CN109470074B - Fin group and fin tube type heat exchanger - Google Patents

Fin group and fin tube type heat exchanger Download PDF

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Publication number
CN109470074B
CN109470074B CN201710802266.1A CN201710802266A CN109470074B CN 109470074 B CN109470074 B CN 109470074B CN 201710802266 A CN201710802266 A CN 201710802266A CN 109470074 B CN109470074 B CN 109470074B
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fin
tube
fluid
heat exchange
curved side
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CN109470074A (en
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赵中闯
岳宝
欧汝浩
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Midea Group Co Ltd
Guangdong Midea White Goods Technology Innovation Center Co Ltd
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Midea Group Co Ltd
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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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The invention provides a fin group and a fin tube type heat exchanger, wherein the fin group comprises: at least one fin, each fin comprising: each pipe hole group comprises at least one pipe hole, and each pipe hole penetrates through two sides of each fin; the fin is provided with a first concave-convex corrugation on a first section in the flowing direction of the fluid; the fins are in second concave-convex corrugations at a second section perpendicular to the fluid flowing direction; the first concave-convex corrugation and the second concave-convex corrugation have different wave amplitudes, pipe holes of two adjacent fins are coaxial, and the distance between the two adjacent fins is the same. The finned tube heat exchanger further comprises: the heat exchange tube is sleeved in the tube hole of the fin group. Through the technical scheme of the invention, the heat exchange area of the fin group can be increased, meanwhile, the second concave-convex corrugation is utilized to enable the fluid to continuously destroy and develop a new boundary layer, and the first concave-convex corrugation is utilized to reduce the characteristic dimension of heat exchange, so that the heat exchange performance of the fin group is improved.

Description

Fin group and fin tube type heat exchanger
Technical Field
The invention relates to the technical field of heat exchangers, in particular to a fin group and a fin tube type heat exchanger.
Background
The fin tube type heat exchanger is very widely applied, flat fins are mostly adopted in common fin tube type heat exchangers, the heat resistance occupation ratio of the air side of the fin tube type heat exchanger adopting the flat fins is the largest, the heat exchange coefficient of the air side is lower, and corrugated fins and slotted fins are mostly adopted for improving the heat exchange performance of the fin tube type heat exchanger. However, although the heat exchange coefficient of the air side of the common corrugated fin is improved compared with that of a flat fin, the improvement is very limited, and the heat exchange performance of the fin-tube heat exchanger cannot be obviously improved; the slotted fin can greatly improve the heat exchange coefficient of the air side, but the problem of frosting can exist under the low-temperature working condition, and the manufacturing process is complex.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art or the related art.
In view of the above, it is an object of the present invention to provide a fin set.
Another object of the present invention is to provide a finned tube heat exchanger.
In order to achieve the above object, according to a first aspect of the present invention, there is provided a fin group, including: at least one fin, each fin comprising: each pipe hole group comprises at least one pipe hole, and each pipe hole penetrates through two sides of each fin; the fin is provided with a first concave-convex corrugation on a first section in the flowing direction of the fluid; the fins are in second concave-convex corrugations at a second section perpendicular to the fluid flowing direction; the first concave-convex corrugation and the second concave-convex corrugation have different wave amplitudes, pipe holes of two adjacent fins are coaxial, and the distance between the two adjacent fins is the same.
In the technical scheme, when fluid flows between the fins for heat exchange, the first concave-convex corrugations can reduce the characteristic size of the flowing heat exchange between the fluid and the fins so as to strengthen the heat exchange, and the second concave-convex corrugations enable the fluid to continuously change the movement direction under the action of the fins in the movement process, so that on one hand, the fluid continuously breaks and develops a new boundary layer so as to strengthen the heat exchange on the surfaces of the fins; on the other hand, the fluid continuously impacts the surface of the fin, so that the possibility of scaling on the surface of the fin can be reduced, and the heat exchange performance of the fin group is more stable. The amplitudes of the first concave-convex corrugation and the second concave-convex corrugation are set to be reasonable values according to the design requirements of the fin group, the amplitudes of the first concave-convex corrugation and the second concave-convex corrugation are different, when fluid flows between fins, the flowing direction of the fluid is not easy to change due to the fact that the amplitudes of the first concave-convex corrugation and the second concave-convex corrugation are different, the situation that the flowing direction of the fluid among the fins is reduced or even a backflow area appears due to the fact that the flowing direction is changed in the flowing process of the fluid is reduced, on one hand, the flowing direction of the fluid among the fins is limited, the heat exchange performance of the fin group is improved, the heat exchange performance of the fin group is more stable, on the other hand, the kinetic energy loss of the fluid among the fins is reduced, the fluid can more easily pass through the fins, the requirement for the initial speed. Meanwhile, the first concave-convex corrugations and the second concave-convex corrugations can increase the heat exchange area of the fins, so that the heat exchange performance of the fin group is improved. The tube holes of two adjacent fins are coaxial so that the tubes can be arranged in the fin group, and the fin group is convenient to apply to the tube type heat exchanger. And meanwhile, the distance between two adjacent fins is the same, so that the fluid between the fins flows stably, and all parts of the fins exchange heat uniformly.
The heat exchanger is a single-row tube heat exchanger when each tube hole group corresponds to one tube hole, and the heat exchanger is a multi-row tube heat exchanger when each tube hole group corresponds to a plurality of tube holes.
Wherein, it should be pointed out that the thickness of fin can be confirmed according to the design needs of fin group, and when fin thickness was inhomogeneous, the fin left and right sides first unsmooth ripple was different with the second unsmooth ripple, therefore the heat transfer performance of fin left and right sides is also different.
In the above technical solution, preferably, the upper edge and the lower edge of the fin in any first cross section are the same distance in the axial direction of the tube hole.
In the technical scheme, the fins in the fin group are uniform in thickness, and the thickness and the shape of all the fins in the fin group are the same, so that the types of dies used for producing the fins are reduced, the fins are convenient to manufacture, and the fins are convenient to replace in the maintenance process of the fin group.
In the above technical solution, preferably, each of the pipe orifice groups includes: a first tube hole; the second pipe hole is in a first distance with the first pipe hole along the fluid flowing direction, and the second pipe hole is in a second distance with the first pipe hole along the direction vertical to the fluid flowing direction; the first distance is nonzero, the number of the pipe hole groups is multiple, and the pipe hole groups are arrayed along the fluid flow direction and the direction perpendicular to the fluid flow direction respectively.
In the technical scheme, the first pipe hole and the second pipe hole in each pipe hole group are at a nonzero first distance in the flowing direction of the fluid and at a second distance in the direction perpendicular to the flowing direction of the fluid, the fluid flowing through the pipe hole groups can be disturbed by setting the first distance and the second distance, the fluid is promoted to be damaged, a new boundary layer is developed, the heat exchange effect of the fluid and the fin group is improved, and when the heat exchange effect is improved, the flow of heat in a heat carrier in the pipe holes can be improved under the same heat exchange requirement, so that the heat exchange efficiency of the fin group is improved.
The number of the pipe hole groups is multiple, and the pipe hole groups are arrayed along the fluid flow direction and the direction perpendicular to the fluid flow direction respectively. The array interval, the first distance and the second distance of the tube hole group determine arrangement of tube holes in the fin group, and by setting numerical values of the array interval, the first distance and the second distance, on one hand, heat exchange area can be increased through the side faces of the tube holes, on the other hand, the position relation of the tube holes in the tube hole group and the array distance among the tube hole groups are reasonably set, so that the tube holes can disturb fluid among fins, the fluid is continuously damaged and develops a new boundary layer by matching with second concave-convex corrugations, and the heat exchange performance of the fin group is improved. Meanwhile, the volume of the heat carrier passing through the fin group in unit time is determined by the number of the pipe holes, and the number of the pipe holes is required to be as large as possible on the premise of ensuring the heat exchange efficiency, so that more heat carriers in the fin group in unit time exchange heat, and the heat exchange efficiency of the fin group is improved.
In the above technical solution, preferably, two ends of the fin in the fluid flowing direction are a first end and a second end, respectively, if the fluid flows from the first end to the second end, the first concave-convex corrugations at two sides of the first tube hole are bent to form a first bent side and a second bent side, and the first bent side and the second bent side intersect at the first termination point; wherein a distance between the first curved side and the second curved side gradually decreases from the first end to the second end.
In the technical scheme, the first bent side and the second bent side form a flow guide structure, and when fluid flows from the first end to the second end, part of the fluid on two sides of the first pipe hole is guided to one side, close to the second end, of the first pipe hole, so that the heat transfer of the weak side of the first pipe hole, namely one side, which cannot be directly contacted with the fluid in the flow direction during the flowing of the fluid, is strengthened, and the heat exchange performance of the fin group is improved.
It is to be noted, among other things, that the drainage effect of the first curved side and the second curved side differs with respect to the different positions of the first termination point. The position of the first termination point can be set according to the properties of fluid among the fins and the position among the tube holes, so that the flow of the fluid among the fins can be better regulated, and the heat exchange performance of the fin group is improved.
In the above technical solution, preferably, the first termination point is collinear with a center of the first pipe hole in the fluid flow direction.
In the technical scheme, the first termination point and the circle center of the first pipe hole are collinear in the fluid flowing direction, namely the first bending side and the second bending side are located on two sides of the circle center of the first pipe hole in the fluid flowing direction, at the moment, drainage of the first bending side and drainage of the second bending side are more average, fluid flowing of the heat exchange weak side of the first pipe hole is more uniform, and therefore the heat exchange effect of the heat exchange weak side of the first pipe hole is improved.
Wherein, preferably, the first curved side and the second curved side are symmetrical about a second cross section of the first pipe hole center.
In the above technical solution, preferably, if the fluid flows from the second end to the first end, the first concave-convex corrugations on both sides of the second pipe hole are bent to form a third bent side and a fourth bent side, and the third bent side and the fourth bent side intersect at the second termination point; wherein a distance between the third curved side and the fourth curved side gradually decreases from the second end to the first end.
In the technical scheme, the third bent side and the fourth bent side form a flow guide structure, and when fluid flows from the second end to the first end, part of the fluid on two sides of the second tube hole is guided to one side, close to the first end, of the second tube hole, so that heat transfer of the weak heat exchange side of the tube hole is strengthened, and the heat exchange performance of the fin group is improved. Meanwhile, the first bent side and the second bent side are matched, the flow direction of fluid among the fins is better controlled, and heat exchange of the heat exchange weak side of the fin group is increased.
It is to be noted, among other things, that the drainage effect of the third curved side and the fourth curved side differs with respect to the different position of the second termination point. The position of the first termination point can be set according to the properties of fluid among the fins and the position among the tube holes, so that the flow of the fluid among the fins can be better regulated, and the heat exchange performance of the fin group is improved.
The flow structure (namely the first concave-convex corrugation, the first bent side, the second bent side and the pipe hole group) which is sequentially passed by the fluid from the first end to the second end and the flow structure (namely the first concave-convex corrugation, the third bent side, the fourth bent side and the pipe hole group) which is sequentially passed by the fluid from the second end to the first end are consistent in sequence and have the same characteristics, so that the whole processing and installation of the heat exchanger are facilitated.
In the above technical solution, preferably, the second termination point and a center of the second pipe hole are collinear in the fluid flow direction.
In the technical scheme, the second termination point and the circle center of the second pipe hole are collinear in the fluid flowing direction, namely the third bending side and the fourth bending side are positioned on two sides of the circle center of the second pipe hole in the fluid flowing direction, at the moment, the drainage of the third bending side and the fourth bending side is more average, the fluid flowing of the heat exchange weak side of the pipe hole is more uniform, and therefore the heat exchange of the heat exchange weak side of the pipe hole is more uniform.
Wherein preferably the third curved side and the fourth curved side are symmetrical about a second cross-section through a centre of the second tube aperture.
In the above technical solution, preferably, the first concave-convex corrugation of the first pipe hole and/or the second pipe hole near the first end forms a fifth curved side and a sixth curved side, the first concave-convex corrugation of the first pipe hole and/or the second pipe hole near the second end forms a seventh curved side and an eighth curved side, the fifth curved side and the sixth curved side intersect at the third termination point, and the seventh curved side and the eighth curved side intersect at the fourth termination point.
Wherein, in the fluid flow direction, the distance between the fifth curved side and the sixth curved side gradually increases from the first end to the second end, and the distance between the seventh curved side and the eighth curved side gradually decreases from the first end to the second end.
In the technical scheme, a fifth bending side and a sixth bending side are arranged on one side, close to the first end, of the first pipe hole and/or the second pipe hole, a seventh bending side and an eighth bending side are arranged on one side, close to the second end, of the first pipe hole and/or the second pipe hole, the flow direction of fluid near the first pipe hole and the second pipe hole is adjusted, so that flowing heat transfer near the pipe holes is strengthened, and particularly, part of fluid on two sides of the first pipe hole and the second pipe hole is led to the heat exchange weak side of the first pipe hole and the second pipe hole, so that flowing heat exchange of the fluid on the heat exchange weak side is strengthened.
It should be noted that, corresponding to different schemes and different tube hole arrangement modes, the fifth bending side, the sixth bending side, the seventh bending side and the eighth bending side can not only strengthen the weak heat exchange side of the heat exchange tube, but also adjust the overall flow direction of the fluid between the fins, strengthen the heat exchange between the fluid and the fins, and improve the overall heat exchange performance of the fin group.
In the above technical solution, preferably, the third termination point and the center of the pipe hole are collinear in the fluid flow direction; and/or the fourth termination point and the center of the orifice are collinear in the direction of fluid flow.
In the technical scheme, when the third termination point and the center of the pipe hole are collinear in the fluid flowing direction, namely the fifth bending side and the sixth bending side are positioned at two sides of the center of the pipe hole in the fluid flowing direction, the drainage of the fifth bending side and the drainage of the sixth bending side are more average, the fluid flowing of the heat exchange weak side of the pipe hole is more uniform, and therefore the heat exchange of the heat exchange weak side of the pipe hole is more uniform.
Wherein preferably the fifth curved side and the sixth curved side are symmetrical about a second cross-section through the centre of the tube aperture.
When the fourth termination point and the center of the pipe hole are collinear in the fluid flowing direction, namely the seventh curved side and the eighth curved side are positioned at two sides of the center of the pipe hole in the fluid flowing direction, the drainage of the seventh curved side and the eighth curved side is more average at the moment, the fluid flowing at the weak side of the pipe hole heat exchange is more uniform, and therefore the heat exchange at the weak side of the pipe hole heat exchange is more uniform.
Wherein preferably the seventh curved side and the eighth curved side are symmetrical about a second cross-section through the centre of the tube aperture.
When the third termination point and the center of the pipe hole are collinear in the fluid flowing direction, and simultaneously, the fourth termination point and the center of the pipe hole are collinear in the fluid flowing direction, the fifth bending side, the sixth bending side, the seventh bending side and the eighth bending side are positioned on two sides of the center of the pipe hole in the fluid flowing direction, so that the fluid flowing of the heat exchange weak side of the pipe hole is more uniform, and the heat exchange of the heat exchange weak side of the pipe hole is more uniform.
Wherein preferably the fifth curved side and the sixth curved side are symmetrical about a second cross-section through the centre of the tube aperture, while the seventh curved side and the eighth curved side are symmetrical about a second cross-section through the centre of the tube aperture.
In the above technical solution, preferably, a ratio of a second distance between two adjacent wave troughs on the second cross section of the second concave-convex corrugation to a first distance between two adjacent wave troughs on the first cross section of the first concave-convex corrugation ranges from 4 to 12, and a numerical range of the first distance between two adjacent wave troughs on the first cross section of the first concave-convex corrugation ranges from 1 to 5 mm.
In the technical scheme, when the ratio of the second distance between two adjacent wave troughs of the second concave-convex corrugation on the second section to the first distance between two adjacent wave troughs of the first concave-convex corrugation on the first section is in the range of 4-12, the heat exchange performance of the fin is greatly improved due to the existence of the first concave-convex corrugation and the second concave-convex corrugation within the numerical range; the numerical range of the first distance between two adjacent wave troughs on the first section of the first concave-convex corrugation is 1-5 mm, so that the flowing heat exchange scale of fluid and the fins can be reduced, and the heat exchange is enhanced.
In the above technical solution, preferably, a first acute angle formed by a tangent line of any point of the first uneven corrugation on the first cross section and a tangent line of any one of the troughs on the first cross section is not greater than 75 °, and a second acute angle formed by a tangent line of any point of the second uneven corrugation on the second cross section and a tangent line of a lowest point of any one of the troughs on the second cross section is not greater than 30 °.
In this technical scheme, the tangent line of first unsmooth ripple at any point on first cross-section and the tangent line of any trough on the first cross-section are first acute angle and are not more than 75, reduce the flow heat transfer scale of fluid and fin to strengthen the heat transfer. The tangent line of any point of the second concave-convex corrugation on the second section and the tangent line of the lowest point of any wave trough on the second section form a second acute angle which is not more than 30 degrees, and in the angle range, the second concave-convex corrugation can break the boundary layer of the airflow, increase the heat exchange effect of the fluid and the fins, reduce the flow pressure loss of the fluid between the fins and reduce the energy consumption of the fluid between the fins during the flow heat exchange.
In the above technical solution, preferably, a ratio range of a first vertical distance from a trough of a first contour line of the first concave-convex corrugation on the first cross section to an adjacent crest to a pitch is 0 to 0.3, a ratio range of a second vertical distance from a trough of a second contour line of the second concave-convex corrugation on the second cross section to an adjacent crest to a pitch is 0.4 to 1.2, and a pitch range is 0.8 to 2.5 mm.
In this technical scheme, the interval is 0.8 ~ 2.5mm, and in this numerical range, can enough make the fluid between the fin can carry out good heat transfer with the fin, can make the fluidic flow between the fin again in reasonable scope, can satisfy the requirement to heat transfer effect and heat exchange efficiency among the operating condition. Simultaneously, the ratio range of the first vertical distance between the wave trough of the first contour line of the first concave-convex corrugation on the first section and the adjacent wave crest to the distance is 0-0.3, the ratio range of the second vertical distance between the wave trough of the second contour line of the second concave-convex corrugation on the second section and the adjacent wave crest to the distance is 0.4-1.2, so that fluid between the fins can increase the flowing heat exchange with the fins under the action of the first concave-convex corrugation and the second concave-convex corrugation, and the heat exchange performance of the fins is further improved.
In the above technical solution, preferably, a hole group pitch of two adjacent pipe hole groups in a fluid flow direction is in a range of 8 to 22mm, and a ratio of a second pitch of the second concave-convex corrugation to the hole group pitch is in a range of 0.2 to 0.5.
In the technical scheme, the hole group interval range of two adjacent pipe hole groups in the fluid flow direction is 8-22 mm, the pipe hole groups are in the interval range, a heat carrier in the pipe hole on one side can rapidly transfer heat to the fin, and then the fin and the fluid perform flow heat exchange, so that rapid heat exchange is realized, the heat exchange efficiency is improved, meanwhile, the ratio range of the second interval of the second concave-convex corrugation to the hole group interval is 0.2-0.5, the heat exchange efficiency can be further improved by the enhancement of the second concave-convex corrugation to the heat exchange effect in the ratio range, so that the heat exchange performance of the fin group can be still kept in a stable range when the hole group interval is changed, and the fin group can be suitable for more working conditions to meet more heat exchange requirements.
A second aspect of the present invention provides a finned tube heat exchanger, including any one of the fin groups in the first aspect, and further including: the heat exchange tube is sleeved in the tube hole of the fin group.
In the technical scheme, a heat carrier flows in the heat exchange tube, and fluid flows among the fins. The heat carrier transfers heat to the heat exchange tubes, the heat exchange tubes transfer heat to the fins through heat conduction, and then the fins and fluid between the tube holes and the fins perform flowing heat exchange. When fluid flows among the fins for heat exchange, the first concave-convex corrugations can reduce the characteristic size of the flowing heat exchange between the fluid and the fins so as to strengthen the heat exchange, and the second concave-convex corrugations enable the fluid to continuously change the movement direction under the action of the fins in the movement process, so that on one hand, the fluid continuously breaks and develops a new boundary layer so as to strengthen the heat exchange and improve the heat exchange coefficient of the surfaces of the fins; on the other hand, the fluid continuously impacts the surface of the fin, so that the possibility of scaling on the surface of the fin can be reduced, and the heat exchange performance of the fin group is more stable. The amplitudes of the first concave-convex corrugation and the second concave-convex corrugation are set to be the optimal values according to the design requirements of the fin group, and the amplitudes of the first concave-convex corrugation and the second concave-convex corrugation are different, so that heat exchange can be strengthened to the maximum extent by the first concave-convex corrugation and the second concave-convex corrugation, and the heat exchange performance of the fin group can be improved to the maximum extent. Meanwhile, the heat exchange area of the fin can be increased by the first concave-convex corrugations and the second concave-convex corrugations, so that the heat exchange performance of the fin group is improved. And meanwhile, the distance between two adjacent fins is the same, so that the fluid between the fins flows stably, and all parts of the fins exchange heat uniformly.
In the above technical solution, preferably, when the number of the orifice groups is plural, the plural orifice groups are arrayed in a direction perpendicular to the fluid flow direction; the distance between every two adjacent pipe hole groups along the direction perpendicular to the flowing direction of the fluid is 12-25 mm.
In this technical scheme, when the quantity of tube hole group is a plurality of, a plurality of tube hole groups are along perpendicular to fluid flow direction array, and every two adjacent tube hole groups are 12 ~ 25mm along the distance between the perpendicular to fluid flow direction this moment, and in this numerical range, can enough satisfy the requirement of trading the effect for heat carrier in the tube hole group carries out abundant heat transfer in the fin, and the flow of heat carrier is in reasonable within range when guaranteeing again to trade under the prerequisite of heat effect, improves heat exchange efficiency.
In the technical scheme, the inner diameter of the heat exchange tube is preferably within a range of 5-9 mm.
In the technical scheme, the range of the inner diameter of the heat exchange tube is 5-9 mm, the heat carrier in the heat exchanger can be ensured to carry out sufficient heat exchange within the numerical range, and the flow of the heat carrier in the heat exchanger can be increased, so that the heat exchange performance of the heat exchanger can meet the actual requirement.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
FIG. 1 shows a schematic structural view of a fin pack according to an embodiment of the present invention;
FIG. 2 shows a side view perpendicular to the direction of fluid flow according to another embodiment of the present invention;
FIG. 3 shows a side view in the direction of fluid flow according to yet another embodiment of the present invention;
FIG. 4 shows a schematic structural view of a fin pack according to yet another embodiment of the present invention;
FIG. 5 illustrates a top view of a fin set according to yet another embodiment of the present invention;
wherein, the correspondence between the reference numbers and the part names in fig. 1 to 5 is:
10 fin group, 102 tube hole group, 1022 first tube hole, 1024 second tube hole, 104 fin, 1042 first corrugation, 1044 fifth curved side, 1046 sixth curved side, 1048 third termination point, 1050 seventh curved side, 1052 eighth curved side, 1054 fourth termination point, 1056 second corrugation, 106 first end, 108 second end.
Detailed Description
So that the manner in which the above recited objects, features and advantages of the present invention can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to the embodiments thereof which are illustrated in the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.
Some embodiments according to the invention are described below with reference to fig. 1 to 5.
Example 1:
a fin group 10 according to an embodiment of the present invention includes: at least one fin 104, each fin 104 comprising: at least one tube hole set 102, each tube hole set 102 comprising at least one tube hole, each tube hole penetrating both sides of the fin 104; the fins 104 have a first corrugation 1042 in a first cross section along the fluid flow direction; the fins 104 have a second corrugation 1056 in a second cross-section perpendicular to the direction of fluid flow; wherein, the amplitudes of the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 are different, the pipe holes of two adjacent fins 104 are coaxial, and the distance F between two adjacent fins 104pThe same is true.
In this embodiment, when fluid performs flow heat exchange between the fins 104 shown in fig. 1, the first concave-convex corrugation 1042 shown in fig. 2 can reduce the characteristic dimension of the flow heat exchange between the fluid and the fins 104, so as to enhance the heat exchange, and the second concave-convex corrugation 1056 shown in fig. 3 enables the fluid to continuously change the movement direction under the action of the fins 104 during the movement process, so that on one hand, the fluid continuously breaks and develops a new boundary layer, so as to enhance the heat exchange, and improve the heat exchange coefficient of the surface of the fins 104; on the other hand, the fluid continuously impacts the surface of the fin 104, so that the possibility of scaling on the surface of the fin 104 can be reduced, and the heat exchange performance of the fin group 10 is more stable. The amplitudes of the first corrugations 1042 and the second corrugations 1056 are set to reasonable values according to the design requirements of the fin assembly 10, and the amplitudes of the two corrugations are different, so that when fluid flows between the fins 104, because the wave amplitudes of the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 are different, the flowing direction of the fluid is not easy to change, the condition that the flowing speed of the fluid among the fins 104 is reduced and even a backflow area occurs due to the change of the flowing direction in the flowing process of the fluid is reduced, on the one hand, the flow direction of the fluid between the fins 104 is well limited, the heat exchange performance of the fin group 10 is improved, the heat exchange performance of the fin group 10 is more stable, on the other hand, the kinetic energy loss of the fluid among the fins 104 is reduced, the fluid can more easily pass through the fins 104, and the requirement of the initial speed of the fluid entering the fins 104 during heat exchange of the fin group 10 is reduced, so that the energy consumption of the fluid conveying device is reduced. Meanwhile, the first concave-convex corrugations 1042 and the second concave-convex corrugations 1056 can increase the heat exchange area of the fin 104, so that the heat exchange performance of the fin group 10 is improved. The tube holes of two adjacent fins 104 are coaxial to enable the arrangement of tubes in the fin group 10, which facilitates the application of the fin group 10 in a tube heat exchanger.
The number of the pipe holes corresponding to each pipe hole group 102 may be one or multiple, when each pipe hole group 102 corresponds to one pipe hole, the heat exchanger is a single-row pipe heat exchanger, and when each pipe hole group 102 corresponds to multiple pipe holes, the heat exchanger is a multi-row pipe heat exchanger.
As shown in fig. 4, when the number of fins 104 in the fin group 10 is 2 or more, the distance F between two adjacent fins 104 is setpIs the same so thatThe fluid flow between the fins 104 is smooth.
Example 2:
in this embodiment, on the basis of embodiment 1, preferably, when the fin group 10 includes 3 or more than 3 fins 104, and when two adjacent fins 104 of the fin group 10 have different heat exchange requirements, during production, the adjustment of the heat exchange performance is realized by adjusting parameters of the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056, at this time, the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 of the two portions of the fin group 10 are not all the same, at this time, the fin 104 located at the boundary between the two portions of the fin 104 is different from the two portions of the fin 104, and the thickness of the fin 104 at the boundary is made non-uniform, so that the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 at the two sides of the fin 104 are the same as the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 of the adjacent fin 104, and thus the distance F between the fin 104 at the boundary and the adjacent fin 104 is thepAll can be equal everywhere.
The thickness of the fin 104 can be determined according to the design requirement of the fin group 10, and when the thickness of the fin 104 is uneven, the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 on the left and right sides of the fin 104 are different, so the heat exchange performance on the left and right sides of the fin 104 is also different, and this embodiment is only one of several embodiments.
Example 3:
in another embodiment of the present invention, on the basis of embodiment 1, preferably, when 2 or more than 2 fins 104 are included in the fin group 10, the upper edges of the fins 104 in any first cross section are the same as the lower edges in the axial direction of the tube holes.
In this embodiment, the fins 104 in the fin group 10 have uniform thickness, and the thickness and shape of all the fins 104 in the fin group 10 are the same, so that the variety of dies used for producing the fins 104 is reduced, the fins 104 can be conveniently manufactured, and the fins 104 can be conveniently replaced during the maintenance of the fin group 10.
Example 4:
in another embodiment of the present invention, based on embodiment 1, it is preferable that each of the groups of pipe orifices 102 includes: a first tube aperture 1022; a second pipe hole 1024 spaced a first distance from the first pipe hole 1022 in the fluid flow direction, the second pipe hole 1024 spaced a second distance from the first pipe hole 1022 in a direction perpendicular to the fluid flow direction; the first distance is non-zero, the number of the pipe hole groups 102 is multiple, and the plurality of pipe hole groups 102 are respectively arrayed along the fluid flow direction and the direction perpendicular to the fluid flow direction.
In this embodiment, the first tube hole 1022 and the second tube hole 1024 in each tube hole group 102 are at a first distance that is nonzero along the fluid flow direction and at a second distance that is perpendicular to the fluid flow direction, and the fluid flowing through the tube hole groups 102 can be disturbed by setting the first distance and the second distance, so that fluid destruction is promoted, a new boundary layer is developed, and a heat exchange effect between the fluid and the fin group 10 is improved.
Example 5:
in another embodiment of the present invention, based on embodiment 4, the number of the pipe hole groups 102 is plural, and the plural pipe hole groups 102 are respectively arrayed along the fluid flow direction and the direction perpendicular to the fluid flow direction. At this time, the array pitch, the first distance, and the second distance of the tube hole group 102 determine the arrangement of the tube holes in the fin group 10, and by setting the numerical values of the array pitch, the first distance, and the second distance, on one hand, the heat exchange area can be increased through the side surface of the tube hole group 102, on the other hand, the positional relationship of the tube holes in the tube hole group 102 and the array distance between the tube hole groups 102 are reasonably set, so that the fluid between the fins 104 can be disturbed by each tube hole, and the fluid is continuously destroyed and develops a new boundary layer by matching with the second concave-convex corrugation 1056, thereby improving the heat exchange performance of the fin group 10. Meanwhile, the number of the pipe holes determines the volume of the heat carrier passing through the fin group 10 in unit time, so that the number of the pipe holes in the embodiment is as large as possible on the premise of ensuring the heat exchange efficiency, so that more heat carriers in the fin group 10 in unit time exchange heat, and the heat exchange efficiency of the fin group 10 is improved.
Example 6:
according to another embodiment of the present invention, on the basis of embodiment 5, the two ends of the fin 104 in the fluid flow direction are respectively defined as a first end 106 and a second end 108, if the fluid flows from the first end 106 to the second end 108, the first concavo-convex corrugation 1042 at both sides of the first tube hole 1022 is bent and forms a first bent side and a second bent side, and the first bent side and the second bent side intersect at a first termination point; wherein the distance between the first curved side and the second curved side gradually decreases from the first end 106 to the second end 108. At this time, the first curved side and the second curved side form a flow guiding structure, when the fluid flows from the first end 106 to the second end 108, a part of the fluid on both sides of the first tube hole 1022 is guided to a side of the first tube hole 1022 close to the second end 108, so that the heat transfer on the weak side of the first tube hole 1022, that is, the side which cannot be directly contacted with the fluid in the flow direction during the fluid flow is enhanced, and the heat exchange performance of the fin group 10 is increased.
Example 7:
in this embodiment, on the basis of embodiment 6, when a fluid flows from the first end 106 to the second end 108, when a portion of the fluid near the second curved side behind the first tube hole 1022 in the flow direction flows slowly, the heat exchange performance of the portion is low at this time, the first termination point is set on the side near the first curved side during design, the drainage effect of the second curved side is stronger than that of the first curved side at this time, and when the heat exchange enhancement is performed on the side near the second end 108 of the first tube hole 1022, the flow of the portion of the fluid near the second curved side behind the first tube hole 1022 in the flow direction is accelerated, so that the overall heat exchange performance of the fin group 10 is greatly improved.
The drainage effect of the first curved side and the second curved side is different with respect to different positions of the first termination point. In practical applications, the first termination point is set according to the properties of the fluid between the fins 104 and the positions between the tube holes, so as to better regulate the flow of the fluid between the fins 104 and improve the heat exchange performance of the fin group 10. This embodiment is but one of several implementations.
Example 8:
in this embodiment, based on embodiment 6, the first termination point is collinear with the center of the first pipe hole 1022 in the fluid flow direction.
At this time, the first curved side and the second curved side are located on two sides of the center of the circle of the first pipe hole 1022 in the fluid flowing direction, the drainage of the first curved side and the second curved side is more even at this time, the fluid on the heat exchange weak side of the first pipe hole 1022 flows more uniformly, and the heat exchange effect of the heat exchange weak side of the first pipe hole 1022 is improved.
Example 9:
in the present embodiment, on the basis of embodiment 8, the first curved side and the second curved side are symmetrical with respect to the second cross section at the center of the first tube hole 1022.
At this time, the first curved side and the second curved side have the same flow guiding effect, so that the fluid flow around the first pipe hole 1022 is more uniform, and the heat exchange around the first pipe hole 1022 is uniform.
Example 10:
according to another embodiment of the present invention, in addition to embodiment 1, if the fluid flows from the second end 108 to the first end 106, the first corrugation 1042 at both sides of the second tube hole 1024 bends and forms a third bending side and a fourth bending side, and the third bending side and the fourth bending side intersect at a second termination point; wherein the distance between the third curved side and the fourth curved side gradually decreases from the second end 108 to the first end 106.
In this embodiment, the third curved side and the fourth curved side form a flow-directing structure that directs portions of the fluid on both sides of the second tube hole 1024 to a side of the second tube hole 1024 near the first end 106 when the fluid flows from the second end 108 to the first end 106, thereby enhancing heat transfer on the weak heat exchange side of the tube hole and increasing the heat exchange performance of the fin assembly 10. Meanwhile, the first bent side and the second bent side are matched, so that the flow direction of fluid among the fins 104 is better controlled, and the heat exchange of the weak heat exchange side of the fin group 10 is increased.
Example 11:
in this embodiment, on the basis of embodiment 10, when the fluid flows from the second end 108 to the first end 106, and a part of the fluid near the third curved side behind the second tube hole 1024 in the flow direction flows slowly, the heat exchange performance of the part is lower at this time, the second termination point is disposed at a side near the fourth curved side, the drainage effect of the third curved side is stronger than that of the fourth curved side, and when the heat exchange enhancement is performed on the side of the second tube hole 1024 near the first end 106, the part of the fluid near the third curved side behind the second tube hole 1024 in the flow direction is accelerated, so that the overall heat exchange performance of the fin group 10 is greatly improved.
The drainage effect of the third curved side and the fourth curved side is different with respect to the different position of the second termination point. In practical applications, the first termination point is set according to the properties of the fluid between the fins 104 and the positions between the tube holes, so as to better regulate the flow of the fluid between the fins 104 and improve the heat exchange performance of the fin group 10. This embodiment is but one of several implementations.
Example 12:
in this embodiment, on the basis of embodiment 10, the second termination point and the center of the second tube hole 1024 are collinear in the fluid flow direction.
In this embodiment, the second termination point and the center of the second tube hole 1024 are collinear in the fluid flowing direction, that is, the third curved side and the fourth curved side are located on two sides of the center of the second tube hole 1024 in the fluid flowing direction, at this time, the drainage of the third curved side and the fourth curved side is more average, and the fluid flowing on the tube hole heat exchange weak side is more uniform, so that the heat exchange on the tube hole heat exchange weak side is more uniform.
Example 13:
in this embodiment, on the basis of embodiment 12, the third curved side and the fourth curved side are symmetrical with respect to the second cross section at the center of the second tube hole 1024.
At this time, the drainage effect of the third curved side and the fourth curved side is the same, so that the fluid around the second pipe hole 1024 flows more uniformly, and the heat exchange around the second pipe hole 1024 is uniform.
In the above embodiment, it is preferable that the flow structure (i.e., the first corrugation 1042, the first curved side and the second curved side, and the tube hole group 102) through which the fluid passes from the first end 106 to the second end 108 is identical in sequence and characteristics to the flow structure (i.e., the first corrugation 1042, the third curved side and the fourth curved side, and the tube hole group 102) through which the fluid passes from the second end 108 to the first end 106, and has a symmetrical structure, so as to facilitate the overall processing and installation of the heat exchanger.
Example 14:
according to another embodiment of the present invention, the first and second tube apertures 1022, 1024 each have a fifth curved side 1044 and a sixth curved side 1046 on a side thereof adjacent the first end 106 and a seventh curved side 1050 and an eighth curved side 1052 on a side thereof adjacent the second end 108. Wherein, in the direction of fluid flow, the distance between the fifth curved side 1044 and the sixth curved side 1046 gradually increases from the first end 106 to the second end 108, and the distance between the seventh curved side 1050 and the eighth curved side 1052 gradually decreases from the first end 106 to the second end 108. When fluid flows from the first end 106 to the second end 108, the fifth curved side 1044 and the sixth curved side 1046 guide part of the fluid flowing to the side of the tube hole close to the first end 106 to both sides of the tube hole, and the seventh curved side 1050 and the eighth curved side 1052 guide part of the fluid on both sides of the tube hole to the side of the tube hole close to the second end 108, so as to enhance heat exchange of the side of the tube hole close to the second end 108, and simultaneously, in cooperation with the first distance and the second distance between the tube holes and the array pitch of the tube holes, the fifth curved side 1044 and the sixth curved side 1046 of the tube hole close to the first end 106 and the seventh curved side 1050 and the eighth curved side 1052 of the tube hole close to the second end 108 can cooperate with each other, so that the flow direction of the fluid among the fins 104 is more reasonable, and the heat exchange enhancement.
When fluid flows from the second end 108 to the first end 106, the seventh curved side 1050 and the eighth curved side 1052 direct a portion of the fluid flowing to a side of the tube bore near the second end 108 to both sides of the tube bore, and the fifth curved side 1044 and the sixth curved side 1046 direct a portion of the fluid on both sides of the tube bore to a side of the tube bore near the first end 106, thereby enhancing heat exchange of the side of the tube bore near the first end 106, and simultaneously, in cooperation with the first distance and the second distance between the tube bores and the array pitch of the tube bores, the fifth curved side 1044 and the sixth curved side 1046 of the tube bore near the first end 106 and the seventh curved side 1050 and the eighth curved side 1052 of the tube bore near the second end 108 may cooperate with each other, so that the direction of fluid flow between the fins 104 is more reasonable, and heat exchange enhancement of the weak sides of the.
Example 15:
according to another embodiment of the present invention, the first and second tube apertures 1022, 1024 each have a fifth curved side 1044 and a sixth curved side 1046 on a side thereof adjacent the first section, and the seventh curved side 1050 and the eighth curved side 1052 are on only a side of the first tube aperture 1022 adjacent the second end 108. When fluid flows from the first end 106 to the second end 108, the portions of the fluid flowing to the first tube hole 1022 and the second tube hole 1024 near the first end 106 are guided to the two sides of the tube hole by the fifth curved side 1044 and the sixth curved side 1046, and the seventh curved side 1050 and the eighth curved side 1052 guide the portions of the fluid at the two sides of the first tube hole 1022 to the side of the tube hole near the second end 108, so that the heat transfer of the heat exchange weak side of the first tube hole 1022, i.e., the side which cannot be directly contacted by the fluid flowing from the first end 106 to the second end 108, is enhanced. As fluid flows from the second end 108 to the first end 106, the fifth curved side 1044 and the sixth curved side 1046 direct fluid on both sides of the first tubing bore 1022 and the second tubing bore 1024 to a side of the first tubing bore 1022 and the second tubing bore 1024 proximate the first end 106, respectively, enhancing heat exchange of the first tubing bore 1022 and the second tubing bore 1024 proximate the first end 106.
Example 16:
according to another embodiment of the present invention, the first and second tube apertures 1022, 1024 each have a fifth curved side 1044 and a sixth curved side 1046 on a side proximate the first end 106, and the second tube aperture 1024 has a seventh curved side 1050 and an eighth curved side 1052 on a side proximate the second end 108. At this point, when fluid flows from the first end 106 to the second end 108, a portion of the fluid on both sides of the second tube aperture 1024 is directed by the seventh curved side 1050 and the eighth curved side 1052 to a side of the second tube aperture 1024 near the second end 108; when fluid flows from the second end 108 to the first end 106, part of the fluid on both sides of the first tube hole 1022 is guided to the side of the first tube hole 1022 close to the first end 106 by the fifth curved side 1044 and the sixth curved side 1046, and part of the fluid on both sides of the second tube hole 1024 is guided to the side of the second tube hole 1024 close to the first end 106 by the fifth curved side 1044 and the sixth curved side 1046, so that heat exchange on the heat exchange weak sides of the first tube hole 1022 and the second tube hole 1024 in flow heat exchange is enhanced, and the heat exchange performance of the fin 104 is increased.
Example 17:
according to another embodiment of the present invention, the first tube bore 1022 has a fifth curved side 1044 and a sixth curved side 1046 on a side proximate the first end 106, and the first tube bore 1022 and the second tube bore 1024 each have a seventh curved side 1050 and an eighth curved side 1052 on a side proximate the second end 108. When fluid flows from the first end 106 to the second end 108, portions of the fluid on both sides of the first tube aperture 1022 are directed to a side of the first tube aperture 1022 near the second end 108 by the seventh curved side 1050 and the eighth curved side 1052, and portions of the fluid on both sides of the second tube aperture 1024 are directed to a side of the second tube aperture 1024 near the second end 108 by the seventh curved side 1050 and the eighth curved side 1052; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the first conduit aperture 1022 are directed toward the side of the first conduit aperture 1022 near the first end 106 by the fifth curved side 1044 and the sixth curved side 1046. Through the fifth curved side 1044, the sixth curved side 1046, the seventh curved side 1050 and the eighth curved side 1052, the heat exchange of the weak heat exchange side in the flow heat exchange is enhanced, and the heat exchange performance of the fin 104 is increased.
Example 18:
according to another embodiment of the present invention, there is a fifth curved side 1044 and a sixth curved side 1046 at a side of the first conduit aperture 1022 adjacent the first end 106 and a seventh curved side 1050 and an eighth curved side 1052 at a side of the first conduit aperture 1022 adjacent the second section. When fluid flows from the first end 106 to the second end 108, portions of the fluid on either side of the first aperture 1022 are directed toward the side of the first aperture 1022 near the second end 108 by the seventh curved side 1050 and the eighth curved side 1052; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the first conduit aperture 1022 are directed toward the side of the first conduit aperture 1022 near the first end 106 by the fifth curved side 1044 and the sixth curved side 1046. The fifth bent side 1044, the sixth bent side 1046, the seventh bent side 1050 and the eighth bent side 1052 enhance the heat exchange of the heat exchange weak side of the first tube hole 1022 in the flow heat exchange, and increase the heat exchange performance of the fin 104.
Example 19:
according to another embodiment of the present invention, the first tube bore 1022 has a fifth curved side 1044 and a sixth curved side 1046 on a side adjacent the first end 106 and the second tube bore 1024 has a seventh curved side 1050 and an eighth curved side 1052 on a side adjacent the second section. When fluid flows from the first end 106 to the second end 108, portions of the fluid on either side of the second tube aperture 1024 are directed toward the side of the second tube aperture 1024 proximate the second end 108 by the seventh curved side 1050 and the eighth curved side 1052; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the first conduit aperture 1022 are directed toward the side of the first conduit aperture 1022 near the first end 106 by the fifth curved side 1044 and the sixth curved side 1046. The fifth bent side 1044, the sixth bent side 1046, the seventh bent side 1050 and the eighth bent side 1052 enhance the heat exchange of the heat exchange weak sides of the first tube hole 1022 and the second tube hole 1024 in the flow heat exchange, and increase the heat exchange performance of the fin 104.
Example 20:
according to another embodiment of the present invention, there are fifth 1044 and sixth 1046 curved sides on the side of the second tube bore 1024 adjacent the first end 106 and seventh 1050 and eighth 1052 curved sides on the side of the first 1022 and second 1024 tube bores adjacent the second section. When fluid flows from the first end 106 to the second end 108, portions of the fluid on both sides of the first tube aperture 1022 are directed to a side of the first tube aperture 1022 near the second end 108 by the seventh curved side 1050 and the eighth curved side 1052, and portions of the fluid on both sides of the second tube aperture 1024 are directed to a side of the second tube aperture 1024 near the second end 108 by the seventh curved side 1050 and the eighth curved side 1052; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the second tube aperture 1024 are directed toward the side of the second tube aperture 1024 proximate the first end 106 by the fifth curved side 1044 and the sixth curved side 1046. Through the fifth curved side 1044, the sixth curved side 1046, the seventh curved side 1050 and the eighth curved side 1052, the weak heat exchange side of the first pipe hole 1022 and the second pipe hole 1024 in flow heat exchange, that is, the heat exchange of the area of one side which cannot be directly contacted with the fluid in the flow direction during the fluid flow is enhanced, and the heat exchange performance of the fin 104 is increased.
Example 21:
according to another embodiment of the present invention, the second tube bore 1024 has a fifth curved side 1044 and a sixth curved side 1046 on a side thereof adjacent the first end 106 and the first tube bore 1022 has a seventh curved side 1050 and an eighth curved side 1052 on a side thereof adjacent the second end 108. When fluid flows from the first end 106 to the second end 108, portions of the fluid on either side of the first aperture 1022 are directed toward the side of the first aperture 1022 near the second end 108 by the seventh curved side 1050 and the eighth curved side 1052; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the second tube aperture 1024 are directed toward the side of the second tube aperture 1024 proximate the first end 106 by the fifth curved side 1044 and the sixth curved side 1046. The fifth bent side 1044, the sixth bent side 1046, the seventh bent side 1050 and the eighth bent side 1052 enhance the heat exchange of the heat exchange weak sides of the first tube hole 1022 and the second tube hole 1024 in the flow heat exchange, and increase the heat exchange performance of the fin 104.
Example 22:
according to another embodiment of the present invention, there is a fifth curved side 1044 and a sixth curved side 1046 on a side of the second tube bore 1024 adjacent the first end 106 and a seventh curved side 1050 and an eighth curved side 1052 on a side of the second tube bore 1024 adjacent the second section. When fluid flows from the first end 106 to the second end 108, portions of the fluid on either side of the second tube aperture 1024 are directed toward the side of the second tube aperture 1024 proximate the second end 108 by the seventh curved side 1050 and the eighth curved side 1052; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the second tube aperture 1024 are directed toward the side of the second tube aperture 1024 proximate the first end 106 by the fifth curved side 1044 and the sixth curved side 1046. The fifth bent side 1044, the sixth bent side 1046, the seventh bent side 1050 and the eighth bent side 1052 enhance the heat exchange of the heat exchange weak sides of the first tube hole 1022 and the second tube hole 1024 in the flow heat exchange, and increase the heat exchange performance of the fin 104.
Example 23:
as shown in fig. 5, when the second distance is equal to half of the array distance of the group of apertures 102 in the direction perpendicular to the flow direction, a seventh curved side 1050 and an eighth curved side 1052 are provided on a side of the first aperture 1022 close to the second end 108, and a fifth curved side 1044 and a sixth curved side 1046 are provided on a side of the second aperture 1024 close to the first end 106, wherein a distance between the fifth curved side 1044 and the sixth curved side 1046 gradually increases from the first end 106 to the second end 108, a distance between the seventh curved side 1050 and the eighth curved side 1052 gradually decreases from the first end 106 to the second end 108, the fifth curved side 1044 and the sixth curved side 1046 are symmetrical with respect to a longitudinal section of the first aperture 1022, and the seventh curved side 1050 and the eighth curved side 1046 are symmetrical with respect to a longitudinal section of the second aperture 1024. When fluid flows from the first end 106 to the second end 108, part of the fluid on both sides of the first pipe hole 1022 is guided to the side of the first pipe hole 1022 close to the second end 108 by the seventh curved side 1050 and the eighth curved side 1052, meanwhile, the fifth curved side 1044 on the second pipe hole 1024 can guide part of the fluid flowing to the side of the second pipe hole 1024 close to the first end 106 to the side of the first pipe hole 1022 close to the second end 108 in the same pipe hole group 102, and the sixth curved side 1046 on the second pipe hole 1024 can guide part of the fluid flowing to the side of the second pipe hole 1024 close to the first end 106 to the side of the first pipe hole 1022 close to the second end 108 in the adjacent pipe hole group 102 in the direction perpendicular to the fluid flowing direction; as fluid flows from the second end 108 to the first end 106, portions of the fluid on either side of the first conduit aperture 1022 are directed toward the side of the first conduit aperture 1022 near the first end 106 by the fifth curved side 1044 and the sixth curved side 1046.
In this embodiment, the bent sides of the tube holes are matched, and the bent sides of the tube holes also have heat exchange strengthening effect on the heat exchange weak sides of the adjacent tube holes, so that the heat exchange performance of the heat exchange weak sides of the tube holes is further strengthened, and the overall heat exchange performance of the fin group 10 is improved.
Corresponding to different embodiments and different tube hole arrangements, the fifth bending side 1044, the sixth bending side 1046, the seventh bending side 1050 and the eighth bending side 1052 can not only strengthen the weak heat exchange side of the heat exchange tube, but also adjust the overall flow direction of the fluid between the fins 104, strengthen the heat exchange between the fluid and the fins 104, and improve the heat exchange performance of the fin group 10. This embodiment is but one of several implementations.
Example 24:
in another embodiment of the present invention, the third termination point 1048 and the center of the tube hole are collinear in the fluid flowing direction, that is, the fifth curved side 1044 and the sixth curved side 1046 are located at two sides of the center of the tube hole in the fluid flowing direction, at this time, the drainage of the fifth curved side 1044 and the sixth curved side 1046 is more even, the fluid flowing at the heat exchanging weak side of the tube hole is more uniform, so that the heat exchanging at the heat exchanging weak side of the tube hole is more uniform.
Example 25:
in another embodiment of the present invention, based on embodiment 24, the fifth curved side 1044 and the sixth curved side 1046 are symmetrical about the second cross section passing through the center of the pipe hole. At this time, the drainage effect of the fifth curved side 1044 is the same as that of the sixth curved side 1046, so that the fluid flow around the tube holes is uniform, and the possibility of occurrence of conditions such as fluctuation of the fluid around the tube holes is reduced, so that the overall flow of the fluid among the fins 104 is more stable, and the heat exchange performance of the fin group 10 is more stable.
Example 26:
in another embodiment of the present invention, the fourth termination point 1054 and the center of the tube hole are collinear in the fluid flowing direction, that is, the seventh curved side 1050 and the eighth curved side 1052 are located at two sides of the center of the tube hole in the fluid flowing direction, and at this time, the drainage of the seventh curved side 1050 and the eighth curved side 1052 is more even, the fluid flowing in the heat exchanging weak side of the tube hole is more uniform, so that the heat exchanging in the heat exchanging weak side of the tube hole is more uniform.
Example 27:
in another embodiment of the present invention, in addition to embodiment 26, the seventh curved side 1050 and the eighth curved side 1052 are symmetrical about a second cross section through the center of the tube hole. At this time, the drainage effect of the seventh bending side 1050 is the same as that of the eighth bending side 1052, so that the fluid flow around the tube hole is uniform, the possibility of occurrence of conditions such as fluctuation of the fluid around the tube hole is reduced, the overall fluid flow among the fins 104 is more stable, and the heat exchange performance of the fin group 10 is more stable.
Example 28:
in another embodiment of the present invention, when the third termination point 1048 and the center of the tube hole are collinear in the fluid flow direction, and at the same time, the fourth termination point 1054 and the center of the tube hole are collinear in the fluid flow direction, the fifth bending side 1044, the sixth bending side 1046, the seventh bending side 1050 and the eighth bending side 1052 are located at two sides of the center of the tube hole in the fluid flow direction, so that the fluid flow of the tube hole heat exchange weak side is more uniform, and the heat exchange of the tube hole heat exchange weak side is more uniform.
Example 29:
in another embodiment of the present invention, in the base of embodiment 28, fifth curved side 1044 and sixth curved side 1046 are symmetrical about the second cross-section through the center of the aperture, while seventh curved side 1050 and eighth curved side 1052 are symmetrical about the second cross-section through the center of the aperture. At this time, the drainage effect of the fifth bending side 1044, the sixth bending side 1046, the seventh bending side 1050 and the eighth bending side 1052 is the same, and the fluid flows uniformly when flowing through the tube hole group 102, so that the possibility of occurrence of conditions such as fluctuation of the fluid around the tube hole group 102 is reduced, the overall flow of the fluid among the fins 104 is more stable, and the heat exchange performance of the fin group 10 is more stable.
In the above embodiment, preferably, the second concavo-convex corrugation 1056 has the second pitch P between two adjacent wave troughs in the second cross sectionwA first pitch P between two adjacent valleys of the first concavo-convex corrugation 1042 in the first cross sectionlThe ratio of the first concave-convex corrugation 1042 is in a range of 4-12, and a first pitch P between two adjacent wave troughs on the first sectionlThe numerical range of (A) is 1-5 mm.
Second pitch P between two adjacent troughs of the second corrugation 1056 in the second cross sectionwA first pitch P between two adjacent valleys of the first concavo-convex corrugation 1042 in the first cross sectionlThe ratio of the first concave-convex corrugation 1042 to the second concave-convex corrugation 1056 is in a range of 4-12, and the heat exchange performance of the fin 104 is greatly improved in the numerical range; first concave-convex corrugation1042 first pitch P between two adjacent troughs in the first cross-sectionlThe range of the first uneven corrugation 1042 is 1-5 mm, when the first uneven corrugation 1042 is at a first pitch P between two adjacent wave troughs on a first sectionlWhen the diameter is 1mm, the characteristic dimension of heat exchange is minimum, the thermal resistance of the fins 104 is minimum, the heat exchange performance of the fins 104 is high, and the heat exchanger is suitable for the working condition with high requirement on the heat exchange performance; when the first uneven corrugation 1042 has a first pitch P between two adjacent valleys in the first cross sectionlWhen the diameter is 5mm, the characteristic dimension of heat exchange is small, the thermal resistance of the fins 104 is small, the heat exchange performance of the fins 104 is high, the heat exchange requirement is met, the processing cost of the fin group 10 can be saved, and in practical application, the first pitch P between two adjacent wave troughs on the first section of the first concave-convex corrugation 1042 islAnd selecting any value between 1mm and 5mm according to the actual working condition.
In the above embodiment, preferably, a tangent line of any point of the first concave-convex corrugation 1042 on the first cross section and a tangent line of any trough on the first cross section form a first acute angle αlNot more than 75 degrees, and a second acute angle α is formed by the tangent of the second concavo-convex corrugation 1056 at any point on the second cross section and the tangent of the lowest point of any wave trough on the second cross sectionwNot greater than 30.
At this time, a tangent line of any point of the first concave-convex corrugation 1042 on the first cross section and a tangent line of any trough of the first cross section form a first acute angle αlNo greater than 75 deg. to reduce the extent of heat transfer from the fluid flowing through the fins 104, thereby enhancing heat transfer, the second corrugation 1056 has a second acute angle α between a tangent to any point on the second cross-section and a tangent to the lowest point of any trough on the second cross-sectionwWithin the angle range of not more than 30 degrees, the second concave-convex corrugation 1056 can break the boundary layer of the airflow, increase the heat exchange effect between the fluid and the fins 104, reduce the flow pressure loss of the fluid among the fins 104, and reduce the energy consumption of the fluid among the fins 104 during the heat exchange.
In the above-described embodiment, it is preferable that the first concavo-convex corrugation 1042 has a first perpendicular distance H from the valley of the first contour line to the adjacent peak in the first cross sectionlAnd a distance FpIn the range of the ratio of0 to 0.3, and a second vertical distance H from the trough of a second contour line of the second concave-convex corrugation 1056 on the second cross section to the adjacent crestwAnd a distance FpThe ratio of (A) to (B) is in the range of 0.4-1.2, and the distance FpThe range is 0.8-2.5 mm.
At this moment, the interval is 0.8 ~ 2.5mm, and in this numerical range, can enough make the fluid between fin 104 and fin 104 can carry out good heat transfer, can make the fluidic flow between fin 104 again in reasonable scope, can satisfy the requirement to heat transfer effect and heat exchange efficiency among the operating condition. Meanwhile, the first concave-convex corrugation 1042 has a first vertical distance H from the trough of the first contour line to the adjacent crest on the first cross sectionlAnd a distance FpThe ratio of the second concave-convex corrugation 1056 on the second section is in the range of 0-0.3, and the second vertical distance H from the wave trough of the second contour line to the adjacent wave crestwAnd a distance FpThe ratio of (3) to (2) is in a range of 0.4-1.2, so that the fluid between the fins 104 can increase the flow heat exchange with the fins 104 under the action of the first concave-convex corrugations 1042 and the second concave-convex corrugations 1056, and the heat exchange performance of the fins 104 is further improved.
In the above embodiment, it is preferable that the hole group pitch W in the fluid flow direction of two adjacent pipe hole groups 102 in the fluid flow direction is in the range of 8 to 22mm, and the second pitch P of the second concavo-convex corrugation 1056wThe ratio of the number of holes to the pitch W of the hole group is in the range of 0.2 to 0.5.
At the moment, the hole group distance W between the two adjacent pipe hole groups 102 in the fluid flowing direction is 8-22 mm, the pipe hole groups 102 are in the distance range, heat carriers in the pipe holes in one side can rapidly transfer heat to the fins 104, and then the fins 104 and the fluid perform flowing heat exchange, so that rapid heat exchange is realized, the heat exchange efficiency is improved, and meanwhile, the second distance P between the second concave-convex corrugations 1056 is larger than the second distance P between the second concave-convex corrugations 1056wThe range of the ratio of the width of the fin group to the hole group distance W is 0.2-0.5, the heat exchange efficiency can be further improved by enhancing the heat exchange effect of the second concave-convex corrugations 1056 in the range of the ratio, so that the heat exchange performance of the fin group 10 can be still kept in a stable range when the hole group distance W is changed, and the fin group 10 can be suitable for more working conditions to meet the requirement of more working conditionsMore heat exchange requirements.
Example 30:
another embodiment of the present invention provides a fin 104 tube heat exchanger, which includes the fin group 10 of any one of the above embodiments, and further includes a heat exchange tube sleeved in the tube hole of the fin group 10. When the number of the orifice groups 102 is plural, the plural orifice groups 102 are arrayed in a direction perpendicular to the fluid flow direction; the distance P between every two adjacent pipe hole groups 102 along the direction perpendicular to the fluid flowt12-25 mm, and the range of the inner diameter D of the heat exchange tube is 5-9 mm.
When the fin 104 tube heat exchanger exchanges heat, a heat carrier flows in the heat exchange tubes, and fluid flows among the fins 104. The heat carrier transfers heat to the heat exchange tubes, the heat exchange tubes transfer heat to the fins 104, and then the fins 104 and fluid between the tube holes and the fins 104 perform flow heat exchange. When fluid flows among the fins 104 for heat exchange, the first concave-convex corrugations 1042 can reduce the characteristic size of the flowing heat exchange between the fluid and the fins 104, so that the heat exchange is strengthened, the second concave-convex corrugations 1056 enable the fluid to continuously change the movement direction under the action of the fins 104 in the movement process, on one hand, the fluid continuously breaks and develops a new boundary layer, so that the heat exchange is strengthened, and the heat exchange coefficient of the surface of the fins 104 is improved; on the other hand, the fluid continuously impacts the surface of the fin 104, so that the possibility of scaling on the surface of the fin 104 can be reduced, and the heat exchange performance of the fin group 10 is more stable. The amplitudes of the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 are set to be optimal values according to the design requirements of the fin set 10, and the amplitudes of the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056 are different, so that the heat exchange can be strengthened to the maximum extent by the first concave-convex corrugation 1042 and the second concave-convex corrugation 1056, and the heat exchange performance of the fin set 10 can be improved to the maximum extent. Meanwhile, the first concave-convex corrugations 1042 and the second concave-convex corrugations 1056 can increase the heat exchange area of the fin 104, so that the heat exchange performance of the fin group 10 is improved. While the spacing F between two adjacent fins 104pThe same, so that the fluid flow between the fins 104 is smooth, and the heat exchange of all parts of the fins 104 is uniform. Meanwhile, a bent side structure is arranged in the tube hole group 102 under actual working conditions, so that heat exchange of the weak side of tube hole heat exchange is enhanced, and tube exchange of the fins 104 is improvedHeat exchange performance of the heater.
When the number of the pipe hole groups 102 is plural, the plural pipe hole groups 102 are arrayed along the direction perpendicular to the fluid flow direction, and the distance P between every two adjacent pipe hole groups 102 along the direction perpendicular to the fluid flow directiont12-25 mm, when the distance P between every two adjacent pipe hole groups 102 along the direction perpendicular to the flowing direction of the fluidtWhen the diameter is 12mm, the distance between the pipe hole groups 102 is smaller, the fluid can be disturbed more sufficiently under the same fluid flow rate, so that the heat exchange of the fluid in the heat exchanger is more sufficient, meanwhile, the distance between the pipe hole groups 102 is smaller, the number of pipe holes in the fins 104 with the same area size is also larger, and in order to enable the heat carrier in the pipe heat pipe to perform sufficient heat exchange, the flow rate of the heat carrier in the pipe heat pipe should be reduced; the distance P between every two adjacent pipe hole groups 102 along the direction perpendicular to the fluid flowtWhen the diameter is 25mm, the distance between the pipe hole groups 102 is larger, so that the heat exchange pipe is suitable for the condition that the flow velocity of heat carriers in the heat exchange pipe is higher, and in practical application, according to the flow velocity of fluid and the distance P between every two adjacent pipe hole groups 102 along the direction vertical to the flow direction of the fluid under practical working conditionstAny value within the range of 12-25 mm is selected.
The range of the inner diameter D of the heat exchange tube is 5-9 mm, when the inner diameter D of the heat exchange tube is 5mm, the inner diameter D of the heat exchange tube is smaller, and the volume of a heat carrier flowing through the heat exchange tube in unit time at the same flow speed is smaller, so that the flow speed of the heat carrier in the heat exchange tube can be increased under the condition of ensuring the heat exchange effect, and the heat exchange tube is suitable for the condition of higher flow speed of the heat carrier; when the internal diameter D of heat exchange tube was 9mm, this moment the pipe heat pipe internal diameter D was great, and the volume of the heat carrier that flows through in the unit interval is more under the same flow rate, consequently for guaranteeing the heat transfer effect, need reduce the velocity of flow of heat carrier in the heat exchange tube, is applicable to the condition that the heat carrier flow is more slow, selects for use the arbitrary numerical value in 5 ~ 9mm according to fluidic velocity of flow and the internal diameter D of actual condition heat exchange tube among the practical application.
The technical scheme of the invention is explained in detail by combining the attached drawings, and the invention provides a fin group and fin tube type heat exchanger.
In the present invention, the terms "first", "second", and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the term "plurality" means two or more unless expressly limited otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "left", "right", "front", "rear", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the referred device or unit must have a specific direction, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.
In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (15)

1. A fin pack, comprising: at least one fin, each said fin comprising:
at least one pipe hole group, wherein each pipe hole group comprises at least one pipe hole, and each pipe hole penetrates through two sides of the fin;
the fin is provided with a first concave-convex corrugation on a first section along the flowing direction of the fluid;
the fin is provided with a second concave-convex corrugation on a second section perpendicular to the fluid flowing direction;
the amplitude of the first concave-convex corrugation is different from that of the second concave-convex corrugation, the pipe holes of two adjacent fins are coaxial, and the distance between two adjacent fins is the same;
the tangent line of any point of the first concave-convex corrugation on the first cross section and the tangent line of any wave trough on the first cross section form a first acute angle not more than 75 degrees, and the tangent line of any point of the second concave-convex corrugation on the second cross section and the tangent line of any wave trough lowest point on the second cross section form a second acute angle not more than 30 degrees.
2. The fin group according to claim 1, wherein the fins have upper and lower edges in any of the first cross-sections that are the same distance in the axial direction of the tube bore.
3. The fin pack according to claim 2, wherein each of the tube hole groups includes:
a first tube hole;
a second pipe aperture at a first distance from the first pipe aperture in the direction of fluid flow, the second pipe aperture at a second distance from the first pipe aperture in the direction perpendicular to the direction of fluid flow;
wherein the first distance is non-zero, the number of the orifice groups is plural, and the plural orifice groups are arrayed along the fluid flow direction and the perpendicular fluid flow direction, respectively.
4. A fin group according to claim 3, wherein the two ends of the fin in the fluid flow direction are a first end and a second end, respectively, and if the fluid flows from the first end to the second end, the first concavo-convex corrugation at both sides of the first tube hole is bent and forms a first bent side and a second bent side, and the first bent side and the second bent side intersect at a first termination point;
wherein a distance between the first curved side and the second curved side gradually decreases from the first end to the second end.
5. A fin set according to claim 4, wherein the first termination point is collinear with a center of the first tube bore in the direction of fluid flow.
6. A fin set according to claim 4, wherein if said fluid flows from said second end to said first end, said first corrugations on either side of said second tube bore are curved and form third and fourth curved sides, said third and fourth curved sides meeting at a second termination point;
wherein a distance between the third curved side and the fourth curved side gradually decreases from the second end to the first end.
7. The fin pack according to claim 6, wherein the second termination point and the center of the second tube bore are collinear in the direction of fluid flow.
8. A fin group according to claim 3, wherein the first corrugations of the first and/or second tube bores near the first end form fifth and sixth curved sides, the first corrugations of the first and/or second tube bores near the second end form seventh and eighth curved sides the fifth and sixth curved sides intersect at a third termination point, the seventh and eighth curved sides intersect at a fourth termination point;
wherein, in the fluid flow direction, a distance between the fifth curved side and the sixth curved side gradually increases from the first end to the second end, and a distance between the seventh curved side and the eighth curved side gradually decreases from the first end to the second end.
9. A fin set according to claim 8, wherein the third termination point and the center of the tube bore are collinear in the direction of fluid flow; and/or the fourth termination point and the centre of the pipe bore are collinear in the direction of fluid flow.
10. The fin group according to claim 1, wherein a ratio of a second pitch between two adjacent wave troughs of the second corrugation in the second cross section to a first pitch between two adjacent wave troughs of the first corrugation in the first cross section is in a range of 4 to 12, and a value of the first pitch between two adjacent wave troughs of the first corrugation in the first cross section is in a range of 1 to 5 mm.
11. The fin group according to claim 1, wherein a ratio of a first perpendicular distance from a valley to an adjacent peak of a first contour line of the first uneven corrugation in the first cross section to the pitch is in a range of 0 to 0.3, a second perpendicular distance from a valley to an adjacent peak of a second contour line of the second uneven corrugation in the second cross section to the pitch is in a range of 0.4 to 1.2, and the fin pitch is in a range of 0.8 to 2.5 mm.
12. The fin group according to claim 1, wherein a hole group pitch in the fluid flow direction of two adjacent tube hole groups in the fluid flow direction is in a range of 8 to 22mm, and a ratio of the second pitch of the second corrugation/relief to the hole group pitch is in a range of 0.2 to 0.5.
13. A finned tube heat exchanger comprising: the fin pack of any one of claims 1 to 12;
and the heat exchange tube is sleeved in the tube hole of the fin group.
14. The finned tube heat exchanger of claim 13 wherein when the number of said groups of tube holes is plural, the plurality of said groups of tube holes are arrayed in a direction perpendicular to the direction of fluid flow;
and the distance between every two adjacent pipe hole groups along the direction perpendicular to the fluid flowing direction is 12-25 mm.
15. The finned tube heat exchanger of claim 13 wherein the inner diameter of the heat exchange tube is in the range of 5 to 9 mm.
CN201710802266.1A 2017-09-07 2017-09-07 Fin group and fin tube type heat exchanger Active CN109470074B (en)

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CN110608630A (en) * 2019-09-30 2019-12-24 广东万和热能科技有限公司 Two-stage crotch type fin and heat exchanger
CN110595249A (en) * 2019-09-30 2019-12-20 广东万和热能科技有限公司 Multi-stage crotch type fin and heat exchanger
CN112066776A (en) * 2020-08-04 2020-12-11 西安交通大学 Bionic slotted corrugated fin for air-conditioning heat exchanger

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