WO2017129062A1 - 洗衣机、干衣机用翅片换热器及其制作方法 - Google Patents

洗衣机、干衣机用翅片换热器及其制作方法 Download PDF

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Publication number
WO2017129062A1
WO2017129062A1 PCT/CN2017/071904 CN2017071904W WO2017129062A1 WO 2017129062 A1 WO2017129062 A1 WO 2017129062A1 CN 2017071904 W CN2017071904 W CN 2017071904W WO 2017129062 A1 WO2017129062 A1 WO 2017129062A1
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WIPO (PCT)
Prior art keywords
heat exchange
fin
heat exchanger
tube
washing machine
Prior art date
Application number
PCT/CN2017/071904
Other languages
English (en)
French (fr)
Inventor
洪伟国
陈建东
刘明星
陈兰花
Original Assignee
常州市常蒸蒸发器有限公司
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.)
Filing date
Publication date
Application filed by 常州市常蒸蒸发器有限公司 filed Critical 常州市常蒸蒸发器有限公司
Priority to KR1020187020170A priority Critical patent/KR20180097638A/ko
Priority to JP2018533782A priority patent/JP2019502085A/ja
Priority to EP17743677.1A priority patent/EP3409827A4/en
Publication of WO2017129062A1 publication Critical patent/WO2017129062A1/zh
Priority to US16/048,639 priority patent/US20180335260A1/en

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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B23MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23PMETAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P15/00Making specific metal objects by operations not covered by a single other subclass or a group in this subclass
    • B23P15/26Making specific metal objects by operations not covered by a single other subclass or a group in this subclass heat exchangers or the like
    • DTEXTILES; PAPER
    • D06TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06FLAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00Domestic laundry dryers
    • D06F58/20General details of domestic laundry dryers 
    • D06F58/24Condensing arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00Heat-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
    • F28D1/02Heat-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
    • F28D1/04Heat-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
    • F28D1/047Heat-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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477Heat-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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12Tubular 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
    • F28F1/24Tubular 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
    • F28F1/32Tubular 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063Condensers

Definitions

  • the invention relates to the technical field of heat exchangers, and in particular to a fin heat exchanger for a washing machine and a clothes dryer and a manufacturing method thereof.
  • a heat exchanger is a device that transfers part of the heat of a hot fluid to a cold fluid, also known as a heat exchanger.
  • Heat exchangers play an important role in chemical, petroleum, power, food and many other industrial productions. In chemical production, heat exchangers can be used as heaters, coolers, condensers, evaporators and reboilers. Heat exchangers are also used in equipment such as refrigerators, washing machines, dry cleaning machines, and air conditioners used in daily life. Conventional heat exchangers for washing machines and dryers are mainly parallel flow or copper tube fin heat exchangers. Although finned heat exchangers are mature in structure and manufacturing process, there are still some details of defects. .
  • FIG. 1 A commonly used parallel flow form heat exchanger is shown in FIG. 1 , which comprises square tubes 121 arranged in parallel, a heat exchange fin 122 is arranged between the square tubes, a heat exchange medium is introduced into the square tube, and diffusion through the heat exchange sheet is performed.
  • Heat exchange such a heat exchange structure has poor heat exchange efficiency and takes up a large space.
  • the copper tube fin heat exchanger is shown in FIG. 2, which comprises a plurality of heat exchange copper tubes 123 and a plurality of fin groups 124. Each of the fin groups is respectively inserted with a heat exchange copper tube, and the heat exchange copper tubes are passed between The connecting elbow 120 is connected, and the two ends of the heat exchange copper tube are first flared 125 for inserting the connecting elbow, and then the heat exchange copper tube and the connecting elbow are integrally formed by welding, such that the heat exchange method There is no guarantee of smoothness between the inner wall of the copper pipe and the inner wall of the connecting elbow, and the second is to produce a solder joint at the heat exchange copper pipe and the connecting elbow.
  • the disclosure number is CN204830968U, a utility model named "a fin-type heat exchanger containing a U-shaped heat exchange tube", between the two ports of the U-shaped heat exchange tube in the finned heat exchanger
  • the elbow and the heat exchange tube are integrated by welding, that is to say, the heat exchange tube uses a welding method to connect a plurality of tubes, and the welding between the heat exchange tube and the elbow is adopted.
  • the way to make the connection the junction between the tube and the tube produces a solder joint.
  • the patent name is a dryer for dry clothes in a fully automatic washing machine, comprising a plurality of flat rectangular pipes arranged in parallel from top to bottom, disposed between adjacent pipes and on, Fins on the outer wall of the lower pipe, which constitute a metal core for heat exchange, the pipe is composed of a single composite aluminum alloy material bent and brazed; a plastic is connected at each end of the metal core
  • the cover body is configured to form a drawer structure as a whole; the plastic cover body has a flat rectangular window that is butted against the pipe, and the periphery of the plastic cover body is provided with a rubber piece.
  • the pipe is composed of a piece of composite aluminum alloy material bent and brazed.
  • the pipe circulating as a medium also needs to be welded, that is, a solder joint is generated on the pipe.
  • the thickness of the pipe through which the fluid passes is relatively thin.
  • the high temperature generated by the welding is likely to cause damage to the heat exchange tube, the welding is difficult, and the quality of the welded portion is difficult to ensure.
  • the third is because the joint of the joint number CN204830968U needs to be welded one week, and the public number CN202969102U pipe is bent and welded by a piece of composite aluminum alloy material. Due to the small volume of the heat exchanger itself, it is difficult to weld and takes a long time, which results in low efficiency of the heat exchanger/condenser, which increases the processing cost of the enterprise.
  • an object of the present invention is to provide a washing machine and a dry machine which overcome the existing solder joints in the heat exchange pipe and have heat exchanger leakage due to the presence of solder joints, unstable heat exchange performance and short service life.
  • a fin heat exchanger for a washing machine and a dryer comprising a fin group, and a heat exchange tube interposed in the fin group, the heat exchange tube being bent by a metal tube through a plurality of consecutive twists and turns and then passing at least once Folding into at least two rows of bypass groups and inserting into the above-mentioned fin group as a whole; both ends of the heat exchange tube are outside the fin group, one end serves as a medium inlet end, and the other end serves as a medium discharge end; the metal tube It is an aluminum tube or a copper tube.
  • the fin group is formed by arranging a plurality of heat exchange fins, and in order to obtain a heat exchange space between the fins, a gap is formed between adjacent heat exchange fins in the fin group, in order to make the heat exchange tube and the fin Forming a firm bond between the sets of sheets and reasonably distributing the heat exchange space between the heat exchange tubes and the fin sets, and each of the heat exchange fins is provided with a plurality of sockets for inserting the twisted pipe segments in the heat exchange tubes, and each socket corresponds to Insert a bypass pipe section in the heat exchange tube.
  • the sockets on the adjacent heat exchange fins in the fin group are projected from the upper surface or the lower surface of the heat exchange fin to form an overlap.
  • the fin group includes two or more side by side arrangement, and the heat exchange fins arranged side by side in the adjacent fin group are integrally formed, and the integrated heat exchange fins are arranged in the lateral direction thereof. 12 sockets, arranged in the longitudinal direction 2-20 sockets.
  • the heat exchange fins in the adjacent fin groups are staggered or in the same plane, and all the fin groups constitute a fin heat exchange unit for inserting the heat exchange tubes, and are arranged in the lateral direction of the fin heat exchange unit.
  • the socket is arranged in an inclined manner on the corresponding heat exchange fin, and the center line of the socket and the lateral direction of the heat exchange fin An angle A is formed, and the angle A is 0°-90°.
  • the socket includes two arc-shaped jacks, and a linear retaining slot connecting the two arc-shaped jacks between the two arc-shaped jacks, and two straight pipe sections of the heat exchange tube that are twisted back into the pipe section Insert one of the two arc-shaped jacks one by one.
  • the gaps formed between the adjacent heat exchange fins are equal or unequal, and the planes of the adjacent heat exchange fins which are parallel to each other or adjacent to the heat exchange fins form a cross.
  • heat exchange fins are straight or wave type.
  • the meandering bend of the heat exchange tube is an arc segment.
  • the heat exchange tube removes the bypass pipe section at the fold, and forms an angle B between the planes of the adjacent bypass pipe segments at other places.
  • the outer diameter ⁇ of the heat exchange tube is 6 mm - 12.7 mm
  • the wall thickness d1 is not less than 0.4 mm
  • the thickness d2 of the heat exchange fin is not less than 0.09 mm.
  • the inner wall of the heat exchange tube is a smooth surface or a flow guiding tooth arranged along the length direction of the heat exchange tube.
  • the heat exchange tube is bent and formed by a continuous twisting of a metal tube, and then the formed heat exchange tube is integrally inserted into the fin group as a whole, in the whole heat exchange tube.
  • the heat exchanger with such a structure solves the current problem, that is, there is no damage caused by the need to weld, the heat exchange tube during the welding process, and the heat exchange tube is ensured;
  • a whole heat exchange tube is circulated, there is no impact damage to the heat exchange tube due to the large impact force of the fluid, and the fluid is not caused by the high temperature of the fluid flowing into the heat exchange tube.
  • the leakage of the medium ensures the heat exchange performance of the heat exchange tubes; and there is no problem that the inner wall of the welded pipe joints is uneven, the flow of the fluid medium is hindered, and the performance of the heat exchanger is low.
  • the heat exchange tube is continuously twisted and bent and formed into a whole after folding and the heat exchange tube is inserted into the fin group as a whole.
  • the heat exchanger is simple and convenient to manufacture, and the heat exchanger is improved.
  • the working efficiency, and the production cost of the heat exchanger is reduced, and the utility model is convenient for popularization and use, and the clothes dryer and the washing machine adopting the heat exchanger are effectively protected in the drying function, and the heat exchanger problem does not occur. Frequent repairs and replacements.
  • a washing machine and a clothes dryer comprising the fin heat exchanger, which is formed by inserting a fin by a metal tube after a plurality of continuous twisting and bending and at least one folding to form at least two rows of bypass pipes.
  • the composition of the group enhances the drying function of the washing machine and the dryer.
  • a method for manufacturing a fin heat exchanger for a washing machine or a dryer includes the following steps:
  • the total length of a metal tube and the number of heat exchange fins in the fin group are determined according to the size of the heat exchanger;
  • the second step is to determine the number of twists and turns of the metal tube and the radius R of the bend back;
  • the metal pipe is bent back and bent in the second step and the bending radius, and the twisted return pipe is folded at least once to form at least two rows of the bypass pipe group to obtain Heat exchange tube
  • a plurality of sockets for inserting the heat exchange tubes into the heat exchange fins are processed by each of the heat exchange fins, and the corresponding positions on the heat exchange fins are overlapped after being projected;
  • the heat exchange fins are sequentially arranged on the assembly mold, a gap arrangement is formed between the adjacent heat exchange fins, and the sockets at the same position between the adjacent heat exchange fins on the assembly mold are projected and overlapped to obtain a fin group formed by heat exchange fins;
  • the heat exchange tube obtained in the third step is inserted into the fin group in the fifth step as a whole, and the corresponding ones of the heat exchange tubes are inserted into the corresponding positions on the fin group. After being inserted into position, the twisting and bending section of the bypass pipe in the heat exchange tube is outside the fin group;
  • the heat exchange tube inserted in the fin group is introduced into the fluid to expand the tube, so that a solid combination is formed between the heat exchange tube and the fin group to obtain an integral heat exchanger, and the obtained heat exchanger is obtained.
  • the heat exchanger is removed from the assembly mold, that is, the heat exchanger is completed.
  • the obtained heat exchange tube removes the bypass pipe section at the fold, and the other twisted pipe sections at other places form a bend of 0°-90°.
  • sockets are arranged obliquely or horizontally or vertically on the heat exchange fins.
  • the heat exchange tube in the heat exchanger is inserted into the arranged fin group by continuous bending of a metal tube, and can be used for an evaporator or a condenser, and has the advantages that the whole part is integrated except for the inlet and outlet. There is no solder joint, the safety hazard of leakage is eliminated, the production process is simple, the cost is low, and the heat exchange performance is high.
  • the product of the process structure breaks the traditional concept and application range of the heat exchanger for the washing machine and the dryer. The technical innovation and breakthrough of the equipment products in this industry.
  • FIG. 1 is a schematic structural view of a conventional heat exchanger
  • FIG. 2 is a schematic structural view of a bent portion of a heat exchange tube in a conventional heat exchanger
  • Embodiment 3 is a schematic structural view of Embodiment 1 of a heat exchanger according to the present invention.
  • Figure 4 is a top plan view of Figure 3;
  • Figure 5 is a schematic left side view of Figure 3;
  • Figure 6 is a schematic right side view of Figure 3;
  • FIG. 7 is a schematic structural view of a second embodiment of a heat exchanger according to the present invention.
  • FIG. 7A is a schematic rear view of FIG. 7;
  • Figure 8 is a schematic plan view showing the structure of a single heat exchange fin in the present invention.
  • Figure 9 is a schematic view showing the planar structure of a heat exchange tube formed after a plurality of twists and turns bending in the present invention.
  • Figure 10 is a schematic view showing the shape of the heat exchange tube formed by folding the heat exchange tube of Figure 9;
  • Figure 11 is a schematic left side view of Figure 10;
  • FIG. 12 is a schematic cross-sectional structural view of a first embodiment of a heat exchange tube according to the present invention.
  • Figure 13 is a schematic cross-sectional view showing the second embodiment of the heat exchange tube of the present invention.
  • Figure 14 is a schematic cross-sectional view showing the third embodiment of the heat exchange tube of the present invention.
  • Figure 15 is a schematic cross-sectional view showing the fourth embodiment of the heat exchange tube of the present invention.
  • Figure 16 is a schematic cross-sectional view showing the fifth embodiment of the heat exchange tube of the present invention.
  • Figure 17 is a schematic view showing another structure of a bend portion of a heat exchange tube returning pipe section in the present invention.
  • Figure 18 is a schematic structural view of Embodiment 3 of the heat exchanger of the present invention.
  • Figure 19 is a schematic structural view of a fourth embodiment of a heat exchanger according to the present invention.
  • Embodiment 5 of a heat exchanger is a schematic structural view of Embodiment 5 of a heat exchanger according to the present invention.
  • FIG. 21 is a schematic structural view of Embodiment 6 of a heat exchanger according to the present invention.
  • Figure 22 is a schematic structural view of Embodiment 7 of the heat exchanger of the present invention.
  • Figure 23 is a schematic view showing the structure of an embodiment 8 of the heat exchanger of the present invention.
  • 100 is a fin heat exchanger
  • 101 is a fin group
  • 102 is a heat exchange tube
  • 103 is a bypass tube group
  • 104 is a medium inlet end
  • 105 is a medium discharge end
  • 106 is a heat exchange fin
  • 107 For the gap
  • 108 is the return pipe section
  • 109 is the socket
  • 110 is the arc-shaped jack
  • 111 is the retaining slot
  • 112 is the straight pipe section
  • 113 is the winding bend
  • 114 is the fold
  • 115 is the inner groove
  • 116 For the internal teeth
  • 117 is the first side wall
  • 118 is the second side wall
  • 119 is the bottom wall of the groove
  • 120 is the connecting elbow.
  • a fin heat exchanger 100 for a washing machine and a dryer includes a fin group 101 and a heat exchange tube 102 interposed in the fin group, and the heat exchange tube is bent by a metal tube through a plurality of consecutive twists and turns and then at least One fold is formed to have at least two rows of bypass groups 103 and then inserted into the above-mentioned fin group as a whole; both ends of the heat exchange tube are outside the fin group, one end serves as a medium inlet end 104, and the other end serves as a medium discharge end 105.
  • the metal tube is made of aluminum tube or copper tube with good thermal conductivity. In order to consider the manufacturing cost and the processability, the aluminum tube is preferably used for bending.
  • the fin group is formed by a plurality of heat exchange fins 106, and a gap 107 is formed between adjacent heat exchange fins in each fin group, and a branch pipe section is disposed on each heat exchange fin for the heat exchange tube 108 is inserted into a plurality of sockets 109, each of which is correspondingly inserted into a bypass pipe section in the heat exchange tube.
  • the single heat exchange fins in the fin group in the present embodiment are one-piece in one piece to enhance the heat diffusion capability of the entire heat exchange fin.
  • the heat exchange fins can be made of a metal sheet having a good heat transfer property such as an aluminum sheet or a copper sheet.
  • the sockets on the adjacent heat exchange fins in the fin group overlap with the projection of the light source from the upper surface or the lower surface of the heat exchange fin, so that the smoothness of the heat exchanger tube is ensured, and the second is to ensure
  • the heat exchange tubes installed on each heat exchange fin can be uniform and uniform to ensure the heat exchange performance of the entire heat exchanger.
  • Each of the heat exchange fins is arranged with 2-12 sockets in its lateral direction and 2-20 sockets in its longitudinal direction. Referring to Fig. 8, four sockets are arranged in the lateral direction of the heat exchange fins, and four sockets are arranged in the longitudinal direction. Of course, the number of sockets of the heat exchange fins in the lateral or longitudinal direction thereof can be opened as needed. Meet the requirements of making heat exchangers of different sizes.
  • the socket is arranged on the heat exchange fin in the same direction, and the center line of the socket is
  • the transverse direction of the heat exchange fin forms an angle A, and the angle A is between 0° and 90°.
  • the angle A is 0°
  • the overall shape of the socket is consistent with the lateral direction of the heat exchange fin, that is, the socket is horizontal.
  • the whole of the socket is consistent with the longitudinal direction of the heat exchange fin, that is, the socket is arranged vertically on the heat exchange fin; when the socket is inclined, preferably 50° -70°, such as 50° or 55° or 60° or 65° or 70°, can increase the heat exchange area and reduce the volume of the heat exchanger.
  • each socket in order to ensure that the socket can form a stable combination with the inserted heat exchange tube returning pipe segments, each socket includes two curved jacks 110, and two arc jacks are connected between the two arc jacks.
  • Straight type yielding slot 111 let The width of the slot is smaller than the arc-shaped jack but slightly larger than the outer diameter of the heat exchange tube, and the arc-shaped jack is an arc-shaped jack larger than the central angle of more than 180°; the two straight-line segments 112 of the bypass pipe section in the heat exchange tube are respectively One-to-one insertion is inserted into two arc-shaped jacks.
  • the loop-back bend 113 in the loop-back pipe section is inserted through the let-off slot, and the two straight pipe sections on both sides of one turn-back section are respectively placed in two arc-shaped inserts.
  • the outer diameter of the heat exchange tube is increased by expanding the heat exchange tube to compensate for the straight line.
  • the gap between the pipe section and the arc-shaped insertion hole enables the outer wall of the straight pipe section to form a firm bond with the inner wall of the arc-shaped insertion hole, thereby stably assembling the heat exchange pipe into the fin group.
  • the obliquely arranged sockets are inserted into the ones of the heat exchange tubes one by one, so that the entire heat exchange tubes are obliquely inserted on the fin groups, so that the structure can not only increase the length of the heat exchange tubes, but also increase the heat exchange.
  • the number of bending of the tube makes the medium circulation time longer, prolongs the heat exchange time, makes the heat exchange performance better, and the scope of action becomes wider; in addition, the heat exchange tube is compact but not dense, and the layers are distinct. Very convenient for installation and maintenance.
  • such a structure can reduce the volume of the heat exchanger, greatly reduce the space occupied by the heat exchanger, and the heat exchange tube can be better.
  • the connection with the heat exchange fins is compact and firm; and it facilitates the assembly of the heat exchange tubes and fins, greatly improves the assembly efficiency and product quality, and improves the efficiency of the enterprise.
  • the gaps formed between the adjacent heat exchange fins may be equal or unequal, and the planes of the adjacent heat exchange fins which are parallel to each other or adjacent to the heat exchange fins form an intersection.
  • the gaps between the heat exchange fins are selected equally and the heat exchange fins are kept parallel.
  • adjacent The gap d3 between the heat exchange fins is not less than 2 mm to ensure sufficient heat exchange space between the heat exchange fins and improve the heat exchange capacity of the heat exchanger.
  • the heat exchange fins in this embodiment are straight or wave type, and when the heat exchange surface is obtained, the heat exchange fins can be processed into a wave shape, and the heat exchange fins have a shape relative to the straight fin type heat exchange fins. Larger heat transfer surface to further enhance the heat exchange capacity of the entire heat exchanger.
  • the straight-sheet heat exchange fins are easier to manufacture and produce, reduce the input cost of the production equipment, and improve the processing efficiency of the heat exchange fins. Therefore, the heat exchange fins shown in the drawings of the present embodiment are of a straight type.
  • the meandering bend 113 of the heat exchange tube is an arc-shaped section.
  • the meandering bend of the fold-out portion 114 in the heat-exchange tube is greater than the curvature of the other bend-back bend.
  • the curvature of the winding back bend can also be the same as that of other non-folding bends, depending on the product requirements.
  • the winding pipe section of the heat exchange tube is arranged in the horizontal direction except for the turn-over pipe section, and an angle B is formed between the planes of the adjacent bypass pipe sections at other places, and the angle between the angle A and the angle B is selected, and the heat exchange tube is selected.
  • the single bypass group on both sides of the middle fold appears to be arranged in a wave shape to ensure that the twisted and folded heat exchanger can be smoothly inserted into the corresponding position of the socket; the heat exchange shown in FIG. In the tube, there are three folds, that is, four loopback groups. Of course, the number of the two can be rooted. According to different size of the heat exchanger to determine.
  • the outer diameter ⁇ of the heat exchange tube in this embodiment is 6 mm or 7 mm or 8 mm or 9 mm or 10 mm or 11 mm or 12.7 mm, the wall thickness d1 is not less than 0.4 mm, and the thickness d2 of the heat exchange fin is not less than 0.09 mm.
  • the inner wall of the heat exchange tube is a smooth surface or a guide arranged along the length of the heat exchange tube.
  • the flow tooth; the guide tooth may be linear or spiral arranged on the inner wall of the heat exchange tube.
  • the inner wall of the heat exchange tube is uniformly provided with a plurality of inner grooves 115 recessed toward the inner wall of the heat exchange tube, and inner teeth 116 protruding toward the middle portion of the heat exchange tube are formed between the adjacent inner grooves.
  • the inner groove and the inner tooth extend in the axial direction of the inner wall of the heat exchange tube, and the inner groove is formed by the first side wall 117, the second side wall 118 and the bottom wall 119, and the first side wall 117 and the second side An angle ⁇ is formed between the walls 118, and different inner groove structures can be realized by selecting different angles ⁇ ; as shown in FIG.
  • the shape of the inner groove is a trapezoid shape with a large notch and a small groove bottom; or FIG.
  • the shape of the inner groove is a rectangular shape having the same size as the groove bottom; or as shown in FIG. 14, the inner groove shape is a dovetail shape having a small groove and a large groove bottom.
  • the cross section of the inner groove is curved; and the triangular shape as shown in Fig. 16.
  • the inner grooves of different cross sections constitute different guiding teeth, so as to efficiently guide the flow medium in the heat exchange tube and increase the contact area between the circulating medium and the heat exchange tube, thereby improving the heat transfer efficiency.
  • the guide tooth is used on the inner wall of the heat exchange tube, on the one hand, the weight of the heat exchange tube can be reduced, that is, the weight of the heat exchange tube is reduced, and the deformation is not easy to be performed during the manufacturing process of the bent tube to ensure the quality of the product;
  • the tooth can increase the contact area of the fluid medium in the tube and improve the heat exchange efficiency; in particular, the inner wall of the ordinary heat exchange tube is a smooth structure, and collisions are inevitable during the installation process, so that the tube may form a pit, and the inner wall of the tube member
  • the formation of the convex portion disturbs the flow stability and flow of the fluid in the tube, causes uneven heat exchange area, insufficient heat exchange, and short service life, and these problems can be solved by the guide tooth, and the guide tooth can be made
  • the heat transfer coefficient of the entire heat exchanger is greatly improved.
  • the production is convenient, fast, and the yield is high.
  • it is necessary to ensure that the spliced fins are on the same horizontal surface and seamlessly connected, otherwise the spacing between the fins cannot be ensured, and once the deviation occurs, the re-production may occur, otherwise the heat exchange may be caused.
  • the heat exchange effect of the device is also affected; and the invention completely avoids this situation, greatly reduces the wind resistance between the fins, improves the heat exchange rate and the heat exchange effect, and greatly reduces the useless work and improves the yield.
  • the meandering bend of the heat exchange tube is an arc segment, which ensures smooth flow of the fluid medium in the tube and stable flow rate.
  • the connection between the connecting elbow of the copper tube fin heat exchanger and the heat exchange copper tube is not a smooth connection and there is a solder joint.
  • the surface of the tube is recessed in the phase, and there are many folds, that is, the diameter of the tube.shrinked.
  • the flow rate and flow rate are affected.
  • the original medium flows smoothly in the tube, and the rapid flow is suddenly formed in the elbow, which is very unfavorable for the effective heat exchange, and the heat exchange tube will be Uneven heating and cooling causes the heat exchange tubes to burst and is very unsafe.
  • the curved portion of the winding back solves the problem, and the use is safe and reliable and the heat exchange efficiency is improved.
  • Embodiment 2 of the heat exchanger of the present invention is described:
  • Embodiment 2 differs from Embodiment 1 in that the fin group is composed of two side by side, and the heat exchange fins of the two fin groups may be staggered or may be in the same plane, but the two fin groups
  • the heat exchange fins are independent of each other and are not integral.
  • the two fin sets form a fin heat exchange unit for inserting a bent heat exchange tube; likewise, the lateral direction of the fin heat exchange unit
  • There are 2-12 sockets, and 2-20 sockets are arranged in the longitudinal direction for the heat exchange tube after twisting and folding.
  • the number of fin groups can be set as needed, such as three, four, and so on.
  • the number of rows of the bypass pipe group can be increased, as shown in FIGS. 18 and 19: a heat exchanger having six rows of bypass pipes; as shown in FIG. 20: having eight rows of bypass pipes
  • the heat exchanger of the group of course, the increase in the number of the return pipe group can be increased according to the size of the different assembly space; at the same time, the number of columns of the bypass pipe group can be increased on the basis of the second embodiment of the heat exchanger, such as Figure 21 shows a six-row heat exchanger consisting of three fin sets (two rows of bypass groups in each fin set); as shown in Figure 22, two fin sets (each fin set) There are three rows of heat exchangers in which three rows of helium return pipes are formed, and eight columns of heat exchangers composed of two fin groups (four rows of bypass pipes in each fin group) as shown in FIG.
  • the fin group when the number of rows of the loopback pipe group is not more than 6, the fin group preferably adopts a monolithic structure; when the number of rows of the loopback pipe group is greater than 6, two or more fin groups may be selected.
  • a washing machine and a clothes dryer include the fin heat exchanger, which has at least two columns formed by a metal pipe after a plurality of continuous twisting and bending and then at least one folding. After the return pipe group is inserted into the fin group as a whole, the drying function of the washing machine and the dryer is improved.
  • the fin heat exchanger here can be realized by any of the above embodiments, and the fin heat exchanger can directly replace the heat exchange part in the current washing machine and the dryer, and the space is reduced, and The heat transfer performance is greatly improved.
  • a method for manufacturing a fin heat exchanger for a washing machine or a dryer includes the following steps:
  • the first step is to determine the total length of a metal tube and the number of heat exchange fins in the fin group according to the size of the heat exchanger; here, the heat exchange tube can be fabricated by using only one aluminum tube, and the wing
  • the production of the film has also been changed from the original two stitching to the current one-piece integral, which not only saves a lot of cost, but also prevents the fin from being deformed, resulting in a reduction in the heat exchange effect of the fin, and at the same time ensuring the heat exchange tube.
  • the air tightness and the firmness of the heat exchanger structure are examples of the heat exchanger structure.
  • the number of times of bending N 1 , N 2 , N 3 and the bending radii R 1 , R 2 , R 3 of the first bypass pipe group 121, the second bypass pipe group 122 and the third bypass pipe group 123 are determined.
  • the bending wheel with the radius R 1 , R 2 , and R 3 is selected; this can quickly and accurately bend the aluminum tube, thereby forming the heat exchange tube, saving time and greatly improving work efficiency.
  • the bending wheel of R 1 is manually bent at the bending point, and the first winding pipe group is formed after bending N 1 times, and then the bending wheel with the diameter R 2 is replaced by N 2 times to form a second roundabout.
  • the bending wheel of the diameter R 3 is bent N 3 times to form a third loopback group, and then the first loopback group middle, the second loopback group, and the third turnback plugging portion are turned over. Folding, the heat exchange tube as shown in Fig.
  • the process steps are clear, the higher production requirements can be achieved, the yield and quality of the product can be improved, and the yield rate can be improved; the heat exchange tube is removed during the twisting and bending process of the heat exchange tube
  • the loopback section of the fold is bent at 0°-90° between adjacent loopback sections at other locations.
  • the R 2 or the meandering bends R 1 , R 3 of the folds may be a whole R of a circular arc segment (as shown in FIG. 9 ), or may be two arc segments R 10 . Formed in connection with the intermediate straight section 126 (as shown in Figure 17). According to different product needs, choose to use.
  • a plurality of sockets for inserting the heat exchange tubes into the heat exchange fins are processed by each of the heat exchange fins, and the corresponding positions of the heat transfer fins are overlapped after projection; the sockets are inclined Arranged on the heat exchange fin; the socket includes two arcuate jacks, and a linear retaining slot that connects the two arcuate jacks between the two arcuate jacks.
  • the center line of the socket forms an angle A with the lateral direction of the heat exchange fin, and the angle A is between 0° and 90°. When the angle A is 0°, the overall shape of the socket is consistent with the lateral direction of the heat exchange fin.
  • the socket is arranged horizontally on the heat exchange fin; when the angle A is 90°, the whole of the socket is consistent with the longitudinal direction of the heat exchange fin, that is, the socket is arranged vertically on the heat exchange fin;
  • 50°-70° such as 50° or 55° or 60° or 65° or 70°, can increase the heat exchange area and reduce The volume of the heat exchanger. Select settings as needed.
  • the bending angle between the loopback sections is preferably the same as the angle of the socket.
  • the heat exchange fins are sequentially arranged on the assembly mold, a gap arrangement is formed between the adjacent heat exchange fins, and the sockets at the same position between the adjacent heat exchange fins on the assembly mold are projected and overlapped to obtain a fin group formed by heat exchange fins;
  • the heat exchange tube obtained in the third step is inserted into the fin group in the fifth step as a whole, and the corresponding ones of the heat exchange tubes are inserted into the corresponding positions on the fin group.
  • the twisting and bending section of the bypass pipe in the heat exchange tube is outside the fin group; when the plug is inserted, the twisting and bending portion in the twisting pipe is inserted through the letting slot, and two sides of one turnback portion Straight pipe segments are inserted into the two arcuate jacks.
  • the fin group here may be formed by one fin group or may be formed by two or more fin groups.
  • the outer wall of the heat exchange tube forms an interference fit with the inner hole of the socket, and the heat exchange tube and the fin group form a firm joint to obtain a monolithic heat exchanger, and the obtained heat exchanger is assembled from the mold.
  • a copper tube is welded on both ends of the heat exchange tube, and the other end of the copper tube is sealed with a sealing sleeve, and a heat shrinkable tube is formed at a welded portion of the copper tube and the heat exchange tube to form a protective sleeve.
  • the heat transfer area of a single system of the structural heat exchanger shown in Figure 1 can be more than 10 square meters, and the heat transfer coefficient can reach K ⁇ 1000 W / m 2 ° C, while the heat transfer of the single system of the heat exchanger of the present invention
  • the area can be more than 14 square meters, the heat transfer coefficient can reach K ⁇ 3000W / m2 ° C, the scope of action is significantly larger, and the heat transfer effect is obvious.

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Abstract

一种洗衣机、干衣机用翅片换热器及其制作方法,其中,翅片换热器(100)包括翅片组(101),以及穿插于翅片组(101)中的换热管(102),换热管(102)由一根金属管经过多次连续迂回弯折再经过至少一次翻折形成具有至少两列迂回管组后作为整体插入翅片组中。该换热器不会出现因为需要焊接而对换热管造成的破坏,保证换热管的整体;当换热流体在一根整体的换热管中流通时,不会出现因为流体冲击力较大,而造成换热管的冲击损伤,且不会因为通入换热管中流体温度较高,而造成的流体介质的泄漏,保证换热管的换热性能且也不会出现因为焊接管道连接端之间内壁的不平整,造成流体介质流动的阻碍,而导致的换热器性能低下的问题。

Description

洗衣机、干衣机用翅片换热器及其制作方法 技术领域
本发明涉及换热器技术领域,具体涉及一种洗衣机、干衣机用翅片换热器及其制作方法。
背景技术
换热器是将热流体的部分热量传递给冷流体的设备,又称热交换器。换热器在化工、石油、动力、食品及其它许多工业生产中占有重要地位,其在化工生产中换热器可作为加热器、冷却器、冷凝器、蒸发器和再沸器等,而在日常生活中所用的如冰箱、洗衣机、干洗机和空调等设备也使用换热器。常规用于洗衣机及干衣机的换热器主要是平行流形式或铜管翅片换热器,虽然翅片式换热器在结构和制作工艺上很成熟,但还是存在一些细节上的缺陷。
常用的平行流形式换热器如图1所示,其包括平行排列的方管121,方管之间布置换热片122,方管中通入换热介质,并通过换热片的扩散进行换热,这样的换热结构换热效率差,且占用空间大。
铜管翅片换热器如图2所示,其包括多根换热铜管123以及多个翅片组124,每个翅片组中分别穿插换热铜管,换热铜管之间通过连接弯管120进行连通,换热铜管的两端先进行扩口125,供连接弯管插入,然后在采用焊接方式将换热铜管及连接弯管形成一体,这样的方式一是换热铜管内壁与连接弯管内壁之间无法保证平滑,二是在换热铜管与连接弯管处产生焊点。这种做法比较常见,但是投入成本较大,工序复杂,换热器气密性较差,容易造成泄漏,而且管内介质的流通会受影响,最终导致换热器的换热效果不够理想。
如公开号为CN204830968U,名称为“一种内含U型换热管的翅片式热交换器”的实用新型,该翅片式热交换器中的U型换热管的两个端口之间通过弯头连接,所述弯头与所述换热管通过焊接成为一体,也就说该换热管使用了焊接的方式将多个管件进行连接,由于换热管与弯头之间采用焊接方式进行连接,管与管之间的连通处产生焊点。
另外,如公开号CN202969102U,专利名称为一种全自动洗衣机中的干衣用冷凝器,包括若干个自上而下平行设置的横截面为扁平状矩形管道、设置在相邻管道间以及上、下管道外壁上的翅片,由它们组成用于热交换的金属芯体,所述的管道由一片单复合铝合金材料折弯经钎焊连接构成;所述金属芯体两端各连接有一塑料盖体,使其整体构成抽屉式结构;塑料盖体上开有与管道对接的扁平状矩形窗口,塑料盖体的周边设置有橡胶片。根据其描述,管道是由一片复合铝合金材料折弯经钎焊连接构成,同样,作为介质流通的管道,也需要采用焊接方式制作,即在管道上产生焊点。
无论是公开号CN204830968U公开的翅片式热交换器,还是公开号CN202969102U公开的干衣冷凝器,两者在介质流通的管道制作上都具有焊接点;而采用焊接进行连通管道还是制作管道,同样存在如下缺陷:
一是为了获得较好的换热性能,流体经过的管道自身厚度较薄,在焊接时,焊接产生的高温容易造成对换热管的破坏,焊接难度大,且焊接处的质量难以保证。
二是由于需要采用焊接,当换热器中介质流通时,流体产生的冲击力以及当通入的介质温度较高时,容易造成焊点处的脱落,且在长时间使用后,更会加重焊点处的脱落,导致焊接处产生泄漏,影响换热器的换热性能,最终也就导致换热器无法使用,失去换热功能,对企业和使用换热器的设备造成无法挽回的损失。
三是由于公开号CN204830968U中管连接处一周均需要焊接,且公开号CN202969102U管道是由一片复合铝合金材料折弯经钎焊连接。由于换热器的本身体积较小,焊接时难度较大,且需要较长时间,导致换热器/冷凝器的制作效率低,增加了企业的加工制作成本。
发明内容
针对上述技术问题,本发明的目的是提供一种克服现有换热管道中存在焊点并由于存在焊点所导致的换热器泄漏、换热性能不稳定且使用寿命短问题的洗衣机、干衣机用翅片换热器及其制作方法。
实现本发明的技术方案如下:
洗衣机、干衣机用翅片换热器,包括翅片组,以及穿插于翅片组中的换热管,所述换热管由一根金属管经过多次连续迂回弯折再经过至少一次翻折形成具有至少两列迂回管组后作为整体插入上述翅片组中;换热管的两端处于翅片组的外部,一端用作介质进入端,另一端用作介质排出端;金属管为铝管或铜管。
进一步地,翅片组由多个换热翅片排列而成,为了获得翅片之间产生换热空间,翅片组中相邻换热翅片之间形成间隙,为了使换热管与翅片组之间形成牢固的结合且合理分布换热管与翅片组的换热空间,在每个换热翅片上开设有供上述换热管中迂回管段插入的多个插口,每一个插口对应插入换热管中的一个迂回管段。
进一步地,为了便于组装以及翅片组上获得均匀的换热空间,翅片组中相邻换热翅片上的插口从换热翅片的上表面或下表面投影后形成重叠。
进一步地,翅片组包括并排排列的两个或两个以上,相邻翅片组中并排的换热翅片为一体式成型,构成的一体式换热翅片在其横向方向布置有2—12个插口,在其纵向方向布置有 2—20个插口。
进一步地,相邻翅片组中的换热翅片错开布置或处于同一平面内,所有翅片组构成一个翅片换热单元供上述换热管插入,在翅片换热单元的横向方向布置有2—12个插口,纵向方向布置有2—20个插口。
进一步地,为了在换热翅片获得更多的换热面积且换热器体积较小,插口呈倾斜方式布置在对应的换热翅片上,插口的中心线与换热翅片的横向之间形成夹角A,夹角A为0°—90°。
进一步地,所述插口包括两个弧形插孔,以及处于两个弧形插孔之间连通两个弧形插孔的直线型让位槽口,换热管中迂回管段的两个直线管段分别一一对应插入两个弧形插孔中。
进一步地,相邻换热翅片之间形成的间隙相等或不等,相邻换热翅片之间相互平行或相邻换热翅片延伸出的平面形成交叉。
进一步地,所述换热翅片为直片式或波浪式。
进一步地,所述换热管的迂回弯折处为弧形段。
进一步地,所述换热管中除去翻折处的迂回管段,其他处的相邻迂回管段所在平面之间形成夹角B。
进一步地,所述换热管的外径φ为6mm—12.7mm,壁厚d1不小于0.4mm,换热翅片的厚度d2不小于0.09mm。
进一步地,所述换热管内壁为光滑面或者为沿着换热管的长度方向布置的导流齿。
采用了上述技术方案,换热管由一根金属管通过连续迂回弯折后并翻折成型,再将成型后的换热管作为整体一并装插到翅片组中,在整个换热管上无焊点;采用这样结构的换热器解决了目前的问题,即不会出现因为需要焊接,在焊接过程中对换热管造成的破坏,保证换热管的整体;当换热流体在一根整体的换热管中流通时,不会出现因为流体冲击力较大,而造成对换热管的冲击损伤,且不会因为通入换热管中流体温度较高,而造成的流体介质的泄漏,保证换热管的换热性能;并且也不会出现因为焊接管道连接端之间的内壁不平整,造成流体介质流动的阻碍,以及导致的换热器性能低下的问题。
由于不需要采用焊接,将换热管连续迂回弯折且翻折后形成整体并将换热管作为整体插入翅片组中,本换热器在制作上简单、方便,提升了制作换热器的工作效率,且降低了换热器的制作成本,便于推广使用,且采用本换热器的干衣机、洗衣机在干衣功能上得到了有效的保障,不会出现因换热器问题而造成的频繁维修、更换。
一种洗衣机、干衣机,包括所述的翅片换热器,由一根金属管经过多次连续迂回弯折再经过至少一次翻折形成具有至少两列迂回管组后作为整体插入翅片组中构成,提升了洗衣机、干衣机的干衣功能。
洗衣机、干衣机用翅片换热器制作方法,包括以下步骤:
第一步,根据换热器的大小来确定一根金属管的总长度以及翅片组中换热翅片的片数;
第二步,确定金属管的迂回弯折次数,以及迂回弯折处的半径R;
第三步,将金属管以第二步中弯折次数及弯折半径进行迂回弯折,并将迂回弯折后的迂回管进行至少一次的翻折形成至少两列的迂回管组,以获得换热管;
第四步,采用冲压设备在每一个换热翅片加工出供上述换热管迂回管装插的多个插口,每个换热翅片上对应位置的插口在投影后形成重叠;
第五步,将换热翅片依次排列于组装模具上,相邻换热翅片之间形成间隙布置,且组装模具上相邻换热翅片之间同位置的插口投影后重叠,以获得由换热翅片排列而成的翅片组;
第六步,将第三步中获得的换热管作为整体插入第五步中翅片组中,换热管中的迂回管一一对应的装插入于翅片组上对应位置的插口中,装插到位后,换热管中迂回管的迂回弯折段处于翅片组外部;
第七步,对装插于翅片组中的换热管通入流体进行胀管,使换热管与翅片组之间形成牢固结合,以获得整体式的换热器,将获得的换热器从组装模具上取下,即完成换热器的制作过程。
进一步地,在第三步中,所获得的换热管除去翻折处的迂回管段,其他处的相邻迂回管段之间形成0°-90°的弯折。
进一步地,所述插口呈倾斜或水平或竖直布置在换热翅片上。
本换热器中的换热管由一根金属管通过连续弯制成型后插入排列的翅片组中,可用于蒸发器或冷凝器,其优点为除进出口外,其余部分为整体式,没有焊点,消除了泄漏的安全隐患,生产工艺简单,成本低廉,具有高效的换热性能,该工艺结构的产品打破了洗衣机、干衣机用换热器的传统理念及应用范畴,属于该行业设备产品在技术上的创新与突破,该换热器被应用于洗衣机、干衣机领域时,其产品设计相比常规具有换热性能高的特征,及相当的技术难度,主要体现为多排管的一体式整体弯管及胀管的组装工艺,该制作工艺突破了常规工艺的技术能力,突显了该发明技术工艺的先进性。
附图说明
图1为常规换热器的结构示意图;
图2为常规换热器中换热管折弯段的结构示意图;
图3为本发明换热器的实施方式一结构示意图;
图4为图3的俯视结构示意图;
图5为图3的左视结构示意图;
图6为图3的右视结构示意图;
图7为本发明换热器的实施方式二结构示意图;
图7A为图7的后视结构示意图;
图8为本发明中单个换热翅片的平面结构示意图;
图9为本发明中经过多次迂回弯折后形成的换热管平面结构示意图;
图10为图9中的换热管经过翻折后成形的换热管形状示意图;
图11为图10的左视结构示意图;
图12为本发明中换热管实施方式一的截面结构示意图;
图13为本发明中换热管实施方式二的截面结构示意图;
图14为本发明中换热管实施方式三的截面结构示意图;
图15为本发明中换热管实施方式四的截面结构示意图;
图16为本发明中换热管实施方式五的截面结构示意图;
图17为本发明中换热管迂回管段弯折处的另一结构示意图;
图18为本发明换热器实施方式三的结构示意图;
图19为本发明换热器实施方式四的结构示意图;
图20为本发明换热器实施方式五的结构示意图;
图21为本发明换热器实施方式六的结构示意图;
图22为本发明换热器实施方式七的结构示意图;
图23为本发明换热器实施方式八的结构示意图。
附图中,100为翅片换热器,101为翅片组,102为换热管,103为迂回管组,104为介质进入端,105为介质排出端,106为换热翅片,107为间隙,108为迂回管段,109为插口,110为弧形插孔,111为让位槽口,112为直线管段,113为迂回弯折处,114为翻折处,115为内槽,116为内齿,117为第一侧壁,118为第二侧壁,119为槽底壁,120为连接弯管。
具体实施方式
为使本发明实施例的目的、技术方案和优点更加清楚,下面将结合本发明实施例的附图,对本发明实施例的技术方案进行清楚、完整地描述。显然,所描述的实施例是本发明的一部分实施例,而不是全部的实施例。基于所描述的本发明的实施例,本领域普通技术人员在无需创造性劳动的前提下所获得的所有其他实施例,都属于本发明保护的范围。
参见图3-6以及图8—11,对本发明换热器的实施方式一进行说明:
洗衣机、干衣机用翅片换热器100,包括翅片组101,以及穿插于翅片组中的换热管102,换热管由一根金属管经过多次连续迂回弯折再经过至少一次翻折形成具有至少两列迂回管组103后作为整体插入上述翅片组中;换热管的两端处于翅片组的外部,一端用作介质进入端104,另一端用作介质排出端105。其中,金属管选用导热性能好的铝管或铜管,为了考虑制作成本及可加工性,以优先选用铝管进行弯制。
翅片组由多个换热翅片106排列而成,每个翅片组中相邻换热翅片之间形成间隙107,在每个换热翅片上开设有供上述换热管中迂回管段108插入的多个插口109,每一个插口对应插入换热管中的一个迂回管段。这里需要说明的是,本实施方式中翅片组中的单个换热翅片为整体一片式,以提升整个换热翅片的热量扩散能力。换热翅片可以采用铝片或铜片等等热传递性能好的金属片材制成。
翅片组中相邻换热翅片上的插口从换热翅片的上表面或下表面等距离同光源的投影后形成重叠,这样一是为了保证换热管装插的顺畅性,二是保证每个换热翅片上装插的换热管能够均匀一致,以保证整个换热器的热交换性能。
每个换热翅片在其横向方向布置有2—12个插口,在其纵向方向布置有2—20个插口。参见图8,在换热翅片的横向方向布置有4个插口,在纵向方向布置有4个插口,当然,换热翅片在其横向或纵向上的插口数量可以根据需要来进行开设,以满足制作不同尺寸的换热器要求。为了增加换热翅片上供换热管装插的位置,以提升换热面积以及减少整个换热器的占用空间,插口呈同一方向上的倾斜方式布置在换热翅片上,插口的中心线与换热翅片的横向方向形成夹角A,夹角A为0°—90°之间,当夹角A为0°时,插口的整体与换热翅片的横向一致,即插口呈水平方式布置在换热翅片上;当夹角A为90°时,插口的整体与换热翅片的纵向一致,即插口呈竖直方式布置在换热翅片上;在插口倾斜布置时,优选50°—70°,如50°或55°或60°或65°或70°均可以增加换热面积、减少换热器的体积。
其中,为了能够保证插口能够对插入的换热管迂回管段形成稳定的结合,每个插口包括两个弧形插孔110,以及处于两个弧形插孔之间连通两个弧形插孔的直线型让位槽口111,让 位槽口的宽度小于弧形插孔但略大于换热管的外径,弧形插孔为大于圆心角大于180°的圆弧插孔;换热管中迂回管段的两个直线管段112分别一一对应插入两个弧形插孔中,装插时,迂回管段中的迂回弯折处113通过让位槽口插入,而一个迂回部两侧的两个直线管段分别处于两个弧形插孔中,装插时,直线管段的外壁与弧形插孔内壁之间存在装配间隙,当装配到位后,通过对换热管进行胀管,使换热管的外径增大,以弥补直线管段与弧形插孔之间的间隙,使直线管段外壁与弧形插孔内壁形成牢固的结合,从而得以将换热管稳定的装配到翅片组中。采用倾斜布置的插口及将换热管上的迂回管段一一对应插入其中,这样整个换热管就是斜插在翅片组上,如此结构不仅能够增加换热管的长度,即增加了换热管的弯折次数,使得管内介质流通时间较长,延长热量交换时间,使换热性能变得更佳,作用范围变得更广;另外,换热管结构紧凑但不密集,层次分明,在安装和维修方面非常的方便。通过同一插口中的两个弧形插孔对应与同一迂回管段中的两个直线管段,这样的结构,可以缩小换热器体积,大大减少换热器的占用空间,同时换热管可以更好的与换热翅片连接,结构紧凑、牢固;而且便于换热管和翅片的装配,极大的提高的装配效率和产品质量,提高企业的效益。
本实施例中,相邻换热翅片之间形成的间隙可以相等也可以不等,相邻换热翅片之间相互平行或相邻换热翅片延伸出的平面形成交叉。而为了使换热器具有更好的换热性能,换热翅片之间的间隙选择相等且换热翅片之间保持平行,在选择相邻换热翅片之间间隙相等时,相邻换热翅片之间的间隙d3不小于2mm,以保证换热翅片之间具有充足的换热空间,提升换热器的热交换能力。
本实施例中的换热翅片为直片式或波浪式,当为了获得更大的换热面时,可以将换热翅片加工成波浪状,相对于直片式的换热翅片具有较大的换热面,以进一步提升整个换热器的热交换能力。而直片式的换热翅片更便于制作和生产,降低企业生产设备的投入成本,以及提升换热翅片的加工效率。因而,本实施例附图中示出的换热翅片选用直片式。
换热管的迂回弯折处113为弧形段,为了便于组装,换热管中翻折处114的迂回弯折处弧度大于其他处迂回弯折处的弧度。当然,翻折处的迂回弯折处弧度也可以与其他非翻折处的迂回弯折处相同,具体根据不同的产品需求来设定。
参见图10,换热管中除去翻折处的迂回管段水平方向布置,其他处的相邻迂回管段所在平面之间形成夹角B,夹角A与夹角B的角度选择一致,换热管中翻折处两侧的单个迂回管组看上去呈波浪状布置,以保证迂回弯折且翻折的换热器能够顺畅的插入到对应位置的插口中;在图10中示出的换热管中,具有三个翻折处,即四个迂回管组,当然两者的数量可以根 据不同体积大小的换热器来确定。
本实施例中的换热管外径φ为6mm或7mm或8mm或9mm或10mm或11mm或12.7mm,壁厚d1不小于0.4mm,换热翅片的厚度d2不小于0.09mm。
为了对换热管内的流体介质形成高效的导流以及更好的将流体介质中的能量经过换热管传递出,换热管内壁为光滑面或者为沿着换热管的长度方向布置的导流齿;导流齿可为直线型或螺旋状的布置在换热管内壁。导流齿的实现形式有如下几种方式。
如图12、13、14所示,换热管内壁上均布有多个向换热管内壁凹陷的内槽115,相邻内槽之间形成向换热管内中部隆起的内齿116,该内槽与内齿在换热管的内壁作轴线方向进行延伸,内槽由第一侧壁117、第二侧壁118及槽底壁119围合而成,第一侧壁117、第二侧壁118之间形成夹角α,通过选择不同的夹角α,可以实现不同的内槽结构;如图12所示,内槽形状为槽口大、槽底小的梯形状;或如图13所示,内槽形状为槽口与槽底一样大小的矩形状;或如图14所示,内槽形状为槽口小、槽底大的燕尾形状。或者可以如图15示出,内槽的横截面为弧形;以及如图16示出的三角形状。这些不同截面的内槽构成不同的导流齿,以对换热管内的流通介质进行高效导流以及增加流通介质与换热管之间的接触面积,提升热传递效率。在换热管内壁采用导流齿,一方面可以减轻换热管的重量,即减轻了换热管的重量,在弯管制作过程中,不易变形,保证产品的质量;另一方面,导流齿可以增加管内流体介质的接触面积,提高换热效率;特别的,普通的换热管内壁为光滑的结构,在安装过程中难免会发生碰撞,这样管件可能形成凹坑,而在管件内壁就形成凸起部,扰乱了管内流体的流动稳定性和流量,造成换热面积不均匀,换热量不足,使用寿命短等问题,而通过导流齿则可以解决这些问题,导流齿得以使整个换热器的换热系数大大提升。
本发明的换热器相对于目前铜管翅片换热器具有以下优势:
1、工序减少,产品制作效率高。翅片组与换热管装配时间大大节省,投入人工且成本少,在单位时间、单位成本内可以制作更多的产品。
2、原料投入较少,成本降低。原有的拼接在一起的翅片间的缝隙需要通过焊接来密封,而焊接会导致翅片的重量变大,而且还会对翅片本身造成损伤,换热效果变差;现将原来的2个翅片组组合改成现在的一体成型,这样翅片之间就没有缝隙,而且在尺寸一致的情况下,一个整体的翅片面积比2个翅片的组合面积要大,吸热散热效果好,同时避免了翅片在安装过程中发生变形,导致翅片间的间距变小或变大,最终导致换热器整体换热效果差的问题。
3、换热管只需一根,不再需要另外增加连接弯管120。铜管翅片换热器中采用两个换热 器拼接后将两个管口通过连接弯管焊接起来,从而实现连通,这种方式就需要准备两根换热管,相对于本发明成本必然高,而弯管焊接上去之前需要对换热管的气密性进行检测,而之后还需要再次进行密封检测,不仅制作要求高,而且工序上还复杂;本发明只用一根换热管,制作成型简单,快速,无焊接就不会造成换热管上有焊点缺陷,也不会出现换热管泄漏的问题,工作效率大大提高,换热管的气密性只需检测一次即可,大大节省了时间,人力物力。
4、制作方便、快速,成品率高。现有的铜管翅片换热器中需要保证拼接的翅片在同一水平面上,以及无缝连接,否则无法保证翅片之间的间距,一旦出现偏差就要重新制作,不然会导致换热器的换热效果也会受影响;而本发明完全避开此种情况,大大减小了翅片间的风阻,提高了热交换率和热交换效果,同时大大减少无用功,提高成品率。
5、本发明中换热管的迂回弯折处为弧形段,保证管内流体介质流通顺畅,流速稳定。而目前铜管翅片换热器的连接弯管与换热铜管之间的连接并非是平滑的连接且存在焊点,该段管道表面是相内凹陷的,而且有很多褶皱,即管径缩小了。管内流体介质流过该弯管处时流量和流速均受到影响,原先介质在管内平稳流动,而在此弯管内会突然形成激流,非常不利于换热的有效进行,而且换热管会因为冷热不均导致换热管炸裂,非常不安全。而本发明中迂回弯折处为弧形段解决了该问题,使用安全可靠且提升换热效率。
参见图7和图7A对本发明换热器的实施方式二进行说明:
实施方式二与实施方式一的区别之处在于,翅片组由两个并排构成,两个翅片组中的换热翅片可以错开布置,也可以处于同一平面内,但两个翅片组中的换热翅片相互独立并不是一个整体,两个翅片组构成一个翅片换热单元,以供一根弯制的换热管插入;同样,在翅片换热单元的横向方向布置有2—12个插口,纵向方向布置有2—20个插口,以供迂回弯折再翻折后的换热管插入。当然翅片组的数量可以根据需要来设置,比如三个、四个等等。
在换热器的实施方式一基础上,可以增加迂回管组的列数,如图18、19所示:具有六列迂回管组的换热器;如图20所示:具有八列迂回管组的换热器;当然这里迂回管组的数量增加可以根据不同装配空间的大小来进行选择增加;同时,也可以在换热器的实施方式二基础上作出迂回管组的列数增加,如图21所示由三个翅片组(每个翅片组中有两列迂回管组)构成的六列换热器);如图22所示由两个翅片组(每个翅片组中有三列迂回管组)构成的六列换热器,以及如图23所示由两个翅片组(每个翅片组中有四列迂回管组)构成的八列换热器。为了便于换热器的制作,当迂回管组的列数不大于6时,翅片组优先选用整体式结构;当迂回管组列数大于6时,可以选用两个以上的翅片组。
参见图3-6、8-11一种洗衣机、干衣机,包括所述的翅片换热器,由一根金属管经过多次连续迂回弯折再经过至少一次翻折形成具有至少两列迂回管组后作为整体插入翅片组中构成,提升了洗衣机、干衣机的干衣功能。这里的翅片换热器可以采用上面实施方式中任一款结构来实现,翅片换热器可以直接替换目前洗衣机、干衣机中的换热部分,且在空间上有所减小,而换热性能上得以大大提升。
洗衣机、干衣机用翅片换热器制作方法,包括以下步骤:
第一步,根据换热器的大小来确定一根金属管的总长度以及翅片组中换热翅片的片数;这里换热管的制作只需采用一根铝管即可,而翅片的制作也由原来的2个拼接改成现在的一体成型的整体,不仅能在成本上节约很多,而且在能够防止翅片变形,导致翅片的换热效果降低,同时能够保证换热管的气密性,以及换热器结构的牢固性。
第二步,确定第一迂回管组121、第二迂回管组122和第三迂回管组123的折弯次数N1、N2、N3和折弯半径R1、R2、R3,根据折弯半径选取半径为R1、R2、R3的折弯轮;这样可以快速准确的将铝管折弯,从而使换热管成型,节约时间,大大提高了工作效率。
第三步,确定折弯次数后将铝制直管均匀分为S=(N1+N2+N3+1)段,每段铝管上取一个折弯点,再将铝管通过半径为R1的折弯轮在折弯点出进行手工折弯,折弯N1次后形成第一迂回管组,然后更换直径为R2的折弯轮折弯N2次后形成第二迂回管组,最后再次更换直径为R3的折弯轮折弯N3次后形成第三迂回管组,再以第一迂回管组中部、第二迂回管组、第三迂回装插部进行翻折,则获得如图10的换热管;这样工序步骤清晰,能够达到较高制作要求,能够提高产品的产量和质量,提高成品率;换热管的迂回弯折过程中,换热管除去翻折处的迂回管段,其他处的相邻迂回管段之间进行0°-90°的弯折。在手工弯管时,对折处的R2或迂回弯折处R1、R3可以为一个圆弧形段的整R(如图9所示),也可以是由两个弧形段R10与中间直段126连接形成(如图17所示)。具体根据不同的产品需要进行选择使用。
第四步,采用冲压设备在每一个换热翅片加工出供上述换热管迂回管装插的多个插口,每个换热翅片上对应位置的插口在投影后形成重叠;插口呈倾斜状布置在换热翅片上;插口包括两个弧形插孔,以及处于两个弧形插孔之间连通两个弧形插孔的直线型让位槽口。插口的中心线与换热翅片的横向方向形成夹角A,夹角A为0°—90°之间,当夹角A为0°时,插口的整体与换热翅片的横向一致,即插口呈水平方式布置在换热翅片上;当夹角A为90°时,插口的整体与换热翅片的纵向一致,即插口呈竖直方式布置在换热翅片上;在插口倾斜布置时,优选50°—70°,如50°或55°或60°或65°或70°均可以增加换热面积、减少 换热器的体积。具体根据需要进行选择设置。迂回管段之间的弯折角度与插口的角度一致为佳。
第五步,将换热翅片依次排列于组装模具上,相邻换热翅片之间形成间隙布置,且组装模具上相邻换热翅片之间同位置的插口投影后重叠,以获得由换热翅片排列而成的翅片组;
第六步,将第三步中获得的换热管作为整体插入第五步中翅片组中,换热管中的迂回管一一对应的装插入于翅片组上对应位置的插口中,装插到位后,换热管中迂回管的迂回弯折段处于翅片组外部;装插时,迂回管中的迂回弯折处通过让位槽口插入,而一个迂回部两侧的两个直线管段分别对着两个弧形插孔进行插入。这里的翅片组可以由一个翅片组形成,也可以由两个及以上的翅片组排列形成。
第七步,使换热管外壁与插口内孔形成过盈配合,换热管与翅片组之间形成牢固结合,以获得整体式的换热器,将获得的换热器从组装模具上取下,即完成换热器的制作过程。在换热管的两端焊接上铜管,铜管的另一端用密封套密封,在铜管和换热管的焊接处套烫热缩管,形成保护套。
经过测试,图1所示结构换热器的单个系统的换热面积可以做到10个平方以上,传热系数可以达到K≥1000W/㎡℃,而本发明换热器的单个系统的换热面积可以做到14个平方以上,传热系数可以达到K≥3000W/㎡℃,作用范围明显变大,换热效果明显。

Claims (16)

  1. 洗衣机、干衣机用翅片换热器,包括翅片组,以及穿插于翅片组中的换热管,其特征在于,所述换热管由一根金属管经过多次连续迂回弯折再经过至少一次翻折形成具有至少两列迂回管组后作为整体插入上述翅片组中;换热管的两端处于翅片组的外部,一端用作介质进入端,另一端用作介质排出端;金属管为铝管或铜管。
  2. 根据权利要求1所述的洗衣机、干衣机用翅片换热器,其特征在于,所述翅片组由多个换热翅片排列而成,翅片组中相邻换热翅片之间形成间隙,在每个换热翅片上开设有供上述换热管中迂回管段插入的多个插口,每一个插口对应插入换热管中的一个迂回管段。
  3. 根据权利要求2所述的洗衣机、干衣机用翅片换热器,其特征在于,所述翅片组中相邻换热翅片上的插口从换热翅片的上表面或下表面投影后形成重叠。
  4. 根据权利要求2所述的洗衣机、干衣机用翅片换热器,其特征在于,所述翅片组包括并排排列的两个或两个以上,相邻翅片组中并排的换热翅片为一体式成型,构成的一体式换热翅片在其横向方向布置有2—12个插口,在其纵向方向布置有2—20个插口。
  5. 根据权利要求4所述的洗衣机、干衣机用翅片换热器,其特征在于,相邻翅片组中的换热翅片错开布置或处于同一平面内,所有翅片组构成一个翅片换热单元供上述换热管插入,在翅片换热单元的横向方向布置有2—12个插口,纵向方向布置有2—20个插口。
  6. 根据权利要求4或5所述的洗衣机、干衣机用翅片换热器,其特征在于,所述插口呈倾斜方式布置在对应的换热翅片上,插口的中心线与换热翅片的横向之间形成夹角A,夹角A为0°—90°。
  7. 根据权利要求6所述的洗衣机、干衣机用翅片换热器,其特征在于,所述插口包括两个弧形插孔,以及处于两个弧形插孔之间连通两个弧形插孔的直线型让位槽口,换热管中迂回管段的两个直线管段分别一一对应插入两个弧形插孔中。
  8. 根据权利要求4或5所述的洗衣机、干衣机用翅片换热器,其特征在于,相邻换热翅片之间形成的间隙相等或不等,相邻换热翅片之间相互平行或相邻换热翅片延伸出的平面形成交叉。
  9. 根据权利要求8所述的洗衣机、干衣机用翅片换热器,其特征在于,所述换热翅片为直片式或波浪式。
  10. 根据权利要求1所述的洗衣机、干衣机用翅片换热器,其特征在于,所述换热管的迂回弯折处为弧形段。
  11. 根据权利要求1所述的洗衣机、干衣机用翅片换热器,其特征在于,所述换热管中除去翻折处的迂回管段,其他处的相邻迂回管段所在平面之间形成夹角B。
  12. 根据权利要求1—5、7或9—11中任一项所述的洗衣机、干衣机用翅片换热器,其特征在于,所述换热管的外径φ为6mm—12.7mm,壁厚d1不小于0.4mm,换热翅片的厚度d2不小于0.09mm。
  13. 根据权利要求1—5、7或9—11中任一项所述的洗衣机、干衣机用翅片换热器,其特征在于,所述换热管内壁为光滑面或者为沿着换热管的长度方向布置的导流齿。
  14. 一种洗衣机、干衣机,其特征在于,包括如权利要求1—5、7或9—11中任一项所述的翅片换热器。
  15. 洗衣机、干衣机用翅片换热器制作方法,其特征在于,包括以下步骤:
    第一步,根据换热器的大小来确定一根金属管的总长度以及翅片组中换热翅片的片数;
    第二步,确定金属管的迂回弯折次数,以及迂回弯折处的半径R;
    第三步,将金属管以第二步中弯折次数及弯折半径进行迂回弯折,并将迂回弯折后的迂回管进行至少一次的翻折形成至少两列的迂回管组,以获得换热管;
    第四步,采用冲压设备在每一个换热翅片加工出供上述换热管迂回管装插的多个插口,每个换热翅片上对应位置的插口在投影后形成重叠;
    第五步,将换热翅片依次排列于组装模具上,相邻换热翅片之间形成间隙布置,且组装模具上相邻换热翅片之间同位置的插口投影后重叠,以获得由换热翅片排列而成的翅片组;
    第六步,将第三步中获得的换热管作为整体插入第五步中翅片组中,换热管中的迂回管一一对应的装插入于翅片组上对应位置的插口中,装插到位后,换热管中迂回管的迂回弯折段处于翅片组外部;
    第七步,使换热管外壁与插口内孔形成过盈配合,换热管与翅片组之间形成牢固结合,以获得整体式的换热器,将获得的换热器从组装模具上取下,即完成换热器的制作过程。
  16. 根据权利要求15所述的洗衣机、干衣机用翅片换热器制作方法,其特征在于,在第三步中,所获得的换热管除去翻折处的迂回管段,其他处的相邻迂回管段之间形成0°-90°的弯折。
PCT/CN2017/071904 2016-01-29 2017-01-20 洗衣机、干衣机用翅片换热器及其制作方法 WO2017129062A1 (zh)

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