the area of the auxiliary heat exchange region 5-1 is negatively correlated with beta, the difference in width between the second trough 7-2 and the first trough 6-2 is negatively correlated with beta, and the difference between beta and alpha is negatively correlated with beta.
The wider the heat exchange area 5 is, the larger the path difference of the flow guiding area 2 is, the more serious the formed low flow velocity area is, the larger the area of the heat exchange auxiliary area 5-1 is arranged, the fluid adjusting effect can be ensured, the heat exchange effect is improved, the larger the width difference of the second trough 7-2 and the first trough 6-2 is arranged, the larger the formed opening is, the fluid adjusting effect is improved, and the larger the difference of beta and alpha is arranged in the same way, so that the fluid flows in the second flow channel 7 more easily, and the fluid adjusting effect is improved.
The smaller β represents that the smaller the angle between the first flow channel 6 and the length direction of the plate body 1, the easier the fluid flows in the first flow channel 6, the more serious the corresponding low flow velocity region is formed, the larger the area of the heat exchange auxiliary region 5-1 is set, the fluid adjusting effect can be ensured, the heat exchange effect is improved, the larger the difference between the widths of the second trough 7-2 and the first trough 6-2 is set, the larger the opening formed is, the fluid adjusting effect is improved, the larger the difference between β and α is set, the fluid flows in the second flow channel 7 more easily, the fluid adjusting effect is improved, the difference between β and α is, for example, 0.1 ° to 1 °, when the heat exchange plate is a large angle plate, and when β is a small angle plate, β - α1|=0.2 ° can be set, and when β is 25 ° to 35 °, β is a small angle plate, and |β - α1|=0.4°.
In some embodiments, as shown in fig. 1, a third flow passage 8 is disposed in at least one heat exchange auxiliary area 5-1 near the first corner hole 3, and a cross-sectional area of the third flow passage 8 is equal to a cross-sectional area of the first flow passage 6.
The heat exchange auxiliary area 5-1 arranged close to the first corner hole 3 or far from the second corner hole 4 is a region where fluid in the heat exchange area 5 normally flows because of being closer to the first corner hole 3, at least one heat exchange auxiliary area 5-1 is internally provided with a third flow passage 8, as shown in fig. 1, the heat exchange auxiliary areas 5-1 at the upper right and the lower right in the figure are internally provided with the third flow passage 8, as shown in fig. 13, only the heat exchange auxiliary area 5-1 at the upper right in the figure is internally provided with the third flow passage 8, the cross section of the third flow passage 8 is equal to the cross section of the first flow passage 6, the influence on the fluid flow is avoided, and in addition, compared with the cross section of the flow passage in the region, the increase of the fluid pressure drop can be avoided.
In some embodiments, as shown in fig. 3 to 12, the first flow channel 6 includes first peaks 6-1 and first troughs 6-2 alternately arranged, the third flow channel 8 includes third peaks 8-1 and third troughs 8-2 alternately arranged, the width of the first peaks 6-1 is equal to the width of the first troughs 6-2, the width of the third peaks 8-1 is greater than the width of the first peaks 6-1, and the width of the third troughs 8-2 is equal to the width of the first troughs 6-2.
As shown in fig. 2 and 3, the first flow channel 6 includes first peaks 6-1 and first valleys 6-2 alternately arranged, the first peaks 6-1 have a width DA, the first valleys 6-2 have a width DA, and the first peaks 6-1 have a width equal to the width of the first valleys 6-2, i.e., da=da.
As shown in fig. 2 and 9, the third flow channel 8 includes third wave crests 8-1 and third wave troughs 8-2 which are alternately arranged, the width of the third wave crests 8-1 is DD, the width of the third wave troughs 8-2 is DD, the width of the third wave crests 8-1 is larger than the width of the first wave crests 6-1, namely DA < DD, the width of the third wave troughs 8-2 is equal to the width of the first wave troughs 6-2, namely dd=da, so that the cross section area of the third flow channel 8 is ensured to be equal to the cross section area of the first flow channel 6, the fluid distribution of the heat exchange auxiliary area 5-1 and the heat exchange main area 5-2 is avoided, in addition, the width of the third wave crests 8-1 is set to be larger than the width of the first wave crests 6-1, so that the heat exchange auxiliary area 5-1 of the lower plate surface of the plate body 1 is larger than the flow channel cross section area of the heat exchange main area 5-2, and for the lower plate surface, the heat exchange auxiliary area 5-1 is far from the first corner hole 3 of the second heat exchange plate, and flow adjustment is required to ensure the heat exchange effect.
In some embodiments, the direction in which the third flow channel 8 extends to the outside of the plate body 1 is a third direction, the third direction is axisymmetric to the first direction, the length direction of the plate body 1 along the flow guiding region 2 to the heat exchanging region 5 is a second direction, the width of the same third peak 8-1 gradually decreases along the third direction, and/or the width of a plurality of third peaks 8-1 gradually decreases along the second direction.
Fig. 9 is a schematic cross-sectional view of the third flow channel 8 at D-D in fig. 2, where the width of the third peak 8-1 is DD, the width of the third trough 8-2 is DD, fig. 11 is a schematic cross-sectional view of the third flow channel 8 at E-E in fig. 2, where the width of the third peak 8-1 is DE, the width of the third trough 8-2 is DE > DD, de=dd, i.e. the same width of the third peak 8-1 is gradually decreased along the third direction, and the third peak 8-1 corresponds to the second trough 7-2, because the third peak 8-1 and the second trough 7-2 form an open second combined flow channel for adjusting the fluid distribution.
Similarly, the width of the third wave crests 8-1 gradually decreases along the second direction, which corresponds to the second wave troughs 7-2, and the third wave crests 8-1 and the second wave troughs 7-2 form a second combined flow passage with openings for adjusting the fluid distribution.
In some embodiments of the application, a heat exchanger is provided comprising a stack of heat exchanger plates as described in any of the embodiments above.
Through stacking the heat exchange plates, a net-shaped combined runner can be formed, the heat exchange effect is improved, scale deposition is prevented, the heat transfer effect of the heat exchange plates is good, and the service life is long.
The first trough 6-2 of the first heat exchange plate and the first peak 6-1 of the second heat exchange plate form a first combined flow passage as shown in fig. 4, the second trough 7-2 of the first heat exchange plate and the third peak 8-1 of the second heat exchange plate form a second combined flow passage with a sectional area larger than that of the first combined flow passage as shown in fig. 6 and 8, and the third trough 8-2 of the first heat exchange plate and the second peak 7-1 of the second heat exchange plate form a third combined flow passage with a sectional area equal to that of the first combined flow passage as shown in fig. 10 and 12.
It will be appreciated by persons skilled in the art that the foregoing discussion of any embodiment is merely exemplary and is not intended to imply that the scope of the application (including the claims) is limited to these examples, that combinations of technical features in the foregoing embodiments or in different embodiments may be implemented in any order and that many other variations of the different aspects of the embodiments described above exist within the spirit of the application, which are not provided in detail for clarity.
In addition, where details are set forth to describe example embodiments of the application, it will be apparent to one skilled in the art that embodiments of the application may be practiced without, or with variation of, these details. Accordingly, the description is to be regarded as illustrative in nature and not as restrictive.
While the application has been described in conjunction with the embodiments thereof, many alternatives, modifications, and variations of those embodiments will be apparent to those skilled in the art in light of the foregoing description.
The present embodiments are intended to embrace all such alternatives, modifications and variances which fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, and the like, which are within the spirit and principles of the embodiments of the application, are intended to be included within the scope of the application.
Claims (10)
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| CN2890822Y (en) * | 2005-12-02 | 2007-04-18 | 缪志先 | Detachable plate type heat exchanger with low flow resistance structure |
| CN100516758C (en) * | 2007-06-12 | 2009-07-22 | 缪志先 | Strip-free plate-fin heat exchanger |
| CN202734644U (en) * | 2012-07-19 | 2013-02-13 | 上海尔华杰机电装备制造有限公司 | Heat exchanger plate sheet with large flow rate and low resistance drop |
| CN207035928U (en) * | 2017-11-01 | 2018-02-23 | 上海板换机械设备有限公司 | A kind of heat exchanger plates and its heat exchanger |
| JP2019100686A (en) * | 2017-12-08 | 2019-06-24 | 株式会社日阪製作所 | Plate type heat exchanger |
| KR102389234B1 (en) * | 2020-07-16 | 2022-04-21 | 디에이치피이엔지 주식회사 | Structure for combining heat plate with gasket of a plate type heat exchanger |
| CN114485249A (en) * | 2022-02-28 | 2022-05-13 | 上海板换机械设备有限公司 | Unequal-section heat exchange plate and heat exchanger |
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