WO2018040037A1 - 微通道换热器及风冷冰箱 - Google Patents

微通道换热器及风冷冰箱 Download PDF

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Publication number
WO2018040037A1
WO2018040037A1 PCT/CN2016/097689 CN2016097689W WO2018040037A1 WO 2018040037 A1 WO2018040037 A1 WO 2018040037A1 CN 2016097689 W CN2016097689 W CN 2016097689W WO 2018040037 A1 WO2018040037 A1 WO 2018040037A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
heat exchanger
tube
fins
exchange tubes
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PCT/CN2016/097689
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English (en)
French (fr)
Inventor
唐学强
孟宪春
任伟
Original Assignee
合肥美的电冰箱有限公司
合肥华凌股份有限公司
美的集团股份有限公司
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Application filed by 合肥美的电冰箱有限公司, 合肥华凌股份有限公司, 美的集团股份有限公司 filed Critical 合肥美的电冰箱有限公司
Priority to PCT/CN2016/097689 priority Critical patent/WO2018040037A1/zh
Publication of WO2018040037A1 publication Critical patent/WO2018040037A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag

Definitions

  • the invention relates to the field of refrigeration and heat dissipation equipment, in particular to a microchannel heat exchanger and an air-cooled refrigerator.
  • microchannel heat transfer technology engineering originates from the requirement of high-density electronic device cooling and heat transfer of micro-electro-mechanical systems. Due to its compact structure and high heat exchange efficiency, microchannel technology in the domestic market is the first in the automotive air-conditioning industry. Industrialization development.
  • the refrigeration system using the new generation of natural refrigerant CO2 is a supercritical cycle, and the system pressure is high.
  • the high-pressure working pressure of the system should be above 13 MPa, and the design pressure should reach 42.5 MPa, which puts high demands on the pressure resistance of the compressor and the heat exchanger.
  • the microchannel condenser Under the premise of compact structure, the microchannel condenser can simultaneously meet the pressure resistance, durability and system safety.
  • microchannel heat exchangers have gradually become the darling of the heat exchanger industry, and the application industry is more and more. Due to the increasing volume ratio of refrigerators, the use of microchannel evaporators in refrigerators has become one of the development trends of refrigerators.
  • the common microchannel evaporator has a small fin gap and a small fin length.
  • the frost layer When applied to the refrigerator, the frost layer accumulates too fast, and the frost layer easily blocks the fin gap, resulting in a short defrosting interval of the refrigerator and defrosting. frequently.
  • the moisture on the fins is not easy to accumulate into drops, which makes it difficult to drain the defrosting water, and finally forms ice on the surface of the evaporator, which affects the heat exchange effect.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent.
  • one aspect of the present invention is directed to a microchannel heat exchanger that is easy to drain defrosting water during defrosting.
  • Another object of the present invention is to provide an air-cooled refrigerator having the above-described microchannel heat exchanger.
  • the microchannel heat exchanger comprises: two headers, the two headers are arranged in parallel; a plurality of heat exchange tubes, the two ends of the plurality of heat exchange tubes are respectively connected to the two a collecting tube, the plurality of heat exchange tubes are bent along a length thereof to form a plurality of tube layers, and a refrigerant flow resistance of a part of the heat exchange tubes is smaller than a refrigerant flow resistance of the remaining heat exchange tubes; at least one wing a sheet, each of the fins being disposed between adjacent two of the tube layers or outside the tube layer disposed at the outermost layer, wherein each of the fins is in the extending direction of the heat exchange tube a corrugated extension, each of the fins extending continuously in a direction in which the header extends, and each of the fins is connected to at least two of the heat exchange tubes of the tube layer in which the tube is located, Ventilation holes are provided on the fins.
  • each fin is corrugated in the extending direction of the heat exchange tube by providing fins on the outer side of the adjacent tube layer or the outermost tube layer, in the header
  • Each fin extends continuously in the extending direction, so that during the defrosting process, the frosted water on the surface of the fin can accumulate into water droplets, and the water droplets can smoothly slide down along the continuous fins and dissipate the wings.
  • the problem that the surface of the sheet is large in water and cannot be exhausted can prevent the ice on the surface of the microchannel heat exchanger from affecting the heat exchange efficiency.
  • the air flows at different positions of the fins to promote mutual flow, and the other regions of the fins are prevented from being vented by other regions caused by the clogging of the frost layer, thereby increasing the overall heat exchange amount of the heat exchanger.
  • the heat exchange tubes can be disposed at the first windward side of the microchannel heat exchanger, thereby promoting uniform refrigerant flow of the plurality of heat exchange tubes and improving the overall heat exchanger. The amount of heat exchange.
  • the venting opening is provided at a gap between two adjacent flat tubes of the tube layer in which the fins are located. In this way, not only the space of the same pipe layer can be connected through the vent hole, but also the space of different pipe layers can be connected, so that the air at different positions of the heat exchanger can be further fully mixed, so that the air supply temperature is more uniform.
  • the venting hole has a size of 15-18 mm in the extending direction of the header, and the venting hole has a size of 4-7 in a direction perpendicular to the extending direction of the collecting tube. Millimeter.
  • a portion of the heat exchange tubes has a tube length that is less than a length of the remaining heat exchange tubes.
  • the lengths of the plurality of heat exchange tubes are sequentially increased or decreased sequentially in the extending direction of the header, and the heat exchange tubes on the windward side of each of the two adjacent heat exchange tubes are The length of the tube is smaller than the length of the tube of the heat exchange tube located on the leeward side.
  • a portion of the heat exchange tube has a flow area greater than a flow area of the remaining heat exchange tubes.
  • the flow area of the plurality of heat exchange tubes is sequentially increased or decreased sequentially in the extending direction of the header, and the heat exchange tubes located on the windward side of each of the two adjacent heat exchange tubes
  • the flow area is larger than the flow area of the heat exchange tube located on the leeward side. Therefore, the difference in the flow area of the heat exchange tubes passing through the refrigerant layers of each layer is set, and the difference in pressure drop loss of the heat exchange tubes of each layer is reduced, and finally, the refrigerant is evenly distributed in the plurality of heat exchange tubes, thereby Further improve the overall heat exchange capacity of the heat exchanger.
  • At least one of the fins includes a first fin segment and a second fin segment, the first fin segment having a size greater than a dimension of the second fin segment in an extension direction of the header .
  • the air-cooled refrigerator defines a refrigerating compartment and a duct, the duct having a return air inlet for entering air from the refrigerating compartment, the air-cooling refrigerator including the above according to the present invention Micro-pass as described in the embodiment A heat exchanger, the microchannel heat exchanger being disposed in the air duct.
  • the microchannel heat exchanger is arranged to facilitate the exhaustion of the defrosting water on the microchannel heat exchanger during defrosting, preventing the ice on the surface of the microchannel heat exchanger from affecting the heat exchange. effectiveness.
  • the microchannel heat exchanger is the above-described microchannel heat exchanger having a first fin segment and a second fin segment, the microchannel heat exchanger being disposed in the air duct, the two The headers are vertically disposed, and the second fin segments of the fins are disposed above the return air vents. Therefore, by providing the above microchannel heat exchanger, the distribution space of the frost layer is increased, the amount and speed of frost layer accumulation at the bottom of the fin are reduced, and the influence of frosting on the performance of the microchannel heat exchanger is reduced, and the lengthening is extended. Frost cycle.
  • the distribution space of the frost layer is increased, the amount and speed of the frost layer accumulation at the bottom of the fin are reduced, and the heat transfer between the frost and the microchannel is reduced.
  • the performance impact of the device extends the defrosting cycle.
  • FIG. 1 is a perspective view of a microchannel heat exchanger in accordance with one embodiment of the present invention.
  • FIG. 2 is a top plan view of the microchannel heat exchanger shown in FIG. 1.
  • FIG 3 is a perspective view of a fin of a microchannel heat exchanger in accordance with an embodiment of the present invention.
  • FIG. 4 is a perspective view of another fin of a microchannel heat exchanger in accordance with an embodiment of the present invention.
  • Figure 5 is a cross-sectional view of a microchannel heat exchanger employing the fins of Figure 4.
  • Figure 6 is a cross-sectional, enlarged, enlarged view of three heat exchange tubes of a microchannel heat exchanger in accordance with one embodiment of the present invention.
  • Figure 7 is a top plan view of a microchannel heat exchanger in accordance with another embodiment of the present invention.
  • Figure 8 is a cross-sectional view taken along line E-E of Figure 7.
  • Figure 9 is a perspective view of the microchannel heat exchanger shown in Figure 7 with the fins hidden.
  • Microchannel heat exchanger 100 is a Microchannel heat exchanger 100
  • Heat exchange tube 2 tube layer 20, tube section 21, straight section 211, curved section 212, first heat exchange tube 201, second heat exchange tube 202, third heat exchange tube 203, flow passage 210,
  • the fin 3 The fin 3, the first fin segment 31, the second fin segment 32, the vent hole 33, the first vent hole 331, the second vent hole 332, the parallel wall 301, and the vertical wall 302.
  • a microchannel heat exchanger 100 in accordance with an embodiment of the present invention will now be described with reference to Figs.
  • the microchannel heat exchanger 100 comprises: two headers 1, a plurality of heat exchange tubes 2 and at least one fin 3, The two headers 1 are arranged in parallel. Two ends of the plurality of heat exchange tubes 2 are respectively connected to the two header tubes 1, and the plurality of heat exchange tubes 2 are bent along the longitudinal direction thereof (direction indicated by an arrow P in Fig. 1) to form a plurality of tube layers 20.
  • the two headers 1 are spaced apart from each other, and the plurality of heat exchange tubes 2 are bent to form at least two tube layers 20, each of which is bent to form one or more tube segments 21, parallel to the current collection
  • One or more of the tube segments 21 on the same plane constitute a tube layer 20 in the direction in which the tubes 1 extend (in the direction indicated by the arrow M in Fig. 1).
  • a plurality of heat exchange tubes 2 are arranged in parallel along the extending direction of the header 1 shown by the arrow M.
  • the plurality of pipe sections 21 of each heat exchange tube 2 comprises a straight section 211 and a curved section 212 between the straight sections 211, the curved section 212 being parallel to the extension of the header 1
  • the direction (the direction indicated by the arrow M) is curved by a predetermined angle with respect to the straight section 211.
  • the bending angle of each curved section 212 is 180 degrees
  • the lengths of the plurality of heat exchange tubes 2 are equal
  • the number of times of bending of the plurality of heat exchange tubes 2 is equal
  • the plurality of heat exchange tubes 2 are formed by bending.
  • the lengths of the straight sections 211 are equal, and the lengths of the curved sections 212 formed are also equal.
  • a plurality of straight sections 211 of the plurality of heat exchange tubes 2 in the same row constitute a tube layer 20, and when the tube layer 20 of a certain layer is connected with the fins 3, the fins 3 can be connected to the tube layer 20 for replacement.
  • the flat section 211 of the heat pipe 2 is on.
  • the cross-sectional profile of the heat exchange tube 2 is a racetrack shape with two arcs in a straight line, wherein the straight side of the heat exchange tube 2 is parallel to the extending direction of the header 1 (the direction indicated by the arrow M).
  • the fins 3 are connected to the straight sections of the heat exchange tubes 2.
  • the size of the heat exchange tube 2 in the extending direction of the header 1 is the width of the heat exchange tube 2
  • the heat exchange tube 2 is said to be perpendicular to the width direction of the heat exchange tube 2.
  • the width of the heat exchange tube 2 is larger than the thickness of the heat exchange tube 2.
  • each of the fins 3 is disposed between the adjacent two tube layers 20 or outside the tube layer 20 of the outermost layer, where the fins 3 may be one or more.
  • a plurality of fins 3 are provided, and one fin 3 is disposed between each adjacent two tube layers 20, and the outermost one of the plurality of tube layers 20 Outside the tube layer 20
  • the fins 3 are also provided on the sides, respectively.
  • the microchannel heat exchanger 100 is a multi-layer heat exchanger in which the heat exchangers connect the layers 20 of the layers through the fins 3.
  • each fin 3 extends in a corrugated manner in the extending direction of the heat exchange tube 2 (the direction indicated by the arrow P), and each fin 3 in the extending direction of the header 1 (the direction indicated by the arrow M) Continuously extending, and each fin 3 is connected to at least two heat exchange tubes 2 of the tube layer 20 in which it is located. That is, the fins 3 are corrugated in the longitudinal direction of the heat transfer tubes 2, and the fins 3 are continuously provided in the width direction of the heat exchange tubes 2.
  • the fins 3 are continuously disposed in the width direction of the heat exchange tubes 2, meaning that the fins are not divided into a plurality of sections and disposed at intervals in the width direction of the heat transfer tubes, that is, the fins are shown at M
  • the direction is uninterrupted.
  • the fins of most of the microchannel heat exchangers in the prior art are short fins, and the fins are arranged between two adjacent heat exchange tubes, the fin length is small, the gap is small, and the processing is complicated.
  • the evaporator is used at low temperature, the accumulation speed of the frost layer is fast.
  • the frost is defrosted, the moisture on the fins is dispersed on the small fins, and the water vapor does not easily accumulate into drops and drip, which is difficult to discharge.
  • the fins 3 by continuously arranging the fins 3 in the width direction of the heat exchange tubes 2 (direction indicated by the arrow M), not only the processing of the fins 3 is simplified, for example, the entire flat sheets can be processed into wings.
  • the sheet has low processing cost and is easy to assemble, and the water vapor on the fins 3 is easily aggregated into droplets during the defrosting and is easily discharged along the continuous fins 3 to prevent the frost layer from forming ice on the surface of the microchannel heat exchanger 100. In order to ensure the heat exchange effect of the microchannel heat exchanger 100.
  • the fins 3 are connected to at least two heat exchange tubes 2 in the width direction of the heat transfer tubes 2, and the plurality of heat exchange tubes 2 are joined together by fins to ensure the structural strength of the microchannel heat exchanger 100.
  • each of the fins 3 is connected to all of the heat exchange tubes 2 in the tube layer 20 in which it is located, and the heat exchange tubes 2 connected to the fins 3 can be integrally connected by the fins 3, and the structure is firm and reliable.
  • the microchannel heat exchanger 100 includes three heat exchange tubes 2, and three heat exchange tubes 2 are bent to form four rows of tube layers 20, and three fins 3 between the four rows of tube layers 20 will The four rows of tube layers 20 are connected together, and the adjacent fins 3 and the three heat exchange tubes 2 in each of the tube layers 20 are connected together, and one of the outermost two tube layers 20 is also provided with a wing.
  • Slice 3 since the tube layers 20 are spaced apart in the direction indicated by the arrow Q, the outermost outer layer of the tube layer 20 refers to the outermost sides of the plurality of tube layers 20 in the direction indicated by Q.
  • the fins 3 are provided with vent holes 33 so that the blown air can pass through the fins 3 through the vent holes 33 and then blown between the heat transfer tubes 2.
  • the air can be mixed with each other after flowing through the outermost heat exchange tubes 2 or the fins 3.
  • the problem that the bottom gap of some fins is blocked by the frost layer causes no air circulation in the upper portion can be solved, and on the other hand, The air flowing through different positions of the heat exchanger is mixed, so that the air supply temperature is uniform, which helps to improve the uniformity of the box temperature.
  • the refrigerant flow resistance of the partial heat exchange tubes 2 is smaller than the refrigerant flow resistance of the remaining heat exchange tubes 2.
  • the heat exchange tube on the windward side is in contact with the air returning wind first.
  • the temperature difference between the refrigerant and the outside air is the largest, so the heat exchange amount is large and the heat exchange is relatively sufficient.
  • the two-phase section and the superheating section are long, and the refrigerant flow resistance is large.
  • the heat exchange tube with the most heat exchange is easy to be small, and the refrigerant flow rate is easy to be small.
  • the characteristics of the large heat exchange here are contradictory.
  • the refrigerant flow resistance of the partial heat exchange tube 2 is designed to be small, and then the heat exchange tube 2 is disposed at a position where the microchannel heat exchanger 100 can first exchange heat with the blown air.
  • the pressure drop of the refrigerant flowing through the heat exchange tube 2 can be reduced, thereby increasing the refrigerant flow rate of the heat exchange tube 2, so that the refrigerant flow rate of the plurality of heat exchange tubes 2 can be made uniform, thereby making
  • the refrigerant is uniformly distributed in the plurality of heat exchange tubes 2 to improve the overall heat exchange amount of the heat exchanger.
  • each of the fins 3 is corrugated in the extending direction of the heat exchange tubes 2. Extending, each fin 3 extends continuously in the extending direction of the header 1, so that during the defrosting process of the microchannel heat exchanger 100, the frosted water on the surface of the fin 3 can accumulate into water droplets, and the water droplets can be continuous along the wings.
  • the sheet 3 smoothly slides down and drains, solving the problem that the surface of the fin 3 has a large amount of water hanging and cannot be exhausted, and can prevent the ice on the surface of the microchannel heat exchanger 100 from affecting the heat exchange efficiency.
  • the air flows at different positions of the fins to promote mutual flow, and the other portions of the fins which are blocked by the frost layer are prevented from flowing without air, thereby increasing the overall heat exchange amount of the heat exchanger.
  • the refrigerant flow resistance of the partial heat exchange tubes 2 can be small, the heat exchange tubes 2 can be disposed at the first windward direction of the microchannel heat exchanger 100, thereby causing the refrigerant flow rates of the plurality of heat exchange tubes 2 to be uniform. Improve the overall heat exchange capacity of the heat exchanger.
  • the refrigerant flow resistance of the partial heat exchange tubes 2 is set to be smaller than that of the other heat exchange tubes 2, and there are various methods.
  • the tube length of a portion of the heat exchange tubes 2 may be set to be smaller than the tube length of the remaining heat exchange tubes 2. It can be understood that under the same flow area, the shorter the heat exchange tube 2 is, the smaller the flow resistance is, and the difference in the length of the heat exchange tube 2 is designed to make it easier to realize different flow resistance when the refrigerant flows through different heat exchange tubes.
  • the tube lengths of the plurality of heat exchange tubes 2 are sequentially increased or decreased sequentially, and each adjacent two heat exchange tubes 2 is located in the windward direction.
  • the tube length of the heat exchange tube 2 on the side is smaller than the tube length of the heat exchange tube 2 on the leeward side.
  • Such a microchannel heat exchanger 100 sets a difference in tube length of the heat exchange tubes 2 passing through the refrigerant layers of each layer, and reduces the difference in pressure drop loss of the heat exchange tubes of each layer, so that the refrigerant flows through the heat exchange tubes 2 of each layer.
  • the resistance is basically the same, and finally achieves the purpose of uniform liquid separation, thereby further improving the overall heat exchange capacity of the heat exchanger.
  • the tube length ratio of the three heat exchange tubes 2 is 6:5:4 in the extending direction of the header 1.
  • the heat exchange tube 2 having the shortest tube length is located on the windward side of the heat exchanger, and the heat exchange tube 2 having the largest tube length is located on the leeward side of the heat exchanger.
  • the microchannel heat exchanger 100 includes a first heat exchange tube 201, a second heat exchange tube 202, and a third from bottom to top.
  • the heat exchange tube 203 and the three heat exchange tubes 2 have a tube length ratio of 4:5:6, wherein the air flow is blown from below to the heat exchanger when the heat exchanger is in operation, and the first heat exchange tube 201 in the lowermost layer is the longest.
  • the uppermost third heat exchange tube 203 is the shortest.
  • the three heat exchange tubes 2 are bent three times to form four straight sections 211 and three curved sections 212, and the three heat exchange tubes 2 are made to have different tube lengths by adjusting the lengths of the respective straight sections 211.
  • the three heat exchange tubes 2 can also make the respective tube lengths different by adjusting the respective bending times.
  • the first heat exchange tube 201 includes two straight sections 211 and one curved section 212
  • the third heat exchange tube 203 still includes four straight sections 211 and three curved sections 212
  • each of the heat exchange tubes 2 The straight sections 211 are equally long, and the tube length of the first heat exchange tube 201 is about half of the tube length of the third heat exchange tube 203.
  • the number of the heat exchange tubes 2 can be varied according to actual needs, and the tube length ratio of each heat exchange tube 2 can also be adapted to the actual situation.
  • the flow area of the partial heat exchange tubes 2 may be designed to be larger than the flow area of the remaining heat exchange tubes 2. It can be understood that under the same pipe length, the larger the flow area of the heat exchange tube 2, the smaller the refrigerant flow resistance, and the different design of the flow area of the heat exchange tube 2 makes it easy to realize different heat exchange of the refrigerant flow. The flow resistance is different when the pipe is used.
  • the flow areas of the plurality of heat exchange tubes 2 are sequentially increased or decreased sequentially, and in each of the two adjacent heat exchange tubes 2, located on the windward side
  • the overcurrent area of the heat exchange tube 2 is larger than the flow area of the heat exchange tube 2 on the leeward side.
  • Such a microchannel heat exchanger 100 sets a difference in the flow area of the heat exchange tubes 2 through the refrigerant layers of each layer, thereby reducing the difference in pressure drop loss of the heat exchange tubes of each layer, and finally achieving further promotion of the refrigerant in a plurality of exchanges.
  • the heat pipe 2 is evenly distributed, thereby further increasing the overall heat exchange capacity of the heat exchanger.
  • the heat exchange tubes 2 are three, and the microchannel heat exchanger 100 includes a first heat exchange tube 201, a second heat exchange tube 202, and a third from bottom to top.
  • the heat exchange tube 203, the ratio of the flow area of the three heat exchange tubes 2 is 4:3:2, wherein the air flow is blown from below to the heat exchanger during operation of the heat exchanger, and the first heat exchange tube 201 of the lowermost layer passes.
  • the flow area is the largest, and the flow path area of the third heat exchange tube 203 of the uppermost layer is the smallest.
  • a plurality of refrigerant flow passages 210 may be defined in each of the heat exchange tubes 2 , and the cross-sectional area of the flow passages 210 in each heat exchange tube 2 and the flow passage 210 may be changed.
  • the amount, etc., to change the flow area of each heat exchange tube 2, so that the pressure drop of each flow path in the heat exchange process is basically the same, to maximize the liquid separation uniformity and improve the heat transfer performance.
  • the number of the heat exchange tubes 2 can be varied according to actual needs, and the ratio of the flow area of each heat exchange tube 2 can also be adapted to the actual situation.
  • the venting holes 33 are provided at the spaces between the corresponding adjacent two flat tubes 2 of the tube layer 20 where the fins 3 are located.
  • the vent hole 33 not only the space of the same pipe layer 20 can be connected through the vent hole 33, but also the space of the different pipe layers 20 can be connected, so that the air at different positions of the heat exchanger can be further mixed sufficiently, so that the air supply temperature is further increased. Evenly.
  • the size a of the vent hole 33 is 15-18 mm, and the vent hole is perpendicular to the extending direction of the header 1.
  • the size b of 33 is 4-7 mm.
  • the venting holes 33 are square holes, the length a of the venting holes 33 is between 15 and 18 mm, and the width b of the venting holes 33 is between 4 and 7 mm.
  • the vents 33 can also be formed in other shapes, and the vents 33 can also be designed in other sizes.
  • the vent hole 33 includes a first vent hole 331 and a second vent hole 332.
  • the first vent hole 331 is an annular hole
  • the second vent hole 332 is open toward one side in the direction indicated by M.
  • each fin 3 in the extending direction of the heat exchange tubes 2 (the direction indicated by the arrow P in FIG. 1), each fin 3 includes staggered parallel walls 301 and vertical.
  • the wall 302 is formed in a zigzag shape, and the parallel wall 301 is parallel to the extending direction of the heat exchange tube 2, and the vertical wall 302 is perpendicular to the extending direction of the heat exchange tube 2. That is, the parallel wall 301 extends in the direction P, and the vertical wall 302 extends in the direction Q.
  • the vent hole 33 may be disposed on the vertical wall 302, so that the ventilation effect can be ensured, and the contact area between the heat exchange tube 2 and the fin 3 is not reduced, and the heat exchange tube 2 is not affected to the fin. 3 heat transfer.
  • the vent hole 33 may be disposed at a position where the fin 3 does not contact the heat exchange tube 2, and the structure and position of the vent hole 33 are not limited herein.
  • the vent holes 33 of the fins 3 may be provided on the vertical wall 302 or on the parallel wall 301 which is not in contact with the tube layer 20.
  • At least one fin 3 includes a first fin segment 31 and a second fin segment 32, and the first fin segment in the extending direction of the header 1 (direction indicated by arrow M)
  • the size h1 of 31 is larger than the size h2 of the second fin segment 32.
  • the fins 3 are arranged to be long and short, corresponding to the formation of a notch in the fins 3.
  • the second fin segments 32 are shorter than the first fin segments 31 to form the above-mentioned notches, and the notches are provided as microchannel heat exchangers. 100 Design structure optimized for frosting and defrosting characteristics.
  • the microchannel heat exchanger 100 when used to output a cooling capacity, air may be blown from the notch of the corresponding microchannel heat exchanger 100 to the microchannel heat exchanger 100. Since the humidity is lowered after the air absorbs the cold amount, the moisture in the air easily condenses on the surface of the microchannel heat exchanger 100 to form a frost layer. After the air is blown from the gap, there is no blockage of the fins 3 at the notch, and the air can be easily blown into the inner tube layer 20 of the microchannel heat exchanger 100, thereby increasing the distribution space of the frost layer and reducing the wing. The amount and speed of frost layer accumulation at the bottom of the sheet 3 reduces the influence of frost on the performance of the microchannel heat exchanger 100 and prolongs the defrosting cycle.
  • each fin 3 includes at least two first fin segments 31 and/or at least two second fin segments 32 in the direction in which the heat exchange tubes 2 extend (arrow P)
  • the first fin segment 31 and the second fin segment 32 are alternately arranged.
  • the spacing is advantageous for the microchannel heat exchanger 100 to disperse the frost layer during frosting, so that the frost can be removed more quickly during defrosting.
  • the second fin segments 32 on the plurality of fins 3 are correspondingly disposed. That is, when there are a plurality of fins 3, the projection shapes of the plurality of fins 3 are substantially the same in the plane on which the tube layer 20 is located, and each of the fins 3 forms a notch at the same position. Thus, the positions of the notches of the plurality of fins 3 are uniform, so that the heat transfer efficiency of the microchannel heat exchanger 100 can be increased, and the distribution space of the frost layer can be further increased, and the amount and speed of accumulation of the frost layer at the bottom of the fin 3 can be reduced.
  • the dimension h2 of the second fin segment 32 is 0.67-0.75 of the dimension h1 of the first fin segment 31, also That is, the second fin segment 32 is shorter by 1/4-1/3 than the first fin segment 31 in the extending direction of the header 1.
  • the connection strength of the fin 3 to the tube layer 2 at the second fin segment 32 will be weakened, and if the second fin segment 32 is too long, air will be formed.
  • the size h2 of the second fin segment 32 is 0.67-0.75 of the dimension h1 of the first fin segment 31, which can ensure that the fin 3 can smoothly discharge the defrosting water in all the segments, and at the same time ensure the frost at the time of entering the wind.
  • the layers can be evenly distributed.
  • first fin segment 31 and the second fin segment 32 of each fin 3 are connected to all of the heat exchange tubes 2 in the tube layer 20 in which they are located.
  • the windward side of the second fin segment 32 and the outermost heat exchange tube 2 on the tube layer 20 where it is located The contact size m between the electrodes is 5-10 mm. That is to say, even if the fins 3 are notched, the fins 3 form a joint fit with the outermost heat exchange tubes 2 at the portions of the notched edges.
  • the second wing segment 32 is designed such that the contact dimension m between the windward side and the outermost heat exchange tube 2 is 5-10 mm, ensuring that it is connected to the outermost heat exchange tube 2, preventing the fins from being suspended when the fins 3 are suspended. The water droplets on the sheet 3 cannot flow down to the outermost heat exchange tubes 2.
  • the tube layer 20 of the microchannel heat exchanger 100 is disposed vertically and the plurality of tube layers 20 are spaced apart in a horizontal direction.
  • Each of the fins 3 extends in a corrugated manner in the horizontal direction, and each of the fins 3 continuously extends in the vertical direction.
  • the fins 3 are flush at the upper end, the fins 3 are notched at the lower end, and the fins 3 are divided into a first fin segment 31 and a second fin segment 32, wherein between the second fin segment 32 and the lowermost heat exchange tube 2
  • the contact height m is 5-10 mm, and an interference fit is formed between the fin 3 and the lowermost heat exchange tube 2.
  • each of the fins 3 extends in a zigzag shape, as shown in FIG. 4, the gap between adjacent teeth. n is 5-10 mm.
  • the interdental gap n of the fins 3 is substantially the same, and the ratio of the inter-tooth gap n of each of the fins 3 is between 110% and 90%.
  • the microchannel heat exchanger 100 is optimized according to the characteristics of frosting and defrosting on the heat exchanger, and the lengths of the fins 3 and the fins 3 passing through the multilayered tube layer 20 are different.
  • the hole opening on the surface of the fin 3, and the different flow area or tube length of the heat exchange tube are designed to reduce the sensitivity of the heat exchange of the parallel flow heat exchanger to the surface frost layer accumulation, and the surface frost of the heat exchanger is slowed down.
  • the effect of layer accumulation on the operation of the system is beneficial to the exhaustion of the defrosting water, prolonging the defrosting cycle and improving the heat transfer performance.
  • a refrigerator (not shown) according to an embodiment of the present invention includes a microchannel heat exchanger 100 according to the above embodiment of the present invention.
  • the microchannel heat exchanger 100 can be used as a refrigerator of a refrigerator or an evaporator of a greenhouse.
  • the structure of the microchannel heat exchanger 100 has been described by the above embodiments, and will not be described herein.
  • the refrigerator of the embodiment of the present invention by providing the above-mentioned microchannel heat exchanger 100, it is advantageous to exhaust the defrosting water on the microchannel heat exchanger 100 during defrosting, and prevent the ice on the surface of the microchannel heat exchanger 100 from being affected by the ice. Thermal efficiency.
  • the air-cooled refrigerator defines a refrigerating compartment and a duct, the duct having a return air for introducing air from the refrigerating compartment, and the air-cooling refrigerator includes the fin 3 according to the present invention including the first fin section 31 And the microchannel heat exchanger 100 of all embodiments of the second fin segment 32.
  • the structure of the microchannel heat exchanger 100 has been described by the above embodiments, and will not be described herein.
  • the microchannel heat exchanger 100 can be used as a refrigerating chamber of an air-cooled refrigerator or an evaporator of a greenhouse.
  • the microchannel heat exchanger 100 is disposed in the air duct, and the microchannel heat exchanger 100 can be arranged above the air return port of the refrigerating chamber or the greenhouse.
  • the short second fin segment 32 has a longer first fin segment 31 disposed at other locations.
  • the air channel microchannel heat exchanger 100 two headers 1 are vertically disposed, and the second fin segments 32 of the fins 3 are disposed above the return air vents. That is to say, when the air-cooled refrigerator is cooling, the indoor air in the cooling room is blown from the return air port to the air passage, and the blown air is blown into the microchannel heat exchanger 100 from the bottom of the microchannel heat exchanger 100.
  • the portion of the fin 3 that is shorter than the first fin segment 31 in the second fin segment 32 corresponds to a notch, and air can be blown from the notch of the corresponding microchannel heat exchanger 100 toward the microchannel heat exchanger 100. After the air absorbs the cold amount, the humidity is lowered, and the water vapor in the air is easily condensed on the surface of the microchannel heat exchanger 100 to form a frost layer. Since air is blown from the notch to the microchannel heat exchanger 100, air can be easily blown between the inner tube layers 20 of the microchannel heat exchanger 100 after the blockage of the fins 3, thereby increasing the frost layer.
  • the distribution space reduces the accumulation amount and speed of the frost layer at the bottom of the fin 3, reduces the influence of the frost on the performance of the microchannel heat exchanger 100, and prolongs the defrosting cycle.
  • the horizontal width w (marked in FIG. 3) of the second fin segment 32 is substantially 1.1-1.4 times the horizontal width of the return air vent, so that the fin 3 can be avoided as far as possible from the return air vent, and the return air is blown off.
  • the horizontal width w (marked in FIG. 3) of the second fin segment 32 is substantially 1.1-1.4 times the horizontal width of the return air vent, so that the fin 3 can be avoided as far as possible from the return air vent, and the return air is blown off.
  • the outermost fins 3 of the microchannel heat exchanger 100 are directly barely leaked, and there is no shield on the outer side of the fins 3. protection. That is, the outermost fin 3 It is not connected to other components and has no protective facilities to reduce its contact with the tank of the refrigerating compartment and the cover of the heat exchanger, reducing the leakage of the tank and the possibility of frost on the surface of the heat exchanger cover.
  • the length ratio of the two adjacent fin sections is between 75% and 67%, which can increase the fin gap on the windward side of the heat exchanger and reduce the influence of frost layer accumulation on the air supply volume and air supply temperature of the refrigerator. Defrost time
  • the lower edge of the fin 3 extends into or protrudes from the adjacent heat exchange tube by 5-10mm, which facilitates the downward flow of the defrosting water to prevent water droplets from accumulating at the ends of the fin;
  • the flow resistance of the heat exchange tubes in each layer is different, resulting in a small flow of refrigerant at the bottom of the microchannel heat exchanger, and the microchannel heat exchanger can not be confiscated to exert efficient heat transfer.
  • the flow rate of the refrigerant flowing through each heat exchange tube is made as much as possible, thereby reducing the phenomenon of uneven liquid distribution of the heat exchanger, and improving the replacement. Heat exchange capacity of the heat exchanger;
  • This design solves the problem that the heat exchange effect of the evaporator in the air-cooled refrigerator used by the microchannel heat exchanger 100 is sensitive to the increase of the surface frosting amount, fully exerts the characteristics of the parallel flow heat exchanger, and increases the volume ratio of the refrigerator.
  • the refrigerator is also provided with components of other refrigeration systems such as a compressor and a condenser.
  • the structure and working principle of the refrigeration system are already prior art, and the connection structure of the microchannel heat exchanger 100 in the refrigeration system of the refrigerator is also It has been an existing technology and will not be described here.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining “first” and “second” can be clearly indicated Or implicitly include one or more of the features. In the description of the present invention, “a plurality” means two or more unless otherwise stated.
  • the terms “installation”, “connected”, “connected”, and “fixed” are to be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. , or integrated; can be mechanical connection, or can be electrical connection; can be directly connected, or can be indirectly connected through an intermediate medium, can be the internal communication of two elements or the interaction of two elements.
  • installation can be understood in a specific case by those skilled in the art.
  • the description of the terms “embodiment”, “example” and the like means that a specific feature, structure, material or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. .
  • the schematic representation of the above terms does not necessarily mean the same embodiment or example.
  • the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples.

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Abstract

提供了一种微通道换热器（100）和风冷冰箱。微通道换热器（100）包括：两个集流管（1）、多个换热管（2）和至少一个翅片（3），两个集流管（1）平行设置。多个换热管（2）的两端分别连接两个集流管（1），多个换热管（2）沿其长度方向弯折形成多个管层（20），部分换热管（2）的制冷剂流通阻力小于其余换热管（2）的制冷剂流通阻力。每个翅片（3）设在相邻两个管层（20）之间或设在最外层的管层（20）的外侧，在换热管（2）的延伸方向上每个翅片（3）呈波纹状延伸，在集流管（1）的延伸方向上每个翅片（3）连续延伸，翅片（3）上设有通风孔（33）。

Description

微通道换热器及风冷冰箱 技术领域
本发明涉及制冷和散热设备领域，尤其是涉及一种微通道换热器及风冷冰箱。
背景技术
微通道换热技术工程上的发展源自于高密度电子器件冷却及微电子机械系统传热的需求，由于其结构紧凑、换热效率高，国内市场上微通道技术最先在汽车空调行业得到了产业化发展。
应用了新一代自然冷媒CO2的制冷系统为超临界循环，系统压力很高。例如在空调系统中，系统高压工作压力要到13MPa以上，设计压力要达到42.5MPa，这对压缩机和换热器的耐压性均提出了很高的要求。在结构紧凑的前提下，微通道冷凝器可以同时满足耐压性、耐久性和系统安全性。随着生产技术提高，微通道换热器逐渐成为换热器界的宠儿，应用行业越来越多。由于现在冰箱容积率要求越来越高，冰箱使用微通道蒸发器成为冰箱发展趋势之一。
常见的微通道蒸发器翅片间隙较小，且翅片长度较小，应用到冰箱中会存在霜层积累速度过快，霜层容易堵塞翅片间隙，导致冰箱化霜间隔时间短、化霜频繁。同时化霜过程中由于翅片较短，翅片上水分不容易积聚成滴滴落，导致化霜水难以排尽，最终在蒸发器表面形成顽冰，影响换热效果。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明一个方面旨在提出一种微通道换热器，该微通道换热器在除霜时容易排尽化霜水。
本发明的另一个目的在于提供一种具有上述微通道换热器的风冷冰箱。
根据本发明的微通道换热器，包括：两个集流管，所述两个集流管平行设置；多个换热管，所述多个换热管的两端分别连接所述两个集流管，所述多个换热管沿其长度方向弯折形成多个管层，部分所述换热管的制冷剂流通阻力小于其余所述换热管的制冷剂流通阻力；至少一个翅片，每个所述翅片设在相邻两个所述管层之间或设在最外层的所述管层的外侧，在所述换热管的延伸方向上每个所述翅片呈波纹状延伸，在所述集流管的延伸方向上每个所述翅片连续延伸，且每个所述翅片与其所在的所述管层中的至少两个所述换热管相连，所述翅片上设有通风孔。
根据本发明实施例的微通道换热器，通过在相邻管层或者最外侧管层的外侧设置翅片，在换热管的延伸方向上每个翅片呈波纹状延伸，在集流管的延伸方向上每个翅片连续延伸，从而微通道换热器在除霜过程中，翅片表面霜化水可积聚成水滴，水滴可沿连续的翅片顺畅地滑落并排走，解决了翅片表面挂水量较大、无法排尽的问题，可防止微通道换热器表面产生顽冰而影响换热效率。通过在翅片上设置通风孔，促进翅片不同位置处空气相互流动，防止翅片局部间隙被霜层堵塞导致的其他区域没有空气流通，从而增加换热器的整体换热量。通过将部分换热管的流通阻力设计得较小，该换热管可设置在微通道换热器的最先迎风处，从而促使多个换热管的制冷剂流量均匀，提高换热器整体换热量。
在一些实施例中，所述通风孔设在所述翅片所在的所述管层的相邻两个所述扁管之间的空隙处。这样通过通风孔不仅可以将同一管层的空间连通起来，还能将不同管层的空间连通起来，使换热器不同位置的空气能够进一步充分混合，使得送风温度更加均匀。
在一些实施例中，在所述集流管的延伸方向上所述通风孔的尺寸为15-18毫米，在垂直于所述集流管的延伸方向上所述通风孔的尺寸为4-7毫米。
在一些实施例中，部分所述换热管的管长小于其余所述换热管的管长。
具体地，在所述集流管的延伸方向上所述多个换热管的管长依次递增或者依次递减，且每相邻的两个所述换热管中位于迎风侧的换热管的管长小于位于背风侧的换热管的管长。由此，将通过各层制冷剂的换热管的管长差异设定，减小各层换热管压降损失差异，最终达到进一步促使制冷剂在多个换热管内分液均匀，从而进一步提高换热器整体换热量。
在另一些实施例中，部分所述换热管的过流面积大于其余所述换热管的过流面积。
具体地，在所述集流管的延伸方向上所述多个换热管的过流面积依次递增或者依次递减，且每相邻的两个所述换热管中位于迎风侧的换热管的过流面积大于位于背风侧的换热管的过流面积。由此，将通过各层制冷剂的换热管的过流面积差异设定，减小各层换热管压降损失差异，最终达到进一步促使制冷剂在多个换热管内分液均匀，从而进一步提高换热器整体换热量。
在一些实施例中，至少一个所述翅片包括第一翅片段和第二翅片段，在所述集流管的延伸方向上所述第一翅片段的尺寸大于所述第二翅片段的尺寸。由此，空气能容易地吹入微通道换热器的内部管层之间，增大了霜层的分布空间，减小了翅片底部霜层积聚量和速度，减小了结霜对微通道换热器的性能影响，延长化霜周期。
根据本发明的风冷冰箱，所述风冷冰箱内限定出制冷间室和风道，所述风道具有用于从所述制冷间室进风的回风口，所述风冷冰箱包括根据本发明上述实施例所述的微通 道换热器，所述微通道换热器设在所述风道内。
根据本发明实施例的风冷冰箱，通过设置上述微通道换热器，有利于化霜时微通道换热器上化霜水排尽，防止微通道换热器表面产生顽冰而影响换热效率。
在一些实施例中，所述微通道换热器为上述的具有第一翅片段和第二翅片段的微通道换热器，所述微通道换热器设在所述风道内，所述两个集流管竖向设置，所述翅片的所述第二翅片段设置在所述回风口的上方。由此，通过设置上述微通道换热器，增大了霜层的分布空间，减小了翅片底部霜层积聚量和速度，减小了结霜对微通道换热器的性能影响，延长化霜周期。
根据本发明实施例的风冷冰箱，通过设置上述微通道换热器，增大了霜层的分布空间，减小了翅片底部霜层积聚量和速度，减小了结霜对微通道换热器的性能影响，延长化霜周期。
本发明的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本发明的实践了解到。
附图说明
本发明的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是根据本发明一个实施例的微通道换热器的立体图。
图2是图1所示的微通道换热器的俯视图。
图3是根据本发明实施例的微通道换热器的一种翅片的立体图。
图4是根据本发明实施例的微通道换热器的另一种翅片的立体图。
图5是采用图4所示翅片的微通道换热器剖视图。
图6是根据本发明一个实施例的微通道换热器三个换热管的剖面对比放大示意图。
图7是根据本发明另一个实施例的微通道换热器的俯视图。
图8是图7中沿E-E方向的剖视图。
图9是图7所示的微通道换热器在翅片隐藏时的立体图。
附图标记：
微通道换热器100、
集流管1、
换热管2、管层20、管段21、平直段211、弯曲段212、第一换热管201、第二换热管202、第三换热管203、流通通道210、
翅片3、第一翅片段31、第二翅片段32、通风孔33、第一通风孔331、第二通风孔332、平行壁301、垂直壁302。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
下面参考图1-图9描述根据本发明实施例的微通道换热器100。
根据本发明实施例的微通道换热器100，如图1和图2所示，微通道换热器100包括：两个集流管1、多个换热管2和至少一个翅片3，两个集流管1平行设置。多个换热管2的两端分别连接两个集流管1，多个换热管2沿其长度方向(图1中箭头P所示方向)弯折形成多个管层20。
具体地，两个集流管1彼此间隔布置，多个换热管2弯折形成至少两层管层20，每个换热管2弯折形成一个或者多个管段21，在平行于集流管1的延伸方向(图1中箭头M所示方向)上，位于同一平面上的一个或者多个管段21构成一个管层20。可选地，多个换热管2沿箭头M所示的集流管1的延伸方向平行间隔设置。在图1所示示例中，每个换热管2的多个管段21均包括平直段211和位于平直段211之间的弯曲段212，弯曲段212绕平行于集流管1的延伸方向(箭头M所示方向)相对于平直段211弯曲预定角度。在图1中每个弯曲段212的弯曲角度均为180度，多个换热管2的长度相等，多个换热管2弯折的次数相等，多个换热管2弯折后形成的平直段211的长度相等，形成的弯曲段212的长度也相等。多个换热管2的位于同一排的多个平直段211构成一个管层20，当某一层的管层20连接有翅片3时，翅片3可以连接在该管层20上换热管2的平直段211上。
可选地，换热管2的横截面轮廓为两头圆弧中间直线的跑道形，其中，换热管2的直边段与集流管1的延伸方向(箭头M所示方向)相平行，翅片3与换热管2的直边段相连。为方便描述，称换热管2在集流管1的延伸方向(箭头M所示方向)上的尺寸为换热管2的宽度，称换热管2在垂直于换热管2的宽度方向(箭头M所示方向)且垂直于换热管2的长度方向(箭头P所示方向)上的尺寸为换热管2的厚度，换热管2的厚度方向为图1中箭头Q所示方向。在图1中，换热管2的宽度大于换热管2的厚度。
具体地，每个翅片3设在相邻两个管层20之间或设在最外层的管层20的外侧，这里，翅片3可为一个或者多个。在本发明的一个具体示例中，如图1所示，翅片3为多个，每相邻的两个管层20之间设有一个翅片3，在多个管层20中最外侧的管层20的外 侧也分别设有翅片3。微通道换热器100为多层罗列的换热器，换热器通过翅片3把各层管层20连接起来。
具体地，在换热管2的延伸方向(箭头P所示方向)上每个翅片3呈波纹状延伸，在集流管1的延伸方向(箭头M所示方向)上每个翅片3连续延伸，且每个翅片3与其所在的管层20中的至少两个换热管2相连。也就是说，翅片3在换热管2的长度方向上呈波纹状，翅片3在换热管2的宽度方向上连续设置。这里提到翅片3在换热管2的宽度方向上呈连续设置，是指在换热管的宽度方向上，翅片不会分成多段后间隔设置，也就是说，翅片在M所示方向上是不间断的。
可以理解的是，现有技术中大部分微通道换热器的翅片均是短小翅片，翅片设在相邻两个换热管之间，翅片长度小、间隙也小，加工复杂，低温下作蒸发器使用时霜层积累速度快，化霜时翅片上水分分散在各个小翅片上，水汽不容易积聚成滴滴落、难排尽。
而本发明实施例中通过将翅片3在换热管2的宽度方向(箭头M所示方向)上呈连续设置，不仅翅片3的加工得到了简化，例如可由整条平直板加工成翅片，加工成本低，易装配，而且在化霜时翅片3上的水汽容易聚集成滴且容易沿连续的翅片3滑落排尽，避免霜层在微通道换热器100表面形成顽冰，从而保证微通道换热器100的换热效果。
另外，翅片3在换热管2的宽度方向上至少与两个换热管2相连，用翅片将多个换热管2连接在一起，保证了微通道换热器100的结构强度。
可选地，每个翅片3均与其所在的管层20中所有换热管2相连，与翅片3相连的换热管2可通过翅片3连接成一体，结构牢固可靠。
在图1中，微通道换热器100包括三个换热管2，三个换热管2弯折后形成四排管层20，四排管层20之间的三个翅片3将这四排管层20连接在一起，每排管层20中相邻的翅片3与三个换热管2均连接在一起，位于最外侧的两个管层20的外侧也分别设有一个翅片3。这里由于管层20沿箭头Q所示方向间隔开分布，因此管层20的最外外层指的是多个管层20在沿Q所示方向的最外侧。
参照图1，翅片3上设有通风孔33，这样，吹入的空气可通过通风孔33穿过翅片3后吹入换热管2之间。这样，空气在流经最外侧的换热管2或者翅片3之后可以相互混合，一方面可以解决因某些翅片底部间隙被霜层堵塞后导致上部没有空气流通的问题，另一方面通过使流经换热器不同位置的空气混合，使得送风温度均匀，有助于提高箱温均匀性。
在本发明实施例中，部分换热管2的制冷剂流通阻力小于其余换热管2的制冷剂流通阻力。
可以理解的是，在微通道换热器运行时，迎风侧的换热管因与空气回风最先接触， 制冷剂与外部空气温差最大，因此换热量较大、换热比较充分。但是换热最充分的换热管内因两相段及过热段较长，制冷剂流动阻力较大，在制冷剂分配过程中，换热最充分的换热管反而制冷剂流量容易偏小，与此处换热量较大的特点反而相矛盾。
而本发明中将部分换热管2的制冷剂流通阻力设计得较小，然后将该换热管2设置在微通道换热器100运行时能最先与吹来的空气换热的位置，可减小制冷剂流经该换热管2内的压降，进而增大该换热管2的制冷剂流量，这样，可促使多个换热管2的制冷剂流量均匀，从而尽可能使制冷剂在多个换热管2内分液均匀，提高换热器整体换热量。
根据本发明实施例的微通道换热器100，通过在相邻管层20或者最外侧管层20的外侧设置翅片3，在换热管2的延伸方向上每个翅片3呈波纹状延伸，在集流管1的延伸方向上每个翅片3连续延伸，从而微通道换热器100在除霜过程中，翅片3表面霜化水可积聚成水滴，水滴可沿连续的翅片3顺畅地滑落并排走，解决了翅片3表面挂水量较大、无法排尽的问题，可防止微通道换热器100表面产生顽冰而影响换热效率。通过在翅片3上设置通风孔33，促进翅片不同位置处空气相互流动，防止翅片局部间隙被霜层堵塞导致的其他区域没有空气流通，从而增加换热器的整体换热量。通过将部分换热管2的制冷剂流通阻力设计得较小，该换热管2可设置在微通道换热器100的最先迎风处，从而促使多个换热管2的制冷剂流量均匀，提高换热器整体换热量。
将部分换热管2的制冷剂流通阻力设置成比其他换热管2的小，有多种方法。
在一些实施例中，可以将部分换热管2的管长设置成小于其余换热管2的管长。可以理解，在同样过流面积下，换热管2越短则流通阻力就越小，通过换热管2的长度差异化设计，容易实现制冷剂流通不同换热管时流通阻力不同。
具体地，在集流管1的延伸方向(箭头M所示方向)上，多个换热管2的管长依次递增或者依次递减，且每相邻的两个换热管2中，位于迎风侧的换热管2的管长小于位于背风侧的换热管2的管长。
这样的微通道换热器100，将通过各层制冷剂的换热管2的管长差异设定，减小各层换热管压降损失差异，使制冷剂流经各层换热管2的阻力基本相同，最终达到分液均匀的目的，从而进一步提高换热器整体换热量。
在一个具体示例中，换热管2为三个，在集流管1的延伸方向上，三个换热管2的管长比值为6:5:4。其中，管长最短的换热管2位于换热器的迎风侧，管长最大的换热管2位于换热器的背风侧。
在一个具体示例中，如图7-图9所示，换热管2为三个，微通道换热器100由下向上包括：第一换热管201、第二换热管202和第三换热管203，三个换热管2的管长比值为4:5:6，其中换热器运行时气流从下方吹向换热器，最下层的第一换热管201最长， 最上层的第三换热管203最短。
这三个换热管2均弯折了三次形成四个平直段211和三个弯曲段212，三个换热管2通过调整各自的平直段211的长度来使各自管长不等。
当然，本发明实施例中三个换热管2还可通过调整各自的弯折次数，来使各自管长不等。例如，如果第一换热管201包括两个平直段211和一个弯曲段212，而第三换热管203仍包括四个平直段211和三个弯曲段212，各换热管2的平直段211均等长，此时第一换热管201的管长约为第三换热管203的管长的一半。
可以理解的是，根据实际需要，换热管2的数量可变化，各换热管2的管长比值也可适应实际而变化。
在另一些实施例中，可以将部分换热管2的过流面积设计得大于其余换热管2的过流面积。可以理解，在同等管长下，换热管2的过流面积越大则制冷剂流通阻力就越小，通过换热管2的过流面积差异化设计，也容易实现制冷剂流通不同换热管时流通阻力不同。
在集流管1的延伸方向(箭头M所示方向)上，多个换热管2的过流面积依次递增或者依次递减，且每相邻的两个换热管2中，位于迎风侧的换热管2的过流面积大于位于背风侧的换热管2的过流面积。
这样的微通道换热器100，将通过各层制冷剂的换热管2的过流面积差异设定，减小各层换热管压降损失差异，最终达到进一步促使制冷剂在多个换热管2内分液均匀，从而进一步提高换热器整体换热量。
在一个具体示例中，如图1和图6所示，换热管2为三个，微通道换热器100由下向上包括：第一换热管201、第二换热管202和第三换热管203，三个换热管2的过流面积的比值为4:3:2，其中换热器运行时气流从下方吹向换热器，最下层的第一换热管201的过流面积最大，最上层的第三换热管203的过流面积最小。
具体地，如图6所示，每个换热管2内可限定出多个制冷剂的流通通道210，可以改变每个换热管2内流通通道210的横截面积大小、流通通道210的数量等，来改变各个换热管2的过流面积，使得各流路在换热过程中压降基本相同，尽量增加分液均匀性，提高换热性能。
可以理解的是，根据实际需要，换热管2的数量可变化，各换热管2的过流面积比值也可适应实际而变化。
在一些实施例中，通风孔33设在翅片3所在管层20的对应相邻两个扁管2之间的空隙处。这样通过通风孔33不仅可以将同一管层20的空间连通起来，还能将不同管层20的空间连通起来，使换热器不同位置的空气能够进一步充分混合，使得送风温度更加 均匀。
具体地，如图5所示，在集流管1的延伸方向(箭头M所示方向)上通风孔33的尺寸a为15-18毫米，在垂直于集流管1的延伸方向上通风孔33的尺寸b为4-7毫米。
如图3中通风孔33为方形孔，通风孔33的长度a在15-18毫米之间，通风孔33的宽度b在4-7毫米之间。当然，通风孔33也可形成其他形状，且通风孔33也可设计成其他尺寸。
具体地，如图3所示，通风孔33包括第一通风孔331和第二通风孔332，第一通风孔331为环形孔，第二通风孔332朝向M所示方向的一侧敞开。
在一些实施例中，如图1和图3所示，在换热管2的延伸方向(图1中箭头P所示方向)上，每个翅片3均包括交错连接的平行壁301和垂直壁302以形成锯齿形，平行壁301与换热管2的延伸方向相平行，垂直壁302与换热管2的延伸方向相垂直。也就是说，平行壁301沿方向P延伸，垂直壁302沿方向Q延伸。当翅片3位于相邻两个管层20之间时，平行壁301连接在管层20上，垂直壁302夹在两个管层20之间。此时，通风孔33可以设在垂直壁302上，这样可保证通风效果，同时也不会减小换热管2和翅片3之间的接触面积，不会影响换热管2向翅片3传热。
通风孔33可设置在翅片3的与换热管2不接触的位置处，这里对通风孔33的结构、位置不作限制。例如，当最外层管层20的外侧设有翅片3时，该翅片3上通风孔33可设在垂直壁302上，也可设在与管层20不接触的平行壁301上。
在一些实施例中，如图4所示，至少一个翅片3包括第一翅片段31和第二翅片段32，在集流管1的延伸方向(箭头M所示方向)上第一翅片段31的尺寸h1大于第二翅片段32的尺寸h2。这里将翅片3设置得有长有短，相当于在翅片3上形成有缺口，第二翅片段32比第一翅片段31短的部分构成上述缺口，缺口的设置是微通道换热器100针对结霜及化霜特点进行优化的设计结构。
具体而言，当微通道换热器100用于输出冷量时，空气可从对应微通道换热器100的该缺口处吹向微通道换热器100。由于空气吸收冷量后湿度降低，空气中的水汽容易凝结在微通道换热器100的表面形成霜层。而空气从缺口处吹风后，在缺口处没有翅片3的阻挡，空气能容易地吹入微通道换热器100的内部管层20之间，增大了霜层的分布空间，减小了翅片3底部霜层积聚量和速度，减小了结霜对微通道换热器100的性能影响，延长化霜周期。
具体地，如图4所示，每个翅片3均包括至少两个第一翅片段31和/或至少两个第二翅片段32，在换热管2的延伸方向(箭头P所示方向)上，第一翅片段31和第二翅片段32交错设置。这样设置，一方面避免翅片3结构强度降低，另一方面将翅片上缺口 间隔开，有利于微通道换热器100在结霜时霜层分散，从而化霜时能够更加快速去霜。
进一步地，当翅片3为多个时，多个翅片3上第二翅片段32对应设置。也就是说，当翅片3为多个时，在管层20所在的平面上，多个翅片3的投影形状大体相同，每个翅片3均在同一位置处形成缺口。这样多个翅片3的缺口位置一致，从而在提高微通道换热器100的换热效率的同时，可进一步增大霜层的分布空间，减小翅片3底部霜层积聚量和速度。
可选地，如图4所示，在集流管1的延伸方向(箭头M所示方向)上，第二翅片段32的尺寸h2为第一翅片段31的尺寸h1的0.67-0.75，也就是说，在集流管1的延伸方向上第二翅片段32比第一翅片段31短1/4-1/3。
可以理解的是，如果第二翅片段32过短，将会削弱翅片3在第二翅片段32处与管层2的连接强度，而如果第二翅片段32过长，又会对空气形成阻碍，综合考虑后优选第二翅片段32的尺寸h2为第一翅片段31的尺寸h1的0.67-0.75，可保证翅片3在全段均能顺畅排出化霜水，同时保证进风时霜层能均匀分布。
在一些实施例中，每个翅片3中第一翅片段31和第二翅片段32均与其所在的管层20中所有换热管2相连。
由于相邻两个换热管2之间是间隔开的，由翅片3将所有换热管2连接后，翅片3上的化霜水不会落到中间的换热管2上，微通道换热器100容易排尽化霜水。
具体地，如图5所示，在沿集流管1的延伸方向(箭头M所示方向)上，第二翅片段32的迎风侧与其所在的管层20上最外侧的换热管2之间的接触尺寸m为5-10毫米。也就是说，翅片3即使做了缺口设置，翅片3在缺口边缘的部分仍与最外侧的换热管2之间形成连接配合。
将第二翅片段32设计成迎风侧与最外侧的换热管2之间的接触尺寸m为5-10毫米，保证其与最外侧的换热管2相连接，防止翅片3悬空时翅片3上水滴不能顺流到最外侧的换热管2上。
在一些实施例中，微通道换热器100的管层20沿竖向设置，多个管层20沿水平方向间隔开排布。每个翅片3沿水平方向呈波纹状延伸，每个翅片3沿竖向连续延伸。翅片3在上端平齐，翅片3在下端形成缺口，翅片3分成第一翅片段31和第二翅片段32，其中，第二翅片段32与最下方的换热管2之间的接触高度m为5-10mm，该处翅片3与最下端的换热管2之间形成过盈配合。
进一步地，如图1所示，在换热管2的延伸方向(箭头P所示方向)上，每个翅片3均呈锯齿形延伸，如图4所示，相邻齿之间的间隙n为5-10毫米。其中，翅片3的齿间间隙n基本相同，各个翅片3的齿间间隙n的比值在110％-90％之间。
综上，根据本发明实施例的微通道换热器100，根据换热器上结霜及化霜特点进行了优化，通过贯穿多层管层20的翅片3、翅片3长度差异化、在翅片3表面开孔、及不同换热管过流面积或者管长的差异化设计，降低了平行流换热器换热量对表面霜层积聚的敏感性，减缓了换热器表面霜层积聚对系统运行的影响，同时有利于化霜水排尽，尽可能延长化霜周期，提升换热性能。
根据本发明实施例的冰箱(图未示出)，包括根据本发明上述实施例的微通道换热器100。可选地，微通道换热器100可用作冰箱的冷藏室或者变温室的蒸发器，微通道换热器100的结构已由上述实施例说明，这里不再赘述。
根据本发明实施例的冰箱，通过设置上述微通道换热器100，有利于化霜时微通道换热器100上化霜水排尽，防止微通道换热器100表面产生顽冰而影响换热效率。
在风冷冰箱中，风冷冰箱内限定出制冷间室和风道，风道具有用于从制冷间室进风的回风口，风冷冰箱包括根据本发明上述的翅片3包括第一翅片段31和第二翅片段32的所有实施例的微通道换热器100。
微通道换热器100的结构已由上述实施例说明，这里不再赘述。微通道换热器100可用作风冷冰箱的冷藏室或者变温室的蒸发器，微通道换热器100设在风道内，微通道换热器100可以在冷藏室或变温室的回风口上方布置较短的第二翅片段32，其他位置布置较长的第一翅片段31。
具体地，在风道内微通道换热器100，两个集流管1竖向设置，翅片3的第二翅片段32设置在回风口的上方。也就是说风冷冰箱在制冷时，制冷间室内空气从回风口吹向风道，吹入的风从微通道换热器100的底部吹入微通道换热器100。
翅片3在第二翅片段32比第一翅片段31短的部分相当于缺口，空气可从对应微通道换热器100的该缺口处吹向微通道换热器100。空气吸收冷量后湿度降低，空气中的水汽容易凝结在微通道换热器100的表面形成霜层。由于空气从缺口处吹向微通道换热器100，在缺口处没有翅片3的阻挡后，空气能容易地吹入微通道换热器100的内部管层20之间，增大了霜层的分布空间，减小了翅片3底部霜层积聚量和速度，减小了结霜对微通道换热器100的性能影响，延长化霜周期。
具体地，第二翅片段32的水平宽度w(图3中标示出)大体为回风口的水平宽度的1.1-1.4倍，这样，可使翅片3尽可能避开回风口，方便回风吹向微通道换热器100的内部。
进一步地，当微通道换热器100的最外层的管层20上设有翅片3时，微通道换热器100最外侧的翅片3直接裸漏，且翅片3外侧无护板保护。也就是说，最外侧的翅片3 不与其他部件相连，且没有防护设施，以减小其与制冷间室的箱胆和换热器的盖板接触，减小箱体漏冷量及换热器盖板表面结霜的可能。
根据本发明实施例的风冷冰箱，通过设置专门为单循环风冷冰箱设计的微通道换热器，具有以下特点：
1.使用整条平直翅片把3-4层平行的换热管管层连接到一块，减小化霜过程中翅片表面挂水量，防止换热器表面形成“顽冰”；
2.相邻两段翅片段长度比在75％-67％之间，可增大换热器底部迎风面翅片间隙，减小霜层积聚对冰箱送风量和送风温度的影响，延长化霜时间；
3.通过减短冷藏室和变温室回风口上方翅片长度，减小距回风口最近处霜层积累速度，减小霜层积聚对冷藏室和变温室的影响，延长化霜时间；
4.翅片3下边缘伸入或者伸出临近的换热管5-10mm，便于化霜水向下流，防止水滴在翅片端部积聚；
5.相邻两层换热管2之间的翅片3表面开孔，使得空气可以横向流动，防止因霜层堵塞底部翅片间隙导致上方没有空气流经翅片3，减小结霜对换热器换热影响；
6.为了缓解因换热管与回风接触先后，引起各层换热管道流动阻力不同，导致微通道换热器底部制冷剂流量偏小，微通道换热器不能充公发挥高效换热的现象，本发明实施例通过增大部分换热管的过流面积或者流路长度，尽可能使得流经各个换热管的制冷剂流量相同，减轻换热器分液不均的现象，提高了换热器的换热量；
7.两侧翅片3直接裸漏，没有保护层、加强板或支撑板，减小了保护层与箱胆接触带来的漏冷及换热器盖板结霜可能；
8该设计解决了微通道换热器100使用到风冷冰箱中存在的蒸发器换热效果对表面结霜量增加较为敏感的问题，充分发挥平行流换热器特点，增大冰箱容积率。
可以理解，冰箱内还设有压缩机、冷凝器等其他制冷系统的部件等，制冷系统结构及工作原理已为现有技术，另外微通道换热器100在冰箱的制冷系统中的连接结构也已为现有技术，这里不再赘述。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“高度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示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 或者隐含地包括一个或者更多个该特征。在本发明的描述中，除非另有说明，“多个”的含义是两个或两个以上。
在本发明的描述中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本发明中的具体含义。
在本说明书的描述中，参考术语“实施例”、“示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本发明的范围由权利要求及其等同物限定。

Claims (10)

  1. 一种微通道换热器，其特征在于，包括：
    两个集流管，所述两个集流管平行设置；
    多个换热管，所述多个换热管的两端分别连接所述两个集流管，所述多个换热管沿其长度方向弯折形成多个管层，部分所述换热管的制冷剂流通阻力小于其余所述换热管的制冷剂流通阻力；
    至少一个翅片，每个所述翅片设在相邻两个所述管层之间或设在最外层的所述管层的外侧，在所述换热管的延伸方向上每个所述翅片呈波纹状延伸，在所述集流管的延伸方向上每个所述翅片连续延伸，且每个所述翅片与其所在的所述管层中的至少两个所述换热管相连，所述翅片上设有通风孔。
  2. 根据权利要求1所述的微通道换热器，其特征在于，所述通风孔设在所述翅片所在的所述管层的相邻两个所述扁管之间的空隙处。
  3. 根据权利要求1或者2所述的微通道换热器，其特征在于，在所述集流管的延伸方向上所述通风孔的尺寸为15-18毫米，在垂直于所述集流管的延伸方向上所述通风孔的尺寸为4-7毫米。
  4. 根据权利要求1-3中任一项所述的微通道换热器，其特征在于，部分所述换热管的管长小于其余所述换热管的管长。
  5. 根据权利要求4所述的微通道换热器，其特征在于，在所述集流管的延伸方向上所述多个换热管的管长依次递增或者依次递减，且每相邻的两个所述换热管中位于迎风侧的换热管的管长小于位于背风侧的换热管的管长。
  6. 根据权利要求1-5中任一项所述的微通道换热器，其特征在于，部分所述换热管的过流面积大于其余所述换热管的过流面积。
  7. 根据权利要求6所述的微通道换热器，其特征在于，在所述集流管的延伸方向上所述多个换热管的过流面积依次递增或者依次递减，且每相邻的两个所述换热管中位于迎风侧的换热管的过流面积大于位于背风侧的换热管的过流面积。
  8. 根据权利要求1-7中任一项所述的微通道换热器，其特征在于，至少一个所述翅片包括第一翅片段和第二翅片段，在所述集流管的延伸方向上所述第一翅片段的尺寸大于所述第二翅片段的尺寸。
  9. 一种风冷冰箱，所述风冷冰箱内限定出制冷间室和风道，所述风道具有用于从所述制冷间室进风的回风口，其特征在于，所述风冷冰箱包括根据权利要求1-8中任一项所述的微通道换热器。
  10. 根据权利要求9所述的风冷冰箱，其特征在于，所述微通道换热器为根据权利要求8所述的微通道换热器，所述微通道换热器设在所述风道内，所述两个集流管竖向设置，所述翅片的所述第二翅片段设置在所述回风口的上方。
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113587251A (zh) * 2021-07-26 2021-11-02 青岛海信日立空调系统有限公司 空调器
CN114166583A (zh) * 2021-10-26 2022-03-11 楚天华通医药设备有限公司 风冷无菌纯蒸汽取样装置及取样方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010169289A (ja) * 2009-01-21 2010-08-05 Nikkei Nekko Kk 屈曲状熱交換器及びその製造方法
CN101858698A (zh) * 2009-04-10 2010-10-13 三花丹佛斯（杭州）微通道换热器有限公司 微通道热交换器
CN104864634A (zh) * 2015-06-16 2015-08-26 江苏启江实业有限公司 间冷冰箱用扁管穿片式易排水微通道蒸发器
CN204612254U (zh) * 2014-12-31 2015-09-02 浙江盾安热工科技有限公司 一种换热器
CN106288526A (zh) * 2016-08-31 2017-01-04 合肥美的电冰箱有限公司 微通道换热器及冰箱、风冷冰箱
CN106322850A (zh) * 2016-08-31 2017-01-11 合肥美的电冰箱有限公司 微通道换热器及冰箱、风冷冰箱
CN106403388A (zh) * 2016-08-31 2017-02-15 合肥美的电冰箱有限公司 微通道换热器及冰箱、风冷冰箱

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010169289A (ja) * 2009-01-21 2010-08-05 Nikkei Nekko Kk 屈曲状熱交換器及びその製造方法
CN101858698A (zh) * 2009-04-10 2010-10-13 三花丹佛斯（杭州）微通道换热器有限公司 微通道热交换器
CN204612254U (zh) * 2014-12-31 2015-09-02 浙江盾安热工科技有限公司 一种换热器
CN104864634A (zh) * 2015-06-16 2015-08-26 江苏启江实业有限公司 间冷冰箱用扁管穿片式易排水微通道蒸发器
CN106288526A (zh) * 2016-08-31 2017-01-04 合肥美的电冰箱有限公司 微通道换热器及冰箱、风冷冰箱
CN106322850A (zh) * 2016-08-31 2017-01-11 合肥美的电冰箱有限公司 微通道换热器及冰箱、风冷冰箱
CN106403388A (zh) * 2016-08-31 2017-02-15 合肥美的电冰箱有限公司 微通道换热器及冰箱、风冷冰箱

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113587251A (zh) * 2021-07-26 2021-11-02 青岛海信日立空调系统有限公司 空调器
CN114166583A (zh) * 2021-10-26 2022-03-11 楚天华通医药设备有限公司 风冷无菌纯蒸汽取样装置及取样方法

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