WO2018040036A1 - 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 PDFInfo
- Publication number
- WO2018040036A1 WO2018040036A1 PCT/CN2016/097688 CN2016097688W WO2018040036A1 WO 2018040036 A1 WO2018040036 A1 WO 2018040036A1 CN 2016097688 W CN2016097688 W CN 2016097688W WO 2018040036 A1 WO2018040036 A1 WO 2018040036A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchange
- heat exchanger
- fins
- fin
- tube
- Prior art date
Links
Images
Classifications
-
- 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 portion of the heat exchange tubes has a flow area larger than a flow area of the remaining heat exchange tubes; at least one fin, Each of the fins is disposed between adjacent two of the tube layers or outside the tube layer disposed at the outermost layer, and each of the fins is corrugated in a direction in which the heat exchange tubes extend Extendingly, each of the fins extends 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 fins are located, the fins Ventilation holes are provided on the sheet.
- 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 tube can be disposed at the first windward side of the microchannel heat exchanger, thereby promoting the refrigerant of the plurality of heat exchange tubes. The flow rate is uniform, and the overall heat exchange capacity of the heat exchanger is improved.
- the flow areas of the plurality of heat exchange tubes are sequentially increased or decreased sequentially in the extending direction of the header, and each of the two adjacent heat exchange tubes is located on the windward side.
- the flow area of the heat exchange tube 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.
- the heat exchange tubes are three, and the ratio of the flow areas of the three heat exchange tubes in the extending direction of the header is 2:3:4.
- 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.
- each of the fins includes staggered parallel walls and vertical walls to form a zigzag shape in an extending direction of the heat exchange tubes, the parallel walls and an extension of the heat exchange tubes The directions are parallel, the vertical wall is perpendicular to the extending direction of the heat exchange tube, and the venting holes are provided on the vertical wall. This can ensure the ventilation effect, and at the same time, it will not reduce the contact area between the heat exchange tube and the fin, and will not affect the heat transfer of the heat exchange tube to the fin.
- 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 size of the second fin segment is 0.67-0.75 of the size of the first fin segment.
- the first fin segment and the second fin segment of each of the fins are located therewith All of the heat exchange tubes in the tube layer are connected, and in the extending direction of the header tube, the windward side of the second fin segment and the outermost heat exchange tube on the tube layer where the tube layer is located
- the contact size between the 5-10 mm Therefore, it is ensured that the fins are in contact with the outermost heat exchange tubes, and the water droplets on the fins cannot be prevented from flowing down to the outermost heat exchange tubes when the fins are suspended, so that all the heat exchange tubes can be connected to the fins. ,fixed.
- 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
- the microchannel heat exchanger of the embodiment is 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 horizontal width of the second fin segment is substantially 1.1-1.4 times the horizontal width of the corresponding return air opening. In this way, the fins can be avoided as far as possible from the return air outlet, and the return air can be blown to the microchannel heat exchanger.
- FIG. 1 is a perspective view of a microchannel heat exchanger in accordance with an embodiment of the present invention.
- FIG. 2 is a top plan view of a microchannel heat exchanger in accordance with an embodiment of the present invention.
- 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 in accordance with an embodiment of the present invention.
- FIG. 6 is a cross-sectional enlarged enlarged view of three heat exchange tubes of a microchannel heat exchanger according to an embodiment of the present invention.
- 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 fin 3 is disposed between adjacent two tube layers 20 or outside the tube layer 20 of the outermost layer, which
- 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
- the outer side of the tube layer 20 is also provided with fins 3, 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 flow area of the partial heat exchange tubes 2 is larger than the flow area of the remaining heat exchange tubes 2.
- the heat exchange tube on the windward side is in contact with the air return air first, and 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 heat exchange tube with the most heat transfer 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 flow area of the partial heat exchange tube 2 is designed to be large, 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 is reduced, thereby increasing the refrigerant flow rate of the heat exchange tube 2, thereby increasing the heat exchange amount here.
- the refrigerant flow rate of the plurality of heat exchange tubes 2 can be made uniform, so that the refrigerant is uniformly distributed in the plurality of heat exchange tubes 2 as much as possible, and the overall heat exchange amount of the heat exchanger is improved.
- 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 heat exchange tubes 2 can be disposed at the first windward side of the microchannel heat exchanger 100, thereby promoting a plurality of heat exchanges.
- the refrigerant flow rate of the tube 2 is uniform, and the overall heat exchange amount of the heat exchanger is improved.
- the flow areas of the plurality of heat exchange tubes 2 are sequentially increased or decreased sequentially, and each adjacent two heat exchange tubes 2
- the flow area of the heat exchange tube 2 on the windward side 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 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 more uniform.
- 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 fin at the notch. 3, the air can be easily blown into the inner tube layer 20 of the microchannel heat exchanger 100, which increases the distribution space of the frost layer, reduces the accumulation amount and speed of the frost layer at the bottom of the fin 3, and reduces frosting. The performance of the microchannel heat exchanger 100 is affected, and the defrosting cycle is extended.
- 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 structural strength of the fins 3 is prevented from being lowered, and on the other hand, the gaps on the fins are spaced apart, which is advantageous for the microchannel heat exchanger 100 to disperse the frost layer during frosting, thereby enabling quicker defrost 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.
- Wing The sheet 3 is flush at the upper end, the fin 3 is notched at the lower end, and the fin 3 is divided into a first fin segment 31 and a second fin segment 32, wherein the contact between the second fin segment 32 and the lowermost heat exchange tube 2
- the height m is 5-10 mm, and an interference fit is formed between the fins 3 and the lowermost heat exchange tubes 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 differential design of the surface of the fin 3 and the different flow area of the heat exchange tube reduces the sensitivity of the heat exchange of the parallel flow heat exchanger to the accumulation of the frost layer on the surface, and slows down the accumulation of the frost layer on the surface of the heat exchanger.
- the impact of the system operation, at the same time is conducive to the exhaustion of defrosting water, as long as possible to extend the defrosting cycle and improve 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 amount and speed of frost layer accumulation at the bottom of the fin 3, and reduces the knot The effect of frost on the performance of the microchannel heat exchanger 100 extends 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 to say, the outermost fin 3 is not connected to other components, and there is no protective device to reduce the contact with the tank of the refrigerating compartment and the cover of the heat exchanger, thereby reducing the amount of leakage of the casing and changing The possibility of frost on the surface of the heater 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 cross-sectional area of the microchannels in the upper, middle and lower parallel heat exchange tubes 2 are designed to be different, and the ratio is approximately 2:3:4.
- the flow paths are
- the pressure drop in the heat exchange process is basically the same, the liquid separation uniformity is increased as much as possible, and the heat transfer performance is improved;
- 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” may include one or more of the features either explicitly or implicitly. 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.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims (12)
- 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,部分所述换热管的过流面积大于其余所述换热管的过流面积;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。
- 根据权利要求1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。
- 根据权利要求2所述的微通道换热器,其特征在于,所述换热管为三个,在所述集流管的延伸方向上三个所述换热管的过流面积的比值为2:3:4。
- 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,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。
- 根据权利要求1-4中任一项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。
- 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,在所述换热管的延伸方向上,每个所述翅片均包括交错连接的平行壁和垂直壁以形成锯齿形,所述平行壁与所述换热管的延伸方向相平行,所述垂直壁与所述换热管的延伸方向相垂直,所述通风孔设在所述垂直壁上。
- 根据权利要求1-6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。
- 根据权利要求7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,所述第二翅片段的尺寸为所述第一翅片段的尺寸的0.67-0.75。
- 根据权利要求7或者8所述的微通道换热器,其特征在于,每个所述翅片中所述第一翅片段和所述第二翅片段均与其所在的所述管层中所有所述换热管相连,在沿所述 集流管的延伸方向上,所述第二翅片段的迎风侧与其所在的所述管层上最外侧的所述换热管之间的接触尺寸为5-10毫米。
- 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1-9中任一项所述的微通道换热器。
- 根据权利要求10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7-9中任一项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。
- 根据权利要求11所述的风冷冰箱,其特征在于,所述第二翅片段的水平宽度大体为相应的所述回风口的水平宽度的1.1-1.4倍。
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CN2016/097688 WO2018040036A1 (zh) | 2016-08-31 | 2016-08-31 | 微通道换热器及风冷冰箱 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CN2016/097688 WO2018040036A1 (zh) | 2016-08-31 | 2016-08-31 | 微通道换热器及风冷冰箱 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2018040036A1 true WO2018040036A1 (zh) | 2018-03-08 |
Family
ID=61299636
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CN2016/097688 WO2018040036A1 (zh) | 2016-08-31 | 2016-08-31 | 微通道换热器及风冷冰箱 |
Country Status (1)
Country | Link |
---|---|
WO (1) | WO2018040036A1 (zh) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112179016A (zh) * | 2020-09-27 | 2021-01-05 | 海信容声(广东)冰箱有限公司 | 冰箱 |
CN114471409A (zh) * | 2022-01-28 | 2022-05-13 | 青岛科技大学 | 一种大通量双循环微通道反应器 |
Citations (6)
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 |
-
2016
- 2016-08-31 WO PCT/CN2016/097688 patent/WO2018040036A1/zh active Application Filing
Patent Citations (6)
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 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112179016A (zh) * | 2020-09-27 | 2021-01-05 | 海信容声(广东)冰箱有限公司 | 冰箱 |
CN114471409A (zh) * | 2022-01-28 | 2022-05-13 | 青岛科技大学 | 一种大通量双循环微通道反应器 |
CN114471409B (zh) * | 2022-01-28 | 2023-08-25 | 青岛科技大学 | 一种大通量双循环微通道反应器 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9651317B2 (en) | Heat exchanger and air conditioner | |
CN108139089B (zh) | 空气调节机的室外机及室内机 | |
US20130220584A1 (en) | Heat exchanger, and all-in-one air conditioner equipped therewith | |
US20150068244A1 (en) | Heat exchanger and air-conditioning apparatus | |
US20110232884A1 (en) | Heat exchanger | |
EP3156752B1 (en) | Heat exchanger | |
JP2012163328A5 (zh) | ||
WO2015004720A1 (ja) | 熱交換器、及び空気調和機 | |
JP5009413B2 (ja) | 熱交換器及びそれを搭載した空気調和機 | |
CN102748903B (zh) | 换热器及其扁平换热管 | |
JP6157593B2 (ja) | 熱交換器およびこれを用いた冷凍サイクル空調装置 | |
WO2018040036A1 (zh) | 微通道换热器及风冷冰箱 | |
EP3608618B1 (en) | Heat exchanger and refrigeration cycle device | |
WO2018040037A1 (zh) | 微通道换热器及风冷冰箱 | |
JP2014137177A (ja) | 熱交換器および冷凍装置 | |
WO2018040035A1 (zh) | 微通道换热器及风冷冰箱 | |
JP5940895B2 (ja) | パラレルフロー型熱交換器及びそれを搭載した空気調和機 | |
JP5404571B2 (ja) | 熱交換器及び機器 | |
WO2018040034A1 (zh) | 微通道换热器及风冷冰箱 | |
US20210180878A1 (en) | Heat exchanger, heat exchanger unit, and refrigeration cycle apparatus | |
CN109813146A (zh) | 用于换热器的翅片、换热器及空调室外机 | |
CN106440324B (zh) | 一种换热器及采用其的空调 | |
CN106403389A (zh) | 微通道换热器及冰箱、风冷冰箱 | |
JP2012026600A (ja) | 空気調和機の室内機 | |
JP2016017695A (ja) | フィンチューブ熱交換器 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 16914602 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 16914602 Country of ref document: EP Kind code of ref document: A1 |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 16914602 Country of ref document: EP Kind code of ref document: A1 |
|
32PN | Ep: public notification in the ep bulletin as address of the adressee cannot be established |
Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 10/12/2019) |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 16914602 Country of ref document: EP Kind code of ref document: A1 |