WO2019218429A1 - 换热器及换热设备 - Google Patents

换热器及换热设备 Download PDF

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Publication number
WO2019218429A1
WO2019218429A1 PCT/CN2018/093150 CN2018093150W WO2019218429A1 WO 2019218429 A1 WO2019218429 A1 WO 2019218429A1 CN 2018093150 W CN2018093150 W CN 2018093150W WO 2019218429 A1 WO2019218429 A1 WO 2019218429A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
fin
fins
heat exchanger
heat
Prior art date
Application number
PCT/CN2018/093150
Other languages
English (en)
French (fr)
Inventor
何哲旺
北本学
陈新厂
Original Assignee
广东美的制冷设备有限公司
美的集团股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 广东美的制冷设备有限公司, 美的集团股份有限公司 filed Critical 广东美的制冷设备有限公司
Publication of WO2019218429A1 publication Critical patent/WO2019218429A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28F1/14—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 longitudinally
    • F28F1/22—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 longitudinally 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
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/02—Constructions of heat-exchange apparatus characterised by the selection of particular materials of carbon, e.g. graphite
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • 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
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding

Definitions

  • the present application relates to the field of heat exchangers, and in particular to a heat exchanger and a heat exchange device.
  • the heat exchange tubes of the heat exchanger are generally vertically disposed in the fins, and the fins are generally placed vertically, and the heat exchange tubes are generally horizontally penetrated with the fins, and the heat exchange tubes and fins are
  • the heat exchange area of the sheet is small, and the heat resistance is large, resulting in a decrease in heat exchange efficiency between the heat exchange tube and the fin.
  • the present application provides a heat exchanger, which aims to solve the problem of small heat exchange area and large heat resistance of the heat exchange tube and the fin in the prior art.
  • a heat exchanger comprising: a plurality of fins, the plurality of fins are spaced apart; and a heat exchange tube extending over the fin surface or formed on the fin Inside.
  • the present application further provides a heat exchange device including a heat exchanger, the heat exchanger including: a plurality of fins, the plurality of fins are spaced apart; and a heat exchange tube extending from the The fin surface is either formed within the fin.
  • the technical solution of the present application has at least the following technical effects by forming the heat exchange tube in the fin: (1) making any portion of the heat exchange tube contact with the fin, thereby causing the heat exchange Maximizing the heat exchange area between the tube and the fin, and maximizing the heat exchange amount and heat exchange efficiency of the heat exchange tube and the fin; (2) the heat exchange tube is surrounded by the fin The heat exchange tube is not easy to leak the refrigerant, and the reliability and safety are more secure; (3) the heat exchange tube and the fin are integrally formed, and the manufacturing is simpler;
  • the technical solution of the present application has at least the following technical effect by extending the heat exchange tube to the surface of the fin: a long strip-shaped contact portion is formed between the heat exchange tube and the fin, and the heat exchange The heat exchange between the tube and the fin through the elongated contact portion can increase the heat exchange area between the heat exchange tube and the fin, thereby improving the heat exchange tube and the fin Heat exchange and heat transfer efficiency.
  • FIG. 1 is a schematic perspective view of an embodiment of a heat exchanger of the present application
  • FIG. 2 is a schematic structural view of an embodiment of a fin and a heat exchange tube of the present application
  • FIG. 3 is a schematic structural view of another embodiment of a fin and a heat exchange tube of the present application.
  • FIG. 4 is a schematic structural view of another embodiment of a fin and a heat exchange tube of the present application.
  • Figure 5 is a schematic structural view of another embodiment of the fin and heat exchange tube of the present application.
  • FIG. 6 is a schematic structural view of another embodiment of a fin and a heat exchange tube of the present application.
  • FIG. 7 is a schematic structural view of another embodiment of a fin and a heat exchange tube of the present application.
  • FIG. 8 is a schematic structural view of another embodiment of a fin and a heat exchange tube of the present application.
  • Figure 9 is a diagram showing the relationship between the ratio of the thickness of the heat exchange tube at the position of the heat exchange tube and the thickness of the fin to the pressure loss on the air side;
  • Figure 10 is a diagram showing the relationship between the ratio of the area occupied by the fin portion between the heat exchange tubes and the area occupied by the heat exchange tube and the heat exchange efficiency of the fin;
  • FIG. 11 is a schematic structural view of an embodiment of a header, a fin, and a heat exchange tube according to the present application;
  • FIG. 12 is a schematic structural view of another embodiment of a header, a fin and a heat exchange tube according to the present application;
  • FIG. 13 is a schematic structural view of another embodiment of a header, a fin, and a heat exchange tube according to the present application;
  • Figure 14 is a schematic structural view of another embodiment of the fin and the heat exchange tube of the present application.
  • Figure 15 is a schematic structural view of an embodiment of a fin and a heat exchange tube of the present application.
  • Figure 16 is a diagram showing the relationship between the wind speed and the heat exchange amount of the heat exchanger and the finned tube heat exchanger and the microchannel heat exchanger under the same conditions;
  • Figure 17 is a diagram showing the relationship between the wind speed and the air side heat transfer coefficient of the heat exchanger and the finned tube heat exchanger and the microchannel heat exchanger under the same conditions;
  • Figure 18 is a graph showing the relationship between the wind speed and the air pressure drop under the same conditions of the heat exchanger and the finned tube heat exchanger and the microchannel heat exchanger of the present application.
  • first”, “second”, and the like in this application are used for the purpose of description only, and are not to be construed as indicating or implying their relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the technical solutions between the various embodiments may be combined with each other, but must be based on the realization of those skilled in the art, and when the combination of the technical solutions is contradictory or impossible to implement, it should be considered that the combination of the technical solutions does not exist. Nor is it within the scope of protection required by this application.
  • the present application provides a heat exchanger 100 including a plurality of fins 10 , a heat exchange tube 20 , and at least one header 30 .
  • the plurality of fins 10 are spaced apart; at least one heat exchange tube 20 is disposed on each of the fins 10, and the heat exchange tube 20 is formed in the fin 10 or extends to the fin 10
  • the fins 10 are disposed on the header 30, and the heat exchange tubes 20 and the headers 30 communicate with each other.
  • the collecting pipe 30 is used for conveying a refrigerant, and the refrigerant is transferred into the heat exchange pipe 20 through the collecting pipe 30; the heat exchange pipe 20 is used for heat exchange with the fins 10, Thereby, the temperature of the fins 10 is raised or lowered; the fins 10 are used for heat exchange with the gas around the fins 10, thereby raising or lowering the temperature of the gas around the fins 10.
  • the heat exchange tube 20 is formed in the fin 10, and the heat exchange tube 20 and the fin 10 are integrally formed by a casting process.
  • the heat exchange tube 20 is generally vertically disposed in the fin 10, and the heat exchange tube 20 is fixedly connected to the fin 10 by a tube expanding technique, and the heat exchange tube 20 is
  • the fins 10 can only exchange heat between the heat exchange tubes 20 and the fins 10, and the contact heat resistance between the heat exchange tubes 20 and the fins 10 is large.
  • the heat exchange amount and heat exchange efficiency between the heat exchange tube 20 and the fin 10 are low.
  • the heat exchange tube 20 and the fin 10 are integrally formed by a casting process, and the heat exchange tube 20 is formed in the fin 10, and has at least the following technical effects: (1) The heat exchange tube 20 is formed in the fin 10 such that any portion of the heat exchange tube 20 is in contact with the fin 10, so that the heat exchange area of the heat exchange tube 20 and the fin 10 is Maximizing also maximizes heat exchange capacity and heat exchange efficiency of the heat exchange tubes 20 and the fins 10; (2) the heat exchange tubes 20 are surrounded by the fins 10, the heat exchange tubes 20 It is not easy to leak the refrigerant, and the reliability and safety are more secure; (3) The heat exchange tube 20 and the fin 10 are integrally formed by a casting process, and the manufacturing is simpler.
  • the heat exchange tube 20 may be formed in addition to the heat exchange tube 20 formed in the fin 10 .
  • the surface of the fin 10 extends along the surface of the fin 10, and the heat exchange tube 20 is protruded from the surface of the fin 10, and a heat exchange tube 20 and the fin 10 form a surface.
  • the heat exchange tube 20 and the fins 10 exchange heat through the elongated contact portions, and the heat exchange tubes 20 can be enlarged as compared with the prior art.
  • the heat exchange area of the fins 10 increases the heat exchange amount and heat exchange efficiency of the heat exchange tubes 20 and the fins 10.
  • the heat exchange tubes 20 are alternately protruded on opposite sides of the fins 10.
  • the fins 10 are preferably in the form of a sheet, including two surfaces opposite to each other; the dimension of the heat exchange tube 20 in any direction, for example, the diameter of the tube, is greater than the thickness of the fin 10, Therefore, when the heat exchange tube 20 and the fin 10 are integrally formed by a casting process, whether the heat exchange tube 20 is formed in the fin 10 or the heat exchange tube 20 is formed on the fin 10 surface; the heat exchange tube 20 necessarily protrudes from at least one surface of the fin 10.
  • the heat exchange tubes 20 are alternately protruded on opposite sides of the fins 10, and are defined as: the heat exchange tubes 20 are alternately convexly disposed on the fins 10 Two surfaces opposite each other.
  • the heat exchanger 100 is composed of a plurality of the fins 10 stacked, the fins 10 are spaced apart from each other, and a gap between the fins 10 is used to flow a heat exchange airflow (arrows in FIG. 2) In the direction of the finger, that is, both surfaces of the fins 10 opposite each other pass through the heat exchange gas stream.
  • the two surfaces of the fins 10 form a concave-convex structure, and the heat exchange gas flows through the fins.
  • the concave-convex structure can disturb the heat exchange gas flow, thereby improving the heat exchange amount and heat exchange efficiency of the fin 10 and the heat exchange gas stream.
  • the heat exchange tube 20 is protruded from the surface of the fin 10, and the heat exchange area can also be increased.
  • the heat exchange tubes 20 can be arranged on the fins 10 in various manners, and it is only necessary to ensure that the heat exchange tubes 20 are formed in the fins 10 or the heat exchange tubes 20 are formed on the heat exchange tubes 20
  • the surface of the fin 10 may extend over the surface of the fin 10.
  • the heat exchange tube 20 may also be disposed on a single surface of the fin 10; or the fin 10 may be divided into at least a first area and a second area, in the first area, The heat exchange tube 20 is protruded from the upper surface of the fin 10, and in the second region, the heat exchange tube 20 is protruded from the lower surface of the fin 10; of course, the fin 10 may also be The multi-zone division is performed, and the heat exchange tubes 20 may protrude from the upper surface or the lower surface of the fins 10 in different regions.
  • the fins 10 are not limited to a sheet shape, and the fins 10 may also be in a block shape.
  • the fins 10 are spherical, and a part of the heat exchange tubes 20 are formed in the fins 10 .
  • the heat exchange tube 20 is protruded from the spherical surface.
  • the heat exchange tube 20 when the heat exchange tube 20 penetrates the sphere, or when the thickness of the fin 10 is sufficiently thick, the heat exchange tube 20 does not at least partially protrude from the surface of the fin 10, that is, In this embodiment, the heat exchange tube 20 may be convexly disposed on the surface of the fin 10, or may be formed inside the fin 10 without protruding the surface of the fin 10.
  • the plurality of fins 10 are spaced apart from each other, and the gap between the fins 10 is used to flow a heat exchange airflow.
  • a plurality of the fins 10 are preferably equal to each other. The spacings are arranged in parallel such that the heat exchange gas stream passes uniformly through the plurality of fins 10 while reducing the wind resistance of the heat exchange gas stream as it passes through the plurality of fins 10.
  • adjacent fins 10 may also be disposed at an angle, or adjacent fins 10 may be disposed at unequal intervals, and it is only necessary to ensure that there is a gap between the two fins 10 . It can be used for the heat exchange airflow.
  • the fins 10 are integrally arranged in an arc shape, and the cross section of the fins 10 in the width direction is an arc surface, thereby increasing the heat exchange area of the fins 10 and the heat exchange gas flow.
  • the bending directions of the two adjacent fins 10 are opposite, and a swirling airflow may be formed between the concave surfaces of the oppositely disposed fins 10, so that a heat exchange airflow is between the fins. The residence time is longer, which improves the heat exchange efficiency.
  • adjacent heat exchange tubes 20 on the same fin 10 are disposed at equal intervals in parallel.
  • the heat exchange tubes are linear tubes, and the adjacent heat exchange tubes 20 on the same fin 10 are arranged in parallel at equal intervals, and at least include the following cases:
  • the fins 10 are disposed in parallel with a plurality of adjacent fins 10 at equal intervals.
  • the adjacent heat exchange tubes 20 are arranged in parallel at equal intervals, and the refrigerant in the heat exchange tubes 20 is uniformly transferred to the respective portions of the fins 10, thereby improving the heat exchange tubes 20 and The amount of heat exchange between the fins 10 and the heat exchange efficiency.
  • the heat exchange tubes 20 are wavy or polygonal or non-linear tubes such as U-shaped, V-shaped, W-shaped, S-shaped or M-shaped.
  • the heat exchange tubes 20 a plurality of straight segments extending along the length direction of the fins 10 are included, and the distance between the plurality of straight segments is the same, so that the refrigerant in the heat exchange tubes 20 is uniformly transferred to the respective portions of the fins 10, The amount of heat exchange and the heat exchange efficiency between the heat exchange tubes 20 and the fins 10 are increased.
  • the inner diameter or the equivalent inner diameter of the heat exchange tube 20 is greater than or equal to 0.2 mm and less than or equal to 3 mm.
  • the inner diameter of the heat exchange tube 20 is greater than or equal to 0.2 mm and less than or equal to 3 mm; when the flow cross section in the heat exchange tube 20 is not In the case of a circle, if the flow cross section in the heat exchange tube 20 is a square, rectangular, polygonal or the like, or a trapezoidal shape, the equivalent diameter is a circular flow that converts the non-circular flow cross section into an equivalent area.
  • the inner diameter corresponding to the cross section, the equivalent inner diameter is greater than or equal to 0.2 mm and less than or equal to 3 mm.
  • the smaller the inner diameter or the equivalent inner diameter of the heat exchange tube 20, the greater the velocity of the same volume of refrigerant flowing through the heat exchange tube 20, and the heat exchange of the same volume of refrigerant can be performed.
  • the larger inner diameter of the heat exchange tube 20, due to the larger flow cross section the refrigerant at the center of the flow cross section is farther from the tube wall of the heat exchange tube 20, and cannot be sufficiently filled with the tube wall of the heat exchange tube 20.
  • the heat exchange is performed; and the inner diameter or the equivalent inner diameter of the heat exchange tube 20 is smaller, the refrigerant in the heat exchange tube 20 is closer to the tube wall of the heat exchange tube 20, and the heat exchange can be improved to a greater extent. Heat exchange between the tube 20 and the refrigerant.
  • the heat exchange tube 20 having a larger inner diameter forms a large wind resistance on the surface of the fin 10. Therefore, in the present embodiment, the inner diameter or the equivalent inner diameter of the heat exchange tube 20 is 0.2 mm or more and 3 mm or less.
  • the inner diameter or the equivalent inner diameter of the heat exchange tube 20 is made as small as possible, and the flow rate of the refrigerant in the heat exchange tube 20 can be increased, so that the refrigerant in the heat exchange tube 20 is closer to the heat exchange tube 20, thereby improving the heat exchange tube.
  • the amount of heat exchange between the refrigerant and the refrigerant and the heat exchange efficiency; at the same time, the wind resistance of the heat exchange tube 20 is reduced.
  • the fins 10 are arranged in a zigzag manner.
  • the fins 10 are arranged in a zigzag manner in the direction in which the heat exchange tubes 20 are arranged, and the fins 10 are formed with a plurality of tooth tips.
  • the heat exchange tubes 20 are preferably disposed on the fins 10 .
  • the fin 10 is at the tip of the tooth.
  • the fins 10 are integrally arranged in a zigzag manner, and the fins 10 may be described as being entirely wavy, polygonal, S-shaped, W-shaped or M-shaped.
  • the fins 10 are arranged in a zigzag manner in the parallel arrangement direction of the heat exchange tubes 20, and the fins 10 are formed with a plurality of tooth tips.
  • the plurality of The tooth tips are capable of disturbing the heat exchange gas flow, thereby increasing the heat exchange amount and heat exchange efficiency of the fins 10 and the heat exchange gas stream.
  • the fins 10 and/or the bridge 40 are disposed on the fins 10.
  • the window and/or the bridge 40 is a convex structure disposed on any surface of the fin 10, and the heat exchange airflow passes through the surface of the fin 10, and the window and/or the bridge
  • the sheet 40 is capable of disturbing the air while the window and/or the bridge 40 are also capable of heat exchange with the heat exchange gas stream, thereby increasing the amount of heat exchange and heat exchange efficiency of the fin 10 and the heat exchange gas stream.
  • the plurality of windows 40 are preferably disposed along the length direction of the heat exchange tube 20, and at the same time, the plurality of windows 40 are spaced apart, and the window is The gap between them is used to pass the heat exchange gas stream. It can be understood that the plurality of windows 40 can be disposed on the fins 10 according to any rule, such as being arranged in parallel at equal intervals.
  • the window 40 can be any shape, such as an arc shape, a sheet shape, a polygonal line shape, etc.
  • the window 40 is preferably a polygonal window, and the polygonal window includes a sloped section 41 and Parallel section 42.
  • the heat exchange gas stream is blown between the windows 40 in a direction of blowing toward the paper surface.
  • the two ends of the bridge 40 are disposed on the surface of the fin 10, and a bridge hole 43 is formed between the bridge 40 and the surface of the fin 10.
  • the bridge hole 43 is used to pass a heat exchange gas stream.
  • the shape of the bridge 13 of the bridge 40 may be an arch, a semicircle, a square, an isosceles trapezoid or the like.
  • the heat exchange gas stream is blown through the bridge hole 43 as it passes through the fins 10.
  • the length of the window or the bridge 40 in the longitudinal direction of the fin 10 is L1, and the distance between the two windows or the bridge 40 in the longitudinal direction of the fin 10 is L2, the L1 The ratio of the L2 to the L2 is between 0.8 and 1.2; the width of the window or the bridge 40 in the width direction of the fin 10 is D1, and the two windows or bridges 40 are at the fin 10
  • the pitch in the width direction is D2, and the ratio of D1 to D2 is between 0.8 and 1.2.
  • the ratio of the L1 to the L2 is 1, that is, the length of the window or the bridge 40 in the longitudinal direction of the fin 10 is equal to L1, and the window or bridge 40 is The pitch of the fins 10 in the longitudinal direction is L2.
  • the ratio of the D1 to the D2 is 1, that is, the width of the window or the bridge 40 in the width direction of the fin 10 is equal to D1, and the window or bridge 40 is at the fin 10. The pitch in the width direction is D2.
  • the ratio range of the L1 to the L2 and the ratio range of the D1 to the D2 of the embodiment can reduce the production difficulty of the window or the bridge 40, and at the same time ensure the window or the bridge 40 Heat transfer effect.
  • the spacing between adjacent fins 10 is equal to the height of the window and/or bridge 40.
  • the spacing between adjacent fins 10 is equal to the height of the window and/or the bridge 40, that is, the window disposed on one of the fins 10 and / or the top end of the bridge 40 abuts on the surface of another adjacent fin 10, by providing a spacing between adjacent fins 10 equal to the height of the window and / or bridge 40,
  • the plurality of fins 10 need only be stacked together, and the height of the window and/or the bridge 40 can be determined.
  • the distance between adjacent fins 10 greatly simplifies the assembly process of the heat exchanger 100, is easier to assemble, and is simpler to manufacture.
  • the top end of the window piece and/or the bridge piece 40 on the fin 10 is welded and fixed to the adjacent fins 10.
  • the window and/or the bridge on the fin 10 is based on a technical solution in which the spacing between adjacent fins 10 is equal to the height of the window and/or the bridge 40.
  • the top end of the sheet 40 abuts on the surface of another adjacent fin 10.
  • the top end of the window and/or the bridge 40 is directly welded to the surface of the adjacent fin 10, and the welding position is easy. It is determined and the connection stability between adjacent fins 10 is enhanced.
  • the adjacent fins 10 are welded and fixed by the window and/or the bridge 40, the heat conduction between the adjacent fins 10 is facilitated, so that the overall heat of the heat exchanger 100 tends to be In the equalization, the heat exchange amount and heat exchange efficiency of the heat exchanger 100 are improved.
  • the thickness of the portion of the fin 10 adjacent to the heat exchange tube 20 is from the junction of the heat exchange tube 20 and the fin 10 .
  • the fins 10 are gradually thinned.
  • the thickness of the portion of the fin 10 between the adjacent heat exchange tubes 20 gradually decreases from the junction of the heat exchange tube 20 and the fin 10 toward the fin 10, that is, From the junction of the heat exchange tube 20 and the fin 10 toward the middle of the fin 10, the thickness of the fin 10 is gradually reduced, so that the consumable used in the molding of the fin 10 can be reduced, and the cost can be saved.
  • the thickness of the portion of the fin 10 corresponding to the junction of the heat exchange tube 20 and the fin 10 is the thickest, and the connection stability between the heat exchange tube 20 and the fin 10 can be increased.
  • the contact area between the fin 10 and the heat exchange tube 20, that is, the heat exchange area may also be increased, and the wind resistance may be reduced, and the heat exchange amount and heat exchange efficiency may be improved.
  • the surface of the thinned portion of the corresponding fin 10 between the heat exchange tubes 20 forms a groove, and the groove is a V-shaped groove.
  • the surface of the corresponding fin thinned portion between the heat exchange tubes 20 forms a groove, and the groove is an arcuate groove.
  • either surface of the fin may form the groove or both surfaces of the fin opposite each other are formed with the groove.
  • the fin 10 smoothly transitions to the heat exchange tube 20.
  • the fin 10 smoothly transitions to the heat exchange tube 20, that is, in the heat exchange tube 20 and At the junction of the fins 10, the fins 10 are arcuately transitioned to the heat exchange tubes 20, and the joints are approximately horned to enclose the heat exchange tubes 20, so that the heat exchange airflow can be reduced
  • the resistance at the joint A at the same time, the fin 10 smoothly transitions to the heat exchange tube 20 such that the thickness of the fin 10 corresponding to the junction of the heat exchange tube 20 and the fin 10 is the thickest.
  • the connection stability between the heat exchange tube 20 and the fins 10 can be increased.
  • the contact area between the fins 10 and the heat exchange tubes 20, that is, the heat exchange area can be increased to improve heat exchange. Quantity and heat exchange efficiency.
  • the edge portion of the fin 10 in the longitudinal direction is tapered (for example, the portion indicated by B in FIG. 5), that is, the edge portion of the fin 10 in the longitudinal direction is thicker than the middle portion of the fin 10.
  • the partial thickness is thin, reducing the resistance when the heat exchange gas flows between the fins 10.
  • the thickness of the heat exchange tube 20 when the heat exchange tube 20 extends on the surface of the fin 10, the thickness of the heat exchange tube 20 is located, that is, the heat exchange tube 20 And a ratio of the total thickness c of the fins 10 to the thickness d of the fins 10 is greater than or equal to 1 and less than or equal to 15; when the heat exchange tubes 20 are formed in the fins 10, the heat exchange tubes 20 The thickness of the position, that is, the ratio of the thickness c of the heat transfer tube 20 itself to the thickness d of the fin 10 is 1 or more and 15 or less.
  • the thickness c of the position of the heat exchange tube 20 is the thickness and the thickness of the heat exchange tube 20.
  • the sum of the thicknesses d of the fins 10 is described.
  • the thickness c of the position where the heat exchange tube 20 is located is the thickness of the heat exchange tube 20 itself. In the actual production process, the smaller the thickness of the heat exchange tube 20 is, the smaller the heat exchange tube 20 is, and the more difficult the processing of the heat exchange tube 20 is.
  • the air side pressure loss is larger, and the air side pressure loss is heat exchange.
  • the ratio of the thickness of the heat exchange tube 20 to the thickness of the fin 10 is greater than or equal to 1 and less than 15, and the thickness of the position where the heat exchange tube 20 is located and the thickness of the fin 10 are limited.
  • the proportional relationship ensures that the thickness of the heat exchange tube 20 is not too small relative to the thickness of the fin 10 on the one hand, that is, the inner diameter or the equivalent inner diameter of the heat exchange tube 20 is not too small, thereby reducing The processing difficulty of the heat exchange tube 20 is small; on the other hand, the ratio of the thickness of the heat exchange tube 20 to the thickness of the fin 10 is not too large, that is, the inner diameter of the heat exchange tube 20 is ensured. Or the equivalent inner diameter is not too large, reducing the resistance of the heat exchange gas flowing through the heat exchange tube 20, slowing down the attenuation of the heat exchange gas flow rate, thereby improving the heat exchange effect of the heat exchange gas stream.
  • the ratio of the total thickness of the heat exchange tube 20 and the fin 10 to the thickness of the fin 10 is 5;
  • the ratio of the thickness of the heat exchange tube 20 to the thickness of the fin 10 is 5.
  • the ratio b/a ⁇ 10 of the area b occupied by the portion of the fin 10 between the adjacent heat exchange tubes 20 and the area occupied by the position of the heat exchange tube 20 is b/a ⁇ 10.
  • heat exchange is performed between the heat exchange tubes 20 and the fins 10, and the area occupied by the fins 10 between the adjacent heat exchange tubes 20 is as shown in FIG. b.
  • the heat dissipation efficiency of the sheet 10 is lowered; that is, the ratio b/a of the area b occupied by the portion of the fin 10 between the adjacent heat exchange tubes 20 and the area a of the heat exchange tube 20 is larger.
  • the heat dissipation of the portion of the fin 10 is more sufficient, but the heat dissipation efficiency of the fin 10 is partially lowered.
  • the present application defines a ratio b/a ⁇ 10 of the area b occupied by the portion of the fin 10 between the adjacent heat exchange tubes 20 and the area occupied by the heat exchange tube 20, by limiting the adjacent
  • the relative proportion of the area b of the portion of the fins 10 between the heat exchange tubes 20 and the area a of the heat exchange tubes 20 is such that the heat dissipation area and the heat dissipation efficiency of the fins 10 are as balanced as possible.
  • the fin 10 has a large heat dissipation area and has high heat dissipation efficiency.
  • the ratio of the area b occupied by the fin portions between the adjacent heat exchange tubes to the area a occupied by the position of the fins is 5.
  • the fin 10 extends to the header 30 to form a connecting portion 50 , and the thickness of the connecting portion 50 gradually increases from the fin 10 to the collecting tube 30 . .
  • a plurality of openings are formed in the header 30, and the heat exchange tube 20 is inserted into the header 30 through an opening, and insertion time is required in the production process, resulting in a decrease in production processing efficiency and insertion into the opening.
  • the increase also increases the risk of refrigerant leakage and reduces the reliability and safety of the heat exchanger 100.
  • the fin 10 extends to the header 30 to form a connecting portion 50.
  • the connecting portion 50 is welded or fixed to the collecting tube 30 or integrally formed with the collecting tube 30.
  • the thickness of the connecting portion 50 gradually increases from the fin 10 toward the header 30, that is, the closer the connecting portion 50 is to the header 30, the greater the thickness of the connecting portion 50 is. Thereby, the contact area of the connecting portion 50 with the header 30 is increased, and the connection stability between the header 30 and the fin 10 is enhanced.
  • the connecting portion 50 is welded or fixed to the header 30 or integrally formed with the header 30.
  • the connecting portion 50 and the collecting tube 30 are smoothly connected to avoid wing.
  • the risk that the refrigerant generated by the sheet 10 or the heat exchange tube 20 is directly inserted into the header 30 is likely to leak, and the connecting portion 50 and the header 30 are combined by welding or integral molding to increase the header 30 and the fin.
  • the connection between the sheets 10 is stable, while reducing the difficulty of production and processing, and improving production efficiency.
  • the diameter of the heat exchange tube 20 located in the connecting portion 50 gradually increases from the fin 10 to the header 30. Thereby, the inlet area of the refrigerant flowing into the heat exchange tube 20 in the header 30 is increased, so that the refrigerant can more easily flow into the heat exchange tube 20 from the header 30.
  • a portion of the collecting pipe 30 connected to the connecting portion 50 is provided with a plurality of through holes 51, and the number of the plurality of through holes 51 corresponds to The number of the heat exchange tubes 20 on the fins 10, the heat exchange tubes 20 communicate with the headers 30 through the through holes 51, and the refrigerant in the headers 30 flows through the through holes 51. Said inside the heat exchange tube 20.
  • a hollow draft tube 60 is disposed at the inlet of the collecting tube 30 , and the heat exchange tube 20 is in communication with the collecting tube 30 , and the inside of the guiding tube 60
  • the flow cross section is smaller than the flow cross section in the header 30.
  • the refrigerant enters the heat exchange tube 20 through the draft tube 60 and the header 30; the refrigerant is in a high-pressure liquid state when the refrigerant is in the draft tube 60, because the guide tube 60 is in communication with the header 30, and the flow cross section in the draft tube 60 is smaller than the flow cross section in the header 30, and when the high pressure liquid refrigerant flows into the header 30 from the draft tube 60,
  • the air pressure drops suddenly, part of the high-pressure liquid refrigerant is vaporized into a gaseous state, and the refrigerant becomes a gas-liquid mixed state in the header 30, and the gas-liquid mixed state refrigerant can flow more uniformly into the heat exchange tube 20, thereby improving
  • the distribution of the refrigerant in the plurality of heat exchange tubes 20 is uniform, thereby improving the heat exchange effect of the heat exchanger 100.
  • the heat exchanger 100 when used as an evaporator, a large amount of heat is absorbed by the refrigerant from a high-pressure liquid vaporization to a gaseous state, and the cooling effect of the evaporator can be further improved.
  • one end of the collecting tube 30 adjacent to the guiding tube 60 is provided with a temperature sensing memory metal (not shown).
  • a temperature sensing memory metal is disposed at one end of the current collecting tube 30 adjacent to the draft tube 60, and the temperature sensing memory metal can be deformed according to a temperature change, thereby adjusting the guiding current.
  • the tube 60 enters the flow rate of the refrigerant to the header 30, thereby adjusting the amount of heat exchange of the heat exchanger 100.
  • the inlet area of the refrigerant flowing into the header 30 in the draft tube 60 is increased, so that the refrigerant can more easily flow into the header 30 from the draft tube 60.
  • the fins 10 are disposed at an angle with the collecting tube 30, and the angle ranges from 30° to 90°.
  • the header 30 is a long tubular shape, the fins 10 are in the form of a sheet, and the fins 10 are disposed at an angle with the header 30, that is, the fins 10
  • the surface extension direction is disposed at an angle with the length extension direction of the header 30; the length extension direction of the header 30 is generally perpendicular to the inflow direction of the heat exchange gas flow, that is, the surface extension direction of the fin 10. It is disposed at an angle with the inflow direction of the heat exchange gas flow and has an included angle ranging from 0° to 60°.
  • the surface extending direction of the fin 10 When the surface extending direction of the fin 10 is at an angle of 0° with the inflow direction of the heat exchange gas flow, the surface extending direction of the fin 10 is parallel to the inflow direction of the heat exchange gas flow, and the heat exchange gas flow smoothly flows through the The surface of the fin 10 is subjected to heat exchange.
  • the heat exchange gas flow is blown into the fins 10 at an angle, so that the heat exchange gas flow reciprocates back and forth between the fins 10, increasing the residence time of the heat exchange gas flow between the fins 10, Thereby, the heat exchange amount and heat exchange efficiency of the fin 10 and the heat exchange gas flow are improved.
  • the second embodiment is different from the first embodiment in that the heat exchange tube 20 extends over the surface of the fin 10, and the The heat exchange tube 20 is welded to the surface of the fin 10 to be integrally formed with the fin 10.
  • the heat exchange tube 20 is welded to the surface of the fin 10 and integrally formed with the fin 10, so that the heat exchange tube 20 extends on the surface of the fin 10, that is, the The heat exchange tube 20 is protruded from the surface of the fin 10, and an elongated contact portion is formed between the heat exchange tube 20 and the fin 10, and the heat exchange tube 20 and the fin 10 are
  • the heat exchange between the heat exchange tubes 20 and the fins 10 can be increased by heat exchange between the strip-shaped contact portions, thereby increasing the heat exchange between the heat exchange tubes 20 and the fins 10. And heat exchange efficiency.
  • the heat exchange tubes 20 are alternately protruded from the opposite faces of the fins 10 by welding.
  • the fins 10 are preferably in the form of a sheet, including two surfaces opposite to each other; when the heat exchange tubes 20 and the fins 10 are integrally formed by a welding process, the heat exchange tubes 20 are inevitably At least one surface of the fin 10 is projected.
  • the heat exchange tubes 20 welded to the fins 10 are wavy and/or polygonal.
  • the heat exchange tubes 20 welded to the fins 10 are wavy and/or polygonal, and include two forms: one is that the surface of the fins 10 is a plane, and the heat exchange The tube 20 itself is undulated and/or line-shaped (as shown in Fig. 12), the wavy or polygonal heat exchange tube 20 is directly welded to the surface of the fin 10, and the fin 10 is The surface itself is also wavy or polygonal, the wavy or polygonal heat exchange tubes 20 being adapted to the undulating or polygonal surface of the fins 10, said wavy or polygonal heat exchange The tube 20 is fitted to a wavy or polygonal surface on the fin 10 and is welded to the surface of the fin 10.
  • the heat exchange tube 20 has a wave shape or a polygonal shape. It can also be described that the heat exchange tube 20 has a zigzag shape, a U shape, a V shape, a W shape, an S shape or an M shape as a whole.
  • heat exchange tubes 20 can also be the most common linear tubes.
  • the heat exchange tubes 20 welded to the fins 10 are provided in a wave shape and/or a line shape, and the length of the single heat exchange tubes 20 on the fins 10 can be lengthened.
  • the flow path of the refrigerant in the heat exchange tube 20 is made longer, thereby increasing the amount of heat exchange between the heat exchange tube 20 and the refrigerant.
  • the header 30 has at least two installation modes as follows. ;
  • the first arrangement of the header 30 is that the heat exchanger 100 further includes a single-side header 30 disposed at one end of the fin 10 in the longitudinal direction.
  • the unilateral header 30 includes an inflow channel 31 and an outflow channel 32.
  • the inflow channel 31 and the outflow channel 32 are respectively disposed at two ends in the width direction of the fin 10;
  • the inflow passage 31 and the outflow passage 32 are connected.
  • the heat exchange tube 20 may have a U-shaped, a V-shaped, a W-shaped, an S-shaped or an M-shaped shape on the fin 10 as a bent shape.
  • each of the heat exchange tubes 20 only needs to have an inlet at the inflow end 21 of the heat exchange tube 20, and an outlet is provided at the outflow end 22 of the heat exchange tube 20, and the inlet and the outlet are connected to the single
  • the side header 30 is electrically connected, thereby greatly reducing the number of through holes 51 in the single-side header 30, and facilitating welding of the inflow end 21 and the outflow end 22 to the single-side header 30. Improve refrigerant leakage and improve reliability and safety.
  • the header 30 adopts a single-side header 30 including a two-channel form of an inflow channel 31 and an outflow channel 32.
  • the inflow end 21 and the outflow end 22 of the heat exchange tube 20 are integrated with the single-side header 30. Molded or connected by welding, the structure is compact, the heat exchange amount and the heat exchange efficiency are high, and the heat exchanger 100 can be miniaturized.
  • the second arrangement of the header 30 is that the heat exchanger further includes a bilateral header 30 , and the bilateral header 30 includes an inflow tube 33 and an outflow tube 34 , and the inflow The tube 33 and the outflow tube 34 are respectively disposed at opposite ends in the longitudinal direction of the fin 10; both ends of the heat exchange tube 20 communicate with the inflow tube 33 and the outflow tube 34, respectively.
  • the heat exchange tube 20 may be U-shaped, V-shaped, W-shaped, or S-shaped on the fin 10 in addition to the conventional linear tube arrangement. Or the M-shaped or the like is in a bent arrangement, and each of the heat exchange tubes 20 needs to be provided with an inlet and an outlet, except that the inlet and the outlet need to be disposed at opposite ends of the fin 10 in the longitudinal direction.
  • the header 30 is a bilateral header
  • the inflow tube 33 and the outflow tube 34 are flat, such that the inflow tube 33 and the outflow tube 34 are in smooth contact with the fins 10.
  • the material of the fin 10 and the heat exchange tube 20 is graphite.
  • the fin 10 and the heat exchange tube 20 are both graphite materials, and the graphite material has stronger thermal conductivity, and can improve the heat exchange amount and heat exchange efficiency of the fin 10 and the heat exchange tube 20.
  • the graphite material is preferably a graphene material.
  • a hydrophobic layer is disposed on the surface of the fin 10 .
  • the fins 10 are condensed with condensed water, and the fins 10 are provided with a hydrophobic layer for facilitating the condensed water from the fins.
  • the sheet 10 flows down and out of the evaporator.
  • the fourth embodiment claims a fin 10 based on the first embodiment or the second embodiment or the third embodiment.
  • the slitting structure
  • At least one slit concave portion C is disposed on at least one surface of the predetermined slitting position of the fin 10, and a portion of the corresponding fin 10 in the slit concave portion C is thicker than the fin 10
  • the other parts are thin.
  • the recess C is disposed on at least one surface of the predetermined slit position of the fin 10, and the thickness of the corresponding fin 10 portion in the recess C is thinner than the thickness of other portions of the fin 10, thereby reducing
  • the slitting difficulty of the fins 10 can also reduce the wind resistance and enhance the heat exchange effect.
  • the two surfaces of the fins 10 opposite to each other are provided with the slit recess C, and in order to ensure the strength of the fin 10 during the production process, the length of the slit recess C is defined as The range of M, M is 0.5-1 mm, and the thickness of the fin 10 in the slit recess C is defined as H, and the relationship between the thickness H and the length M satisfies 1/4 ⁇ M / H ⁇ 1/2. It can be understood that the ratio of the length M of the slit recess C to the thickness H may not be limited without considering the strength of the fin 10 during production.
  • the slit recess C is a V-shaped groove formed concavely in the fin 10, and the surface of the fin 10 defining the groove surface of the V-shaped groove and the groove surface is defined.
  • the angle between the two is A, and the angle A satisfies 150 ⁇ ⁇ A ⁇ 170 ⁇ .
  • the slit recess C is an arcuate groove formed concavely in the fin 10, and the radius R of the arcuate groove satisfies 8 mm ⁇ R ⁇ 15 mm.
  • two slit recesses C are provided in the predetermined slit position of the fins 10, and the two slit recesses C are disposed to form a W-shaped groove. In the process of slitting the fins 10, it is only necessary to cut one of the slit recesses C, thereby further reducing the difficulty of the slitting of the fins 10.
  • the fins 10 are condensed with condensation water, and the heat exchange tubes 20 and the fins 10 are vertically placed. Under the action of gravity, condensed water flows down from the fins 10 and flows out of the evaporator, and the drainage performance is excellent. Therefore, in the prior art, the problem that the heat transfer tube 20 has a large diameter and the heat exchange tube 20 is horizontally arranged causes the condensed water to be discharged poorly.
  • the heat dissipation effect of the heat exchanger 100 is proportional to the heat dissipation efficiency, and the heat exchange amount is larger, the heat dissipation efficiency is higher, and the heat dissipation effect is better. According to the theory of heat transfer:
  • Air side heat transfer coefficient h o (A p + ⁇ A f )/A o ⁇ h a (3)
  • a o heat conduction area on the air side
  • h w thermal conductivity on the refrigerant side
  • a p heat conduction area of the tube
  • h a air side conductivity of the fin portion
  • a pi heat conduction area on the refrigerant side
  • a f fin portion Thermal conductivity area
  • a co contact area of the fin and the tube
  • ⁇ fin efficiency
  • h c contact conductivity of the fin and the tube
  • ⁇ T temperature difference.
  • the heat transfer amount has a positive linear relationship with the total heat transfer coefficient and the heat conduction area on the air side.
  • the total heat transfer coefficient and the air side can be increased.
  • the way of heat conduction area is realized.
  • the total heat transfer coefficient is affected by the heat transfer area on the air side and the heat transfer coefficient on the air side, and is inversely related to the heat transfer area on the air side, and positively related to the heat transfer coefficient on the air side. This is because the larger the heat transfer area on the air side of the fin 10, the larger the contact surface of the fin 10 with the air, and the contact area between the fin 10 and the heat exchange tube 20 is also compressed, so that the heat transfer area of the fin 10 is made.
  • the heat transfer area of the heat exchange tube 20 is simultaneously reduced, resulting in a decrease in heat conduction efficiency between the two, resulting in poor heat transfer effect, and heat is difficult to exchange heat with the air through the fins 10, thereby reducing the air side heat transfer coefficient.
  • the total heat transfer coefficient is reduced and the heat exchange amount is reduced. Therefore, in order to obtain an ideal heat dissipation effect, it is necessary to satisfy the requirement of the heat transfer area between the fins 10 and the heat transfer tubes 20, and at the same time, it is necessary to increase the air side heat exchange area of the fins 10.
  • FIG. 16 and FIG. 18 respectively compare the heat exchange amount and air side exchange of the heat exchanger 100 with the common fin-and-tube heat exchanger and the microchannel heat exchanger under the same conditions.
  • Thermal coefficient According to the experimental results, under the same conditions, the heat exchanger 100 has a larger heat transfer amount and an air side heat exchange system, and the heat dissipation effect is more than that of the common fin-and-tube heat exchanger and the microchannel heat exchanger. Excellent.
  • Figure 4 compares the loss of air side pressure between the heat exchanger 100 and the common fin-and-tube heat exchanger and microchannel heat exchanger under the same conditions. It is known from the experimental results that the fin-and-tube heat exchanger is Compared with the heat exchanger 100, the air side pressure reduction rate is smaller, and the wind resistance performance has obvious advantages.
  • the present application also provides a heat exchange device (not shown) comprising the heat exchanger 100 of any of the above embodiments.
  • the heat exchange device includes an air conditioner, a refrigerator, or a dehumidifier, and the like that requires heat exchange. Since the heat exchange device includes the heat exchanger 100 of any of the above embodiments, at least the entire technical effects of the heat exchanger 100 described above are not described herein.

Abstract

一种换热器（100）及换热设备。换热器（100）包括：间隔设置的多个翅片（10），延伸于翅片（10）表面或者形成于翅片（10）内的多个换热管（20）。换热器（100）及换热设备具有换热管（20）与翅片（10）的换热量及换热效率高的优点。

Description

换热器及换热设备 技术领域
本申请涉及换热器技术领域，特别涉及一种换热器及换热设备。
背景技术
现有技术中，换热器的换热管一般为垂直穿设于翅片中，翅片一般为竖向放置，换热管一般为水平穿设与所述翅片中，换热管与翅片的换热面积较小，热阻较大，导致换热管与翅片换热效率降低。
发明内容
本申请提供一种换热器，旨在解决现有技术中换热管与翅片的换热面积较小，热阻较大的问题。
本申请提出的一种换热器，所述换热器包括：多个翅片，所述多个翅片间隔设置；以及换热管，延伸于所述翅片表面或者形成于所述翅片内。
本申请还提出一种换热设备，所述换热设备包括换热器，所述换热器包括：多个翅片，所述多个翅片间隔设置；以及换热管，延伸于所述翅片表面或者形成于所述翅片内。
本申请技术方案通过使所述换热管形成于所述翅片内，至少具有如下技术效果：(1)使得所述换热管任意部位均与所述翅片接触，从而使所述换热管与所述翅片的换热面积最大化，也使得所述换热管与所述翅片的换热量和换热效率最大化；(2)所述换热管被所述翅片包围，所述换热管不易泄露冷媒，可靠性和安全性更有保障；(3)所述换热管与所述翅片通过一体成型，制造更简单；
本申请技术方案通过使所述换热管延伸于所述翅片表面，至少具有如下技术效果：所述换热管与所述翅片之间形成一长条状的接触部位，所述换热管与所述翅片之间通过长条状的接触部位进行热交换，能够增大所述换热管与所述翅片的换热面积，进而提高所述换热管与所述翅片的换热量及换热效率。
附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本申请换热器一实施例的立体结构示意图；
图2为本申请翅片与换热管一实施例的结构示意图；
图3为本申请翅片与换热管另一实施例的结构示意图；
图4为本申请翅片与换热管另一实施例的结构示意图；
图5为本申请翅片与换热管另一实施例的结构示意图；
图6为本申请翅片与换热管另一实施例的结构示意图；
图7为本申请翅片与换热管另一实施例的结构示意图；
图8为本申请翅片与换热管另一实施例的结构示意图；
图9为本申请换热管所在位置的厚度与所述翅片厚度之比与空气侧压力损失的关系变化图；
图10为本申请换换热管之间的翅片部分所占面积与所述换热管所在位置所占面积之比与翅片换热效率的关系变化图；
图11为本申请集流管、翅片与换热管一实施例的结构示意图；
图12为本申请集流管、翅片与换热管另一实施例的结构示意图；
图13为本申请集流管、翅片与换热管另一实施例的结构示意图；
图14为本申请翅片与换热管另一实施例的结构示意图；
图15为本申请翅片与换热管一实施例的结构示意图；
图16为本申请换热器与翅片管换热器、微通道换热器在相同条件下，风速与换热量的关系变化图；
图17为本申请换热器与翅片管换热器、微通道换热器在相同条件下，风速与空气侧换热系数的关系变化图；
图18为本申请换热器与翅片管换热器、微通道换热器在相同条件下，风速与空气侧压降的关系变化图。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，本申请实施例中所有方向性指示(诸如上、下、左、右、前、后……)仅用于解释在某一特定姿态(如附图所示)下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，在本申请中涉及“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
请参阅图1，本申请实提出了一种换热器100，所述换热器100包括多个翅片10、换热管20及至少一集流管30。所述多个翅片10间隔设置；每一所述翅片10上至少设置有一所述换热管20，所述换热管20形成于所述翅片10内或者延伸于所述翅片10表面；所述翅片10设置于所述集流管30上，且所述换热管20与所述集流管30相互连通。
其中，所述集流管30用于传送冷媒，冷媒经所述集流管30被传送至所述换热管20内；所述换热管20用于与所述翅片10进行热量交换，从而提升或者降低所述翅片10温度；所述翅片10用于与所述翅片10周围气体进行热量交换，从而提升或者降低所述翅片10周围气体的气温。
请参阅图1，作为本申请的第一种实施例，所述换热管20形成于所述翅片10内，所述换热管20与所述翅片10通过浇筑工艺一体 成型。
现有技术中，所述换热管20一般为垂直穿设于所述翅片10中，所述换热管20通过胀管技术与所述翅片10固定连接，所述换热管20与所述翅片10之间仅能通过所述换热管20与所述翅片10的连接处进行热交换，所述换热管20和所述翅片10之间的接触热阻较大，导致所述换热管20与所述翅片10之间换热量及换热效率较低。同时，通过胀管技术连接的所述换热管20与所述翅片10之间还是会存在间隙，也会降低所述换热管20与所述翅片10之间的换热量及换热效率。
在本实施例中，将所述换热管20与所述翅片10通过浇筑工艺一体成型，所述换热管20形成于所述翅片10内，至少具有如下技术效果：(1)所述换热管20形成于所述翅片10内，使得所述换热管20任意部位均与所述翅片10接触，从而使所述换热管20与所述翅片10的换热面积最大化，也使得所述换热管20与所述翅片10的换热量和换热效率最大化；(2)所述换热管20被所述翅片10包围，所述换热管20不易泄露冷媒，可靠性和安全性更有保障；(3)所述换热管20与所述翅片10通过浇筑工艺一体成型，制造更简单。
可以理解，所述换热管20与所述翅片10通过浇筑工艺一体成型时，除了所述换热管20形成于所述翅片10内之外，所述换热管20也可以形成于所述翅片10表面并延所述翅片10表面延伸，此时所述换热管20凸设于所述翅片10表面，所述换热管20与所述翅片10之间形成一长条状的接触部位，所述换热管20与所述翅片10之间通过长条状的接触部位进行热交换，与现有技术相比，同样能够增大所述换热管20与所述翅片10的换热面积，提高所述换热管20与所述翅片10的换热量及换热效率。
可选地，请参阅图2，所述换热管20交替凸设于所述翅片10相背的两个面上。
在本实施例中，所述翅片10优选为片状，包括相背的两个表面；所述换热管20任意方向上的尺寸例如管径尺寸，均大于所述翅片10的厚度，故所述换热管20与所述翅片10通过浇筑工艺一体成型时，不论所述换热管20形成于所述翅片10内，或是所述换热管20形成 于所述翅片10表面；所述换热管20必然凸出所述翅片10的至少一个表面。
在本实施例中，将所述换热管20交替凸设于所述翅片10相背的两个面上，被定义为：所述换热管20交替凸出设置于所述翅片10相背的两个表面。所述换热器100由多个所述翅片10叠设组成时，所述翅片10之间间隔设置，所述翅片10之间的间隙用于流通换热气流(图2中箭头所指方向)，也即，所述翅片10相背的两个表面均会通过换热气流。
通过将所述换热管20交替凸出设置于所述翅片10相背的两个表面，所述翅片10的两个表面形成凹凸结构，在所述换热气流流经所述翅片10表面时，所述凹凸结构能够扰动所述换热气流，从而提高所述翅片10与所述换热气流的换热量及换热效率。同时，所述换热管20凸设于所述翅片10表面，也能增加换热面积。
可以理解，所述换热管20在所述翅片10上的布设方式可以有多种，只需保证所述换热管20形成于所述翅片10内或者所述换热管20形成于所述翅片10表面且延所述翅片10表面延伸即可。如：所述换热管20也可以设置在所述翅片10单独的一个表面上；或者所述翅片10上至少划分为第一区域及第二区域，在所述第一区域内，所述换热管20凸设于所述翅片10上表面，在所述第二区域内，所述换热管20凸设于所述翅片10下表面；当然也可以对所述翅片10进行多区域划分，在不同的区域内，所述换热管20可以凸设于所述翅片10的上表面或者下表面。
可以理解，所述翅片10不局限为片状，所述翅片10也可为块状，如所述翅片10为球状，所述换热管20一部分形成于所述翅片10内时，贯穿所述球体；所述换热管20另一部分形成于所述翅片10表面且延所述翅片10表面延伸时，所述换热管20凸设于所述球面上。
由上可知，当所述换热管20贯穿所述球体时，或者所述翅片10的厚度足够厚时，所述换热管20至少部分不会凸出所述翅片10表面，也即，在本实施例中，所述换热管20可以凸出设置于所述翅片10表面，也可以形成于所述翅片10内部而不凸出所述翅片10表面。
由上可知，所述多个翅片10之间间隔设置，所述翅片10之间的间隙用于流通换热气流，在本实施例中，多个所述翅片10之间优选为等间距平行设置，使得换热气流均匀通过所述多个翅片10，同时减少换热气流通过所述多个翅片10时的风阻。可以理解，相邻所述翅片10之间也可以呈夹角设置，或者相邻所述翅片10之间也可以不等间距设置，只需保证所述翅片10两两之间有间隙供换热气流通过即可。
可选地，所述翅片10整体为弧形状设置，所述翅片10宽度方向上的截面为弧形面，从而增大所述翅片10与换热气流的换热面积。进一步可选地，相邻两个所述翅片10的弯曲方向相反，相对设置的所述翅片10的内凹面之间可形成气流漩涡，从而使换热气流在所述翅片之间的停留时间更长，从而提升换热效率。
可选地，同一所述翅片10上的相邻所述换热管20之间等间距平行设置。
在本实施例中，所述换热管为直线型管，同一所述翅片10上的相邻所述换热管20之间等间距平行设置，至少包括如下情形：
一是所述换热管20设置在所述翅片10单独的一个表面上时，所述相邻所述换热管20之间等间距平行设置；
二是所述换热管20交替凸设于所述翅片10相背的两个面时，所述翅片10相背的两个面上的且相邻的所述换热管20之间等间距平行设置；
三是所述换热管20形成于块状的所述翅片10内时，所述翅片10与周围多个相邻的翅片10之间等间距平行设置。
在本实施例中，相邻所述换热管20之间等间距平行设置，将所述换热管20内冷媒均匀传送至所述翅片10的各个部位，提高所述换热管20与所述翅片10之间的换热量及换热效率。
在另外一些实施例中，所述换热管20为波浪形或折线形或者呈U形、V形、W形、S形或者M形等非直线型管，此时，所述换热管20包括多个沿所述翅片10长度方向延伸的直线段，多个所述直线段之间的间距相同，从而将所述换热管20内冷媒均匀传送至所述翅 片10的各个部位，提高所述换热管20与所述翅片10之间的换热量及换热效率。
可选地，所述换热管20的内径或者等效内径大于等于0.2mm且小于等于3mm。
在本实施例中，当所述换热管20内的流通截面为圆形时，所述换热管20的内径大于等于0.2mm且小于等于3mm；当所述换热管20内流通截面不是圆形时，如所述换热管20内的流通截面为正方形、矩形、多边形等腰梯形或者异形时，所述等效直径为将所述非圆形流通截面转换成同等面积的圆形流通截面所对应的内径，所述等效内径大于等于0.2mm且小于等于3mm。
在本实施例中，所述换热管20的内径或者等效内径越小，同等体积的冷媒流过所述换热管20的速度也就越大，同等体积冷媒能进行的热交换也就越多；同时，较大内径的换热管20，由于流通截面较大，处于流通截面中心位置的冷媒距离所述换热管20管壁较远，不能与所述换热管20管壁充分进行热交换；而所述换热管20的内径或者等效内径越小，所述换热管20内冷媒距离所述换热管20管壁较近，能较大程度的提高所述换热管20与冷媒之间的热交换。
同时，较大内径的换热管20，会在所述翅片10表面形成较大的风阻。因此，在本实施例中，所述换热管20内径或者等效内径大于等于0.2mm且小于等于3mm。将所述换热管20内径或者等效内径尽量做小，能提高换热管20内冷媒流速，使换热管20内冷媒距离所述换热管20较近，从而提高所述换热管20与冷媒之间的换热量及换热效率；同时减小所述换热管20的风阻。
优选的，请参阅图3，所述翅片10呈锯齿状设置。
在本实施例中，所述翅片10延所述换热管20的排布方向呈锯齿状设置，所述翅片10上形成有多个齿尖，所述换热管20优选为设置于所述翅片10齿尖处。所述翅片10整体锯齿状设置，也可以描述为所述翅片10整体呈波浪形、折线形、S形、W形或者M形设置。通过将翅片10延所述换热管20的平行布设方向呈锯齿状设置，所述翅片10上形成多个齿尖，在换热气流流经所述翅片10表面时，所述多 个齿尖能够扰动所述换热气流，从而提高所述翅片10与所述换热气流的换热量及换热效率。
优选的，请一并参阅图4-6，在所述翅片10上设置有窗片及/或桥片40。
在本实施例中，所述窗片及/或桥片40为设置于所述翅片10任意表面的凸起结构，换热气流经过所述翅片10表面，所述窗片及/或桥片40能够扰动空气，同时所述窗片及/或桥片40也能与换热气流进行热交换，从而提高所述翅片10与所述换热气流的换热量及换热效率。
在一种实施例中，如图4所示，多个窗片40优选为沿着所述换热管20的长度方向延伸布设，同时，多个窗片40之间是间隔设置，窗片之间的空隙用于通过换热气流。可以理解，所述多个窗片40可按照任意规则布设于所述翅片10上，如等间距平行布设。
所述窗片40可为任意形状，如弧形状，片状，折线形状等，在本实施例中，所述窗片40优选为折线形窗片，所述折线形窗片包括斜面段41及平行段42。所述换热气流以吹向纸面的方向吹入所述窗片40之间。
在另一种实施例中，如图5-6所示，所述桥片40两端设置于所述翅片10表面，所述桥片40与所述翅片10表面之间形成桥洞43，所述桥洞43用于通过换热气流。所述桥片40的桥洞13形状可为拱形、半圆形、方形、等腰梯形等。所述换热气流经过所述翅片10时，从所述桥洞43中吹过。
可选地，所述窗片或桥片40在所述翅片10长度方向的长度为L1，两所述窗片或桥片40在所述翅片10长度方向的间距为L2，所述L1与所述L2的比值介于0.8-1.2之间；所述窗片或桥片40在所述翅片10宽度方向的宽度为D1，两所述窗片或桥片40在所述翅片10宽度方向的间距为D2，所述D1与所述D2的比值介于0.8-1.2之间。
进一步可选地，所述L1与所述L2的比值为1，也就所述窗片或桥片40在所述翅片10长度方向的长度为L1等于两所述窗片或桥片40在所述翅片10长度方向的间距为L2。所述D1与所述D2的比值 为1，也即所述窗片或桥片40在所述翅片10宽度方向的宽度为D1等于两所述窗片或桥片40在所述翅片10宽度方向的间距为D2。
若所述L2、D2太小，则所述窗片或桥片40的生产难度将增大，若所述L2、D2太大，则所述窗片或桥片40的换热效果将降低，本实施例的所述L1与所述L2的比值范围、所述D1与所述D2的比值范围能够减小所述窗片或桥片40的生产难度，同时保证所述窗片或桥片40的换热效果。
优选的，相邻所述翅片10之间的间距等于所述窗片及/或桥片40的高度。
在本实施例中，相邻所述翅片10之间的间距等于所述窗片及/或桥片40的高度，也即，设置于其中一所述翅片10上的所述窗片及/或桥片40的顶端抵接于另一相邻翅片10的表面上，通过设置相邻所述翅片10之间的间距等于所述窗片及/或桥片40的高度，在将多个所述翅片10叠设组装成所述换热器100时，只需将所述多个翅片10叠放在一起，通过所述窗片及/或桥片40的高度即可确定相邻翅片10之间的距离，极大简化所述换热器100的组装工序，更便于组装，制造更简单。
优选的，所述翅片10上的所述窗片及/或桥片40的顶端与相邻所述翅片10焊接固定。
在本实施例中，基于相邻所述翅片10之间的间距等于所述窗片及/或桥片40的高度的技术方案，所述翅片10上的所述窗片及/或桥片40的顶端抵接于另一相邻翅片10的表面上，本实施例直接将所述窗片及/或桥片40的顶端与相邻所述翅片10表面焊接固定，焊接位置容易确定，且增强了相邻所述翅片10之间的连接稳固性。此外，由于相邻所述翅片10之间通过所述窗片及/或桥片40焊接固定，便于相邻所述翅片10之间的热传导，使得所述换热器100的整体热量趋于均衡，提高所述换热器100的换热量及换热效率。
可选地，请参阅图7，相邻所述换热管20之间的翅片10部分(例如图7中括弧部分)的厚度自所述换热管20与翅片10的连接处向所述翅片10内逐渐减薄。
在本实施例中，相邻所述换热管20之间的翅片10部分的厚度自所述换热管20与翅片10的连接处向所述翅片10内逐渐减薄，也即，自所述换热管20与翅片10的连接处向所述翅片10中部，所述翅片10的厚度逐渐减薄，如此可以减少所述翅片10成型时使用的耗材，节约成本；同时，所述换热管20与翅片10的连接处对应的翅片10部分的厚度为最厚，可以增加所述换热管20与所述翅片10之间的连接稳固性，此外，也可以增加所述翅片10与所述换热管20的接触面积也即换热面积，同时也可以减小风阻，提高换热量及换热效率。
在本实施例中，可选地，所述换热管20之间对应的翅片10减薄部分表面形成凹槽，所述凹槽为V形槽。
作为一种变形实施例，所述换热管20之间对应的翅片减薄部分表面形成凹槽，所述凹槽为弧形槽。
可以理解，所述翅片任一表面可以形成所述凹槽或者所述翅片相背的两个表面均形成有所述凹槽。
可选地，请参阅图7，在所述换热管20与所述翅片10连接处(例如图7中A所指部分)，所述翅片10平滑过渡至所述换热管20。
在本实施例中，在所述换热管20与所述翅片10连接处A，所述翅片10平滑过渡至所述换热管20，也即，在所述换热管20与所述翅片10连接处，所述翅片10为弧度过渡至所述换热管20，所述连接处近似为一喇叭状包住所述换热管20，如此可以减小换热气流通过经过所述连接处A时的阻力；同时，所述翅片10平滑过渡至所述换热管20使得所述换热管20与翅片10的连接处对应的翅片10的厚度为最厚，可以增加所述换热管20与所述翅片10之间的连接稳固性，此外，也可以增加所述翅片10与所述换热管20的接触面积也即换热面积，提高换热量及换热效率。
可选地，所述翅片10长度方向上的边缘部分呈渐缩设置(例如图5中B所指部分)，也即，所述翅片10长度方向上的边缘部分厚度比翅片10中部部分厚度薄，减少换热气流流入所述翅片10之间时的阻力。
可选地，请一并参阅图8-10，当所述换热管20延伸于所述翅片 10表面时，所述换热管20所在位置的厚度，也即，所述换热管20及所述翅片10的总厚度c与所述翅片10厚度d之比大于等于1小于等于15；当所述换热管20形成于所述翅片10内时，所述换热管20所在位置的厚度，也即所述换热管20自身的厚度c与所述翅片10厚度d之比大于等于1小于等于15。
如图8所示，在本实施例中，当所述换热管20延伸于所述翅片10表面时，所述换热管20所在位置的厚度c为所述换热管20厚度与所述翅片10厚度d的总和。当所述换热管20形成于所述翅片10内时，所述述换热管20所在位置的厚度c即为所述换热管20自身厚度。实际生产过程中，所述换热管20所在位置的厚度越小时，换热管20越小，所述换热管20的加工难度越大。
如图9所示，所述换热管20所在位置的厚度c与所述翅片10厚度d之比c/d越大时，空气侧压力损失越大，所述空气侧压力损失即换热气流经过所述翅片10后的空气压降，由图9可知，当所述换热管20所在位置的最大厚度c与所述翅片10厚度d之比大于15时，空气侧压力损失骤然变大，空气压力下降很快，也即换热气流速度衰减很快，由于所述换热管20凸设于所述翅片10上，导致流经所述换热管20的换热气流会遇到越大的阻力，影响换热气流的换热效果。
本实施例优选所述换热管20所在位置的厚度与所述翅片10厚度之比大于等于1小于等于15，限定所述换热管20所在位置的厚度与所述翅片10厚度的厚度比例关系，一方面保证所述换热管20所在位置的厚度相对所述翅片10厚度不会太小，也即保证所述换热管20的内径或者等效内径不会太小，从而减小所述换热管20的加工难度；另一方面保证所述换热管20所在位置的厚度相对所述翅片10厚度之比不会太大，也即保证所述换热管20的内径或者等效内径不会太大，减少流经所述换热管20的换热气流的阻力，减缓换热气流速度的衰减，从而提高换热气流的换热效果。
优选的，当所述换热管20延伸于所述翅片10表面时，所述换热管20及所述翅片10的总厚度与所述翅片10厚度之比为5；当所述换热管20形成于所述翅片10内时，所述换热管20的厚度与所述翅 片10厚度之比为5。
可选地，相邻所述换热管20之间的翅片10部分所占面积b与所述换热管20所在位置所占面积a之比b/a≤10。
如图10所示，在本实施例中，所述换热管20与所述翅片10之间会进行热量交换，当相邻所述换热管20之间的翅片10部分所占面积b相比所述换热管20所在位置所占面积a越大时，所述翅片10部分的散热性能越好，散热越充分；但是会导致相邻所述换热管20之间的翅片10部分散热效率会降低；也即当相邻所述换热管20之间的翅片10部分所占面积b与所述换热管20所在位置所占面积a之比b/a越大时，所述翅片10部分的散热越充分，但会导致所述翅片10部分散热效率降低。
本申请限定所述相邻所述换热管20之间的翅片10部分所占面积b与所述换热管20所在位置所占面积a之比b/a≤10，通过限定相邻所述换热管20之间的翅片10部分所占面积b与所述换热管20所在位置所占面积a的相对占比，使得所述翅片10的散热面积及散热效率尽可能均衡，所述翅片10具有较大散热面积的同时具有较高的散热效率。
可选地，相邻所述换热管之间的翅片部分所占面积b与所述翅片所在位置所占面积a之比为5。
可选地，请参阅图1，所述翅片10向所述集流管30延伸出一连接部50，所述连接部50厚度自所述翅片10向所述集流管30逐渐增大。
现有技术中，所述集流管30上开设若干开口，所述换热管20通过开口插入所述集流管30中，生产过程中需要插入时间，导致生产加工效率降低，同时插入开口的增多也增加了冷媒泄露的风险，降低换热器100的可靠性和安全性。
在本实施例中，所述翅片10向所述集流管30延伸出一连接部50，所述连接部50与所述集流管30焊接固定或者与所述集流管30浇筑一体成型，所述连接部50厚度自所述翅片10向所述集流管30逐渐增大，也即所述连接部50越靠近所述集流管30，所述连接部50 的厚度越大，从而增大所述连接部50与所述集流管30的接触面积，增强所述集流管30与所述翅片10之间的连接稳固性。
特别需要指出的是，所述连接部50与所述集流管30焊接固定或者与所述集流管30浇筑一体成型，所述连接部50与所述集流管30为平滑连接，避免翅片10或者换热管20直接插入集流管30产生的冷媒易于泄露的风险，由于连接部50与集流管30通过焊接技术或者一体成型结合，增大所述集流管30与所述翅片10之间的连接稳固性，同时降低生产加工难度，提高生产效率。
进一步可选地，位于所述连接部50内的所述换热管20的管径自所述翅片10向所述集流管30逐渐增大。从而增大所述集流管30内冷媒流入所述换热管20的入口面积，使冷媒更易于从所述集流管30流入所述换热管20内。
请一并参阅图1及图11，在本实施例中，所述集流管30与所述连接部50连接的部位开设有多个通孔51，所述多个通孔51数量对应于所述翅片10上的换热管20的数量，所述换热管20通过所述通孔51与所述集流管30连通，所述集流管30内冷媒通过所述通孔51流入所述换热管20内。
可选地，请参阅图1，所述集流管30入口处设置有中空的导流管60，所述换热管20与所述集流管30连通，且所述导流管60内的流通截面小于所述集流管30内的流通截面。
在本实施例中，冷媒经所述导流管60、所述集流管30后进入所述换热管20内；冷媒在所述导流管60时为高压液态，由于所述导流管60与所述集流管30连通，且所述导流管60内的流通截面小于所述集流管30内的流通截面，高压液态冷媒从所述导流管60流入集流管30时，气压骤降，部分高压液态冷媒部分汽化成气态，在所述集流管30内冷媒变成气液混合态，气液混合态的冷媒能更均匀地流通至所述换热管20内，提高多个所述换热管20内冷媒的分布均匀性，从而提高所述换热器100的换热效果。
此外，当所述换热器100作为蒸发器使用时，冷媒从高压液态汽化成气态的过程中吸收大量的热量，可以进一步提高所述蒸发器的降 温效果。
可选地，所述集流管30靠近所述导流管60的一端设置有感温记忆金属(图未标示)。
在本实施例中，通过在所述集流管30靠近所述导流管60的一端设置有感温记忆金属，所述感温记忆金属能根据温度变化进行形变，从而调节从所述导流管60进入到所述集流管30的冷媒的流量，从而调节所述换热器100的换热量。
可选地，所述导流管60距离所述集流管30入口越近，所述导流管60内的连通截面越大。从而增大所述导流管60内冷媒流入所述集流管30的入口面积，使冷媒更易于从导流管60流入所述集流管30内。
可选地，所述翅片10与所述集流管30呈夹角设置，所述夹角范围为30°-90°。
在本实施例中，所述集流管30为长管状，所述翅片10为片状，所述翅片10与所述集流管30呈夹角设置，也即所述翅片10的表面延伸方向与所述集流管30的长度延伸方向呈夹角设置；所述集流管30的长度延伸方向一般与换热气流的流入方向垂直，也即所述翅片10的表面延伸方向与换热气流的流入方向呈夹角设置且夹角范围为0°-60°。所述翅片10的表面延伸方向与换热气流的流入方向夹角为0°时，所述翅片10的表面延伸方向与换热气流的流入方向平行，所述换热气流平顺流经所述翅片10的表面进行热交换。
所述翅片10的表面延伸方向与换热气流的流入方向呈夹角设置且夹角范围为≤60°且＞0°时，所述翅片10的表面延伸方向与换热气流的流入方向不平行，换热气流以一定角度吹入所述翅片10间，使换热气流在所述翅片10之间往复回弹前进，增加换热气流在所述翅片10间的停留时间，从而提高所述翅片10与换热气流的换热量及换热效率。
请参阅图1，作为本申请的第二种实施例，本第二种实施例与第一实施例的不同之处在于：所述换热管20延伸于所述翅片10表面，且所述换热管20焊接于所述翅片10表面与所述翅片10一体成型。
在本实施例中，将所述换热管20焊接于所述翅片10表面与所述翅片10一体成型，使所述换热管20延伸于所述翅片10表面，也即所述换热管20凸设于所述翅片10表面，所述换热管20与所述翅片10之间形成一长条状的接触部位，所述换热管20与所述翅片10之间通过长条状的接触部位进行热交换，能够增大所述换热管20与所述翅片10的换热面积，进而提高所述换热管20与所述翅片10的换热量及换热效率。
请参阅图2，可选地，所述换热管20通过焊接交替凸设于所述翅片10相背的两个面上。
在本实施例中，所述翅片10优选为片状，包括相背的两个表面；所述换热管20与所述翅片10通过焊接工艺一体成型时，所述换热管20必然凸出所述翅片10的至少一个表面。
请一并参阅图12-13，可选地，焊接于所述翅片10上的所述换热管20为波浪形及/或折线形。
在本实施例中，焊接于所述翅片10上的所述换热管20呈波浪形及/或折线形，包括两种形式：一是所述翅片10表面为平面，所述换热管20本身呈波浪形及/或折线形设置(如图12所示)，所述波浪形或折线形的换热管20直接焊接在所述翅片10表面上，二是所述翅片10表面本身也为波浪形或折线形，所述波浪形或折线形的换热管20与所述翅片10上的波浪形或折线形表面相适配，所述波浪形或折线形的换热管20嵌合在所述翅片10上的波浪形或折线形表面并与所述翅片10表面焊接固定。
所述换热管20呈波浪形或折线形也可被描述为所述换热管20整体呈锯齿形、U形、V形、W形、S形或者M形。
可以理解，所述换热管20也可为最常见的直线型管。
在本实施例中，焊接于所述翅片10上的所述换热管20为波浪形及/或折线形设置，能够加长单根所述换热管20在所述翅片10上的长度，使冷媒在所述换热管20内的流经路径更长，从而提高所述换热管20与冷媒的换热量。
请一并参阅图1、图12及图13，作为本申请的第三实施例，在 上述第一实施例或者第二实施例的基础上，所述集流管30至少具有如下两种设置方式；
如图11及图12所示，所述集流管30第一种设置方式是：所述换热器100还包括设置于所述翅片10长度方向上一端的单边集流管30，所述单边集流管30包括流入通道31及流出通道32，所述流入通道31及流出通道32分别设置于所述翅片10宽度方向上的两端；所述换热管20的两端分别连通所述流入通道31和所述流出通道32。
当所述集流管为单边集流管30时，所述换热管20在所述翅片10上可以采用U形、V形、W形、S形或者M形等为弯折状的布置形式，每一所述换热管20均只需在换热管20流入端21设置一个进口，在所述换热管20流出端22设置一个出口，将所述进口及出口与所述单边集流管30导通，从而极大减少了所述单边集流管30上开设通孔51的数量，便于将所述流入端21及流出端22焊接于所述单边集流管30上，减少冷媒泄露点，提高可靠性和安全性。
同时，所述集流管30采用单边集流管30包括流入通道31及流出通道32的双通道形式，所述换热管20的流入端21及流出端22与单边集流管30一体成型或通过焊接连接，结构紧凑，换热量及换热效率高，能够实现换热器100的小型化设计。
请参阅图1，所述集流管30第二种设置方式是：所述换热器还包括双边集流管30，所述双边集流管30包括流入管33和流出管34，所述流入管33、流出管34分别设置于所述翅片10长度方向上相对的两端；所述换热管20的两端分别连通所述流入管33和所述流出管34。
当所述集流管为双边集流管30时，所述换热管20在所述翅片10上除了常规的直线型管布置方式，也可以采用U形、V形、W形、S形或者M形等呈弯折状的布置形式，每一所述换热管20需设置一个进口及一个出口，只是所述进口及出口需要设置在所述翅片10长度方向上相对的两端。
可选地，所述集流管30为双边集流管时，所述流入管33和流出管34为扁平状，以使得所述流入管33、流出管34与所述翅片10平 滑接触。
可选地，所述翅片10及换热管20的材料均为石墨。
在本实施例中，所述翅片10及换热管20均为石墨材料，石墨材料具有更强的导热性能，能够提高所述翅片10及换热管20的换热量及换热效率。所述石墨材料优选为石墨烯材料。
可选地，所述翅片10表面上设置有疏水层。在本实施例中，当所述换热器100作为蒸发器使用时，所述翅片10上凝结有冷凝水，所述翅片10上设置有疏水层，便于所述冷凝水从所述翅片10流下并流出所述蒸发器。
请一并参阅图14-15，作为本申请的第四实施例，在上述第一实施例或者第二实施例或者第三实施例的基础上，本第四实施例要求保护一种翅片10的分切结构。
在本实施例中，在所述翅片10的预设分切位置的至少一表面上设置至少一分切凹部C，所述分切凹部C内对应的翅片10部分的厚度比翅片10其他部分的厚度薄。所述翅片10的预设分切位置上至少一表面上设置有所述凹部C，由于所述凹部C内对应的翅片10部分的厚度比翅片10其他部分的厚度薄，从而减小所述翅片10的分切难度，同时也可减小风阻，提升换热效果。
可选地，所述翅片10相背的两个表面均设置有所述分切凹部C，同时为了保障所述翅片10在生产过程中的强度，定义所述分切凹部C的长度为M，M的范围为0.5-1mm，定义所述分切凹部C内翅片10的厚度为H，厚度H与长度M之间的关系满足1/4≤M/H≤1/2。可以理解，在不考虑所述翅片10在生产过程中的强度的情况下，所述分切凹部C的长度为M与厚度H之间的比值可以不做限定。
在一种实施例中，所述分切凹部C为向所述翅片10内凹陷形成的V形槽，定义所述V形槽的槽面与所述槽面相接的翅片10表面之间的夹角为A，所述夹角A满足150□≤A≤170□。
在一种实施例中，所述分切凹部C为向所述翅片10内凹陷形成的弧形槽，所述弧形槽的半径R满足8mm≤R≤15mm。
在一种实施例中，在所述翅片10预设分切位置上设置有两处分 切凹部C，所述两处分切凹部C相接设置形成一W形槽。在对所述翅片10进行分切的过程中，只需切断其中一分切凹部C皆可，从而进一步减小所处翅片10的分切难度。
作为一种实施例，当所述换热器100作为空调器的蒸发器实用时，所述翅片10上凝结有冷凝水，将所述换热管20及所述翅片10竖直放置，在重力作用下，冷凝水从所述翅片10流下并流出所述蒸发器，排水性能优良。从而解决现有技术中由于换热管20管径过大，且换热管20为水平布置，导致冷凝水排放不畅的问题。
请一并参阅图16-18，具体地，换热器100的散热效果与散热效率成正比，而换热量越大，散热效率越高，散热效果越好。根据传热学理论：
换热量Q＝K·A o·ΔT         (1)
总传热系数
Figure PCTCN2018093150-appb-000001
空气侧换热系数h o＝(A p+η·A f)/A o×h a      (3)
其中，A o：空气侧导热面积；h w：冷媒侧热传导率；A p：管导热面积；h a：翅片部分空气侧传导率；A pi：冷媒侧导热面积；A f：翅片部分导热面积；A co：翅片与管的接触面积；η：翅片效率；h c：翅片与管的接触传导率；ΔT：温度差。
结合关系式(1)、(2)、(3)可知，换热量与总传热系数和空气侧导热面积成正线性关系，若要提高散热效率，可通过增大总传热系数和空气侧导热面积的方式实现。然而，总传热系数受空气侧导热面积和空气侧换热系数的影响，并且与空气侧导热面积成反向关系、与空气侧换热系数成正向关系。这是因为翅片10上空气侧导热面积越大，翅片10与空气的接触面越大，同时亦压缩了翅片10与换热管20之间的接触面积，使翅片10的导热面积和换热管20的导热面积同时减小，导致两者之间的导热效率降低，使得热传递效果较差，热量难以通过翅片10与空气进行热交换，从而使空气侧换热系数减小，总传热系数减小，换热量降低。因此，想要获得理想的散热效果，需要满足翅片10与换热管20之间的导热面积的要求，同时，需要增大 翅片10的空气侧换热面积。
如图16至图18所示，图16和图18分别比较了本换热器100与常见的翅片管式换热器和微通道换热器在同等情况下的换热量和空气侧换热系数。根据实验结果可知，在同等条件下，本换热器100具有更大的传热量和空气侧换热系统，与常见的翅片管式换热器和微通道换热器相比，散热效果更加优异。图4中比较了本换热器100与常见的翅片管式换热器和微通道换热器在同等情况下的空气侧压力的损失，由实验结果可知，与翅片管换热器相比，本换热器100的空气侧压力降低速率更小，风阻性能具有明显的优势。
本申请的还提供一种换热设备(图未标示)，包括上述任一实施例所述的换热器100。所述换热设备包括空调器、冰箱或者除湿器等需要进行热量交换的设备。由于所述换热设备包括上述任一实施例的换热器100，因此，至少具有上述换热器100的全部技术效果，在此不再赘述。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的发明构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。

Claims (17)

  1. 一种换热器，其中，所述换热器包括：
    多个翅片，所述多个翅片间隔设置；以及
    换热管，延伸于所述翅片表面或者形成于所述翅片内。
  2. 根据权利要求1所述的换热器，其中，所述换热管与所述翅片一体成型并凸设于所述翅片上；或者所述换热管焊接于所述翅片表面上。
  3. 根据权利要求1所述的换热器，其中，所述换热管交替凸设于所述翅片相背的两个面上。
  4. 根据权利要求1所述的换热器，其中，所述翅片长度方向上的边缘厚度呈渐缩设置。
  5. 根据权利要求1所述的换热器，其中，所述翅片整体呈弧形设置，所述翅片宽度方向上的截面为弧形面。
  6. 根据权利要求5所述的换热器，其中，相邻的两所述翅片的弯曲方向相反。
  7. 根据权利要求1所述的换热器，其中，所述翅片呈锯齿状设置。
  8. 根据权利要求7所述的换热器，其中，所述换热管设置在所述翅片的齿尖处。
  9. 根据权利要求1所述的换热器，其中，自所述换热管与翅片的连接处向所述翅片中部，所述换热管之间对应的翅片部分的厚度逐渐减薄。
  10. 根据权利要求1所述的换热器，其中，所述换热器还包括设置于所述翅片长度方向上一端的单边集流管，所述单边集流管包括流入通道及流出通道，所述流入通道及流出通道分别设置于所述翅片宽度方向上的两端；所述换热管的两端分别连通所述流入通道和所述流出通道。
  11. 根据权利要求1所述的换热器，其中，所述换热器还包括双边集流管，所述双边集流管包括流入管和流出管，所述流入管、流出 管分别设置于所述翅片长度方向上相对的两端；所述换热管的两端分别连通所述流入管和所述流出管。
  12. 根据权利要求11所述的换热器，其中，所述流入管及流出管流出管呈扁平状。
  13. 根据权利要求1所述的换热器，其中，所述翅片及换热管的材料均为石墨。
  14. 根据权利要求1所述的换热器，其中，所述翅片表面设置有疏水层。
  15. 一种换热设备，其中，所述换热设备包括换热器，所述换热器包括：
    多个翅片，所述多个翅片间隔设置；以及
    换热管，延伸于所述翅片表面或者形成于所述翅片内。
  16. 根据权利要求15所述的换热设备，其中，所述换热器的所述翅片及所述换热管竖向放置。
  17. 根据权利要求16所述的换热设备，其中，所述换热设备为空调器、冰箱或者除湿器。
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