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WO2022036835A1 - 一种空调器 - Google Patents

一种空调器 Download PDF

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Publication number
WO2022036835A1
WO2022036835A1 PCT/CN2020/122468 CN2020122468W WO2022036835A1 WO 2022036835 A1 WO2022036835 A1 WO 2022036835A1 CN 2020122468 W CN2020122468 W CN 2020122468W WO 2022036835 A1 WO2022036835 A1 WO 2022036835A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
communicated
flat tubes
mixing chamber
air conditioner
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2020/122468
Other languages
English (en)
French (fr)
Inventor
田伟
张赫男
曹法立
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Original Assignee
Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Qingdao Hisense Hitachi Air Conditioning System Co Ltd filed Critical Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority to CN202080100396.0A priority Critical patent/CN115427736B/zh
Publication of WO2022036835A1 publication Critical patent/WO2022036835A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle

Definitions

  • the present application relates to the technical field of refrigeration equipment, and in particular, to an air conditioner with uniform distribution of refrigerants.
  • the heat pump air conditioner is a kind of heating and cooling air conditioner that is often used.
  • the air conditioner cools indoors and dissipates heat outdoors, and when heating in winter, the direction is opposite to that in summer, that is, indoor heating and outdoor cooling.
  • Air conditioners exchange heat and cold between different environments through heat pumps. For example, in winter, outdoor air, ground water, groundwater, etc. are low-temperature heat sources, while indoor air is a high-temperature heat source.
  • the function of heat pump air conditioning is to transfer heat from the outdoor environment to the indoor environment.
  • the application provides an air conditioner, comprising:
  • a heat exchange circuit for exchanging heat between indoors and outdoors is provided with a heat exchanger, and the heat exchanger includes:
  • a distributor for evenly distributing the gas-liquid two-phase refrigerant into the plurality of flat tubes, and the distributor is formed with:
  • a return cavity which is communicated with the mixing cavity, and part of the refrigerant in the mixing cavity can be returned to the mixing cavity through the return cavity;
  • a plurality of shunt sections are in one-to-one correspondence with a plurality of the flat tubes, and the inlets of the plurality of shunt sections communicated with the plurality of the flat tubes arranged below are communicated with the mixing chamber, and are connected with the upper section.
  • the inlets of the plurality of branching sections communicated with the plurality of the flat tubes are communicated with the return cavity.
  • Fig. 1 is the principle schematic diagram of a kind of air conditioner
  • FIG. 2 is a schematic structural diagram of a heat exchanger according to some embodiments of the present application.
  • FIG. 3 is a schematic structural diagram of a dispenser according to some embodiments of the present application.
  • Fig. 4 is the schematic diagram of the structure shown in Fig. 3 after the outer wall is made transparent;
  • Fig. 5 is the schematic diagram that Fig. 4 observes from Q direction;
  • Fig. 6 is A-A sectional view in Fig. 3;
  • Fig. 7 is the enlarged view of C part in Fig. 6;
  • Fig. 8 is a sectional view taken along the direction B-B in Fig. 3;
  • Fig. 9 is the enlarged view of D part in Fig. 8.
  • FIG. 10 is a schematic cross-sectional view of a mixing chamber, a recirculation chamber, and a partition portion according to some embodiments of the present application;
  • FIG. 11 is a schematic diagram of a refrigerant cycle of a mixing chamber, a return chamber, and a partition portion according to some embodiments of the present application.
  • the air conditioner in some embodiments of the present application includes a heat exchange circuit for exchanging heat between indoors and outdoors, so as to realize the regulation of the indoor temperature by the air conditioner.
  • the heat pump includes: an evaporator 1 , a compressor 2 , a condenser 3 , an expansion valve 4 and a four-way reversing valve 5 .
  • the specific working process of the heat pump heating is as follows: first, the low-pressure two-phase refrigerant (a mixture of liquid-phase refrigerant and gas-phase refrigerant) in the evaporator 1 absorbs heat from the low-temperature environment; high-pressure gas refrigerant; then, the high-temperature and high-pressure gas refrigerant releases heat energy to the indoor environment in the condenser 3, while its own temperature decreases; finally, it is throttled through the expansion valve mechanism 4 and becomes a low-temperature and low-pressure two-phase refrigerant, Enter the evaporator 1 again, and repeat the heating process of the above cycle.
  • the low-pressure two-phase refrigerant a mixture of liquid-phase refrigerant and gas-phase refrigerant
  • the heat pump air conditioner changes the working mode through the four-way reversing valve 5 .
  • the indoor heat exchanger is used as the evaporator 1
  • the outdoor heat exchanger is used as the condenser 3.
  • the indoor air is cooled down through the surface of the evaporator 1 to achieve the purpose of lowering the indoor temperature, and the heat is transported to the outdoors through the condenser 3 .
  • the position of the valve block of the four-way reversing valve 5 is changed to change the flow direction of the refrigerant.
  • the refrigerant absorbs the heat in the environment through the outdoor heat exchanger and releases heat to the indoor environment to achieve heating purpose.
  • Evaporator 1 is a device that outputs cooling capacity, and its function is to evaporate the refrigerant liquid flowing in through expansion valve 4 to absorb the heat of the object to be cooled and achieve the purpose of refrigeration.
  • the condenser 3 is a device for outputting heat. The heat absorbed from the evaporator 1 and the heat converted from the work consumed by the compressor 2 are taken away by the cooling medium in the condenser 3 to achieve the purpose of heating.
  • the micro-channel heat exchanger is used as an evaporator, when the gas-liquid two-phase refrigerant enters the multiple flat tubes from the inner cavity of the distributor, due to the difference in the density and viscosity of the gas phase and the liquid phase, the flowing refrigerant is easily affected by gravity and pressure.
  • the microchannel heat exchanger of the insert type the distributor is designed to be installed in a vertical or vertically inclined installation direction, which increases the difficulty of flow splitting. Uneven refrigerant not only deteriorates the heat exchange efficiency, but also causes fluctuations in the refrigeration system. Therefore, it is an important issue to realize the uniform distribution of the two-phase refrigerant in different flat tubes in the same process.
  • the heat exchange circuit can adopt the heat exchange principle shown in FIG. 1 , that is, the heat exchange circuit includes an evaporator 1 , a compressor 2 , a condenser 3 , an expansion valve 4 and a four-way exchanger To valve 5, the phase transition process of the refrigerant in the evaporator 1 and the condenser 3 is reversed, and the evaporator 1 and the condenser 3 are collectively referred to as heat exchangers.
  • One of the purposes of the present application is to improve the structure of the heat exchanger, improve the balanced distribution of refrigerant in the heat exchanger, improve the heat exchange effect of the heat exchanger, and further improve the overall heat exchange effect of the air conditioner.
  • the heat exchanger in some embodiments of the present application is a micro-channel heat exchanger, and the heat exchanger includes a plurality of flat tubes 40 and fins 50 arranged at equal intervals.
  • the flat tubes 40 are formed with A plurality of micro-channels for circulating refrigerant, the fins 50 are arranged between two adjacent flat tubes 40, and the flow direction of the air flowing through the fins 50 and the flow direction of the refrigerant flowing through the flat tubes 40 are perpendicular to each other , the heat/cold energy released by the refrigerant in the flat tube 40 is taken away through the cooling fins and the air flow.
  • the flat tube 40 samples porous micro-channel aluminum alloy, and the fins 50 are aluminum alloys with brazing composite layers on the surface, which are light in weight and high in heat exchange efficiency.
  • the heat exchanger further includes a flow divider 20 , a header 30 and a distributor 40 .
  • the refrigerant liquid entering from the flow divider 20 is evenly distributed to the flat tubes 40 in the first flow, and then collected by the header 30 .
  • the gas-liquid two-phase refrigerant collected by the header 30 enters the flat tube 40 in the second process through the distributor 10 .
  • the gas-liquid two-phase refrigerant is evenly distributed into each flat tube 40 in the second process by the distributor 10 , and heat is exchanged through the fins 50 .
  • the refrigerant in the flat tube 40 of the second process changes into gaseous refrigerant after heat exchange, and the gaseous refrigerant is discharged through the gas pipe 70 .
  • the present application focuses on the structural improvement of the distributor 10 in the heat exchanger to improve the uniformity of the refrigerant entering the flat tubes 40 of the second flow.
  • the distributor 10 is formed with a mixing chamber 100 , a return chamber 200 and a plurality of diverting sections 400 .
  • the mixing chamber 100 is communicated with the external refrigeration pipeline 60 , and the gas-liquid two-phase refrigerant in the refrigeration pipeline 60 flows into the mixing chamber 100 .
  • the return chamber 200 is in communication with the mixing chamber 100 , and part of the refrigerant in the mixing chamber 100 can be returned to the mixing chamber 100 through the return chamber 200 .
  • the plurality of branching sections 400 are in one-to-one correspondence with the plurality of flat tubes 40 in the second process.
  • the plurality of flat tubes 40 are arranged at intervals in the vertical direction, and the inlets of the plurality of branch sections 400 communicated with the plurality of flat tubes 40 arranged below communicate with the mixing chamber 100 and communicate with the plurality of flat tubes 40 arranged above The inlets of the plurality of branching sections 400 communicate with the reflux chamber 200 .
  • the number of flat tubes that can be carried by the distributor 10 in some embodiments of the present application is 2-100.
  • 7 flat tubes are used as an example for description in the following and related drawings.
  • the seven flat tubes are sequentially labeled as the first flat tube 41 , the second flat tube 42 , the third flat tube 43 , the fourth flat tube 44 , the fifth flat tube 45 , the sixth flat tube 46 and the seventh flat tube Tube 47.
  • first flat tubes 41 to the seventh flat tubes 47 are arranged in an upward interval in sequence, the first flat tubes 41 are located at the lowest position, and the seventh flat tubes 47 are located at the highest position.
  • the splitting sections 400 corresponding to the seven flat tubes are marked as the first splitting section 401 , the second splitting section 402 , the third splitting section 403 , the fourth splitting section 404 , and the fifth splitting section 405 , the sixth splitting section 406 and the seventh splitting section 407 .
  • the distributor 10 adopts the method of backflow, so that the gas-liquid two-phase refrigerant is impinged, mixed and circulated in the mixing chamber 100, so as to avoid the phenomenon of gas-liquid separation.
  • the split flow The higher the height of the segment 400 is, the greater the flow resistance of the refrigerant (mainly referring to the liquid refrigerant) in the splitting segment 400 under the influence of gravity.
  • the flow velocity of the liquid refrigerant will gradually decrease due to the influence of gravity. This will lead to the fact that under the influence of gravity, the flow rates of the liquid refrigerant entering into different flat tubes 40 are different, and the flow rates of the liquid refrigerant entering into the low-level flat tubes 40 are different.
  • the flow rate of the liquid refrigerant in the tube 40 is greater than the flow rate of the liquid refrigerant in the flat tube 40 located at a high position. Since the heat exchange of the heat exchanger mainly relies on the liquid refrigerant, this will eventually lead to uneven heat exchange of the heat exchanger. sex.
  • the distributor 10 is based on sampling the above-mentioned backflow method, according to the different flow resistance of the refrigerant (mainly refers to the liquid refrigerant) in the branching section 400 communicated with the flat tubes 40 at different heights.
  • different flow channels referring to the mixing cavity 100 and the return cavity 200
  • the flow rate of the gas-liquid two-phase refrigerant in the mixing chamber 100 is smaller than that of the gas-liquid two-phase refrigeration in the reflux chamber 200 agent flow.
  • the flow rate of the gas-liquid two-phase refrigerant entering the first splitting section 401 to the third splitting section 403 is smaller than that entering the fourth splitting section
  • the flow rate of the gas-liquid two-phase refrigerant in the section 404 to the seventh splitting section 407 Since the heights of the first splitting section 401 to the third splitting section 403 are smaller than the heights of the fourth splitting section 404 to the seventh splitting section 407 , they will eventually enter the first flat tube 41 to the seventh flat tube 47 under the influence of gravity. The liquid refrigerant flow is consistent.
  • FIGS. 4 and 5 are schematic views of the outer side wall of the dispenser 10 shown in FIG. 3 after transparent treatment
  • FIGS. 6 and 8 are schematic cross-sectional views of the dispenser 10 shown in FIG.
  • the structures of the cavity 100 , the reflux cavity 200 and the flow splitting section 400 are clearly and intuitively illustrated.
  • the mixing chamber 100 and the reflux chamber 200 are separated by a partition plate 300 , and the partition plate 300 is provided with a first through port 310 and a second through port 320 .
  • the refrigerant in the mixing chamber 100 can flow into the recirculation cavity 200 through the first port 310 , and the refrigerant in the recirculation cavity 200 can flow into the mixing cavity 100 through the second port 320 . Circulation flow between chambers 200 .
  • the area of the second through port 320 is smaller than that of the first through port 310 , so that the refrigerant flowing from the second through port 320 to the mixing chamber 100 is accelerated and the refrigerant in the mixing chamber 100 is enhanced. Impact effect, improve the uniformity effect of mixing.
  • the bottoms of the first through holes 310 are flush with the bottoms of the second through holes 320 , which helps to improve the refrigerant reflux effect.
  • the mixing chamber 100 and the recirculation chamber 200 are symmetrically arranged cavity structures relative to the partition plate 300 , the mixing chamber 100 has a first top wall 510 , the recirculation chamber 200 has a second top wall 520 , and the first Both the top wall 510 and the second top wall 520 are inclined downward from the top end of the partition plate 300 .
  • a refrigerant inlet 110 is provided on the side wall of the mixing chamber 100 , and the refrigeration line 60 communicates with the refrigerant inlet 110 .
  • the axis of the refrigerant inlet 110 and the axis of the second port 320 are on the same horizontal plane, and the direction in which the refrigerant flows from the refrigerant inlet 110 is perpendicular to the direction in which the refrigerant flows from the second port 320 .
  • the refrigerant flowing into the mixing chamber 100 from the second port 320 has the maximum jet impact effect on the refrigerant flowing into the mixing chamber 100 from the refrigerant inlet 110, which helps to further improve the mixing uniformity of the refrigerant.
  • the cavity enclosed by the mixing cavity 100 and the return cavity 200 extends in a horizontal direction.
  • the baffle 300 extends along the length direction of the cavity.
  • a first through port 310 is formed between one end of the baffle 300 away from the refrigerant inlet 110 and the side wall of the cavity.
  • a second through opening 320 is formed between the side walls.
  • the inlets 430 of the plurality of shunt sections communicated with the plurality of flat tubes 40 arranged below are equidistantly provided on the first top wall 510 of the mixing chamber 100, and the inlets 430 communicated with the plurality of flat tubes 40 arranged above are arranged at equal distances.
  • the inlets 430 of the two diverting sections are equidistantly disposed on the second top wall 520 of the reflux chamber 200 .
  • the inlets of the first splitting section 401 to the third splitting section 403 are equidistantly provided on the first top wall 510 of the mixing chamber 100 , and the fourth splitting section 404 to the seventh splitting section The inlet of 407 is provided on the second top wall 520 of the reflux chamber 200 .
  • the inlet areas of the plurality of flow splitting sections 400 communicated with the mixing chamber 100 decrease sequentially.
  • the heights of the small, diverting sections 400 decrease sequentially.
  • the inlet of the first splitting section 401 is located on the side away from the refrigerant inlet 110
  • the third splitting section 403 is located on the side close to the refrigerant inlet 110
  • the third splitting section 403 , the inlet area and height of the second splitting section 402 and the first splitting section 401 decrease sequentially.
  • the flow resistance of the refrigerant under the influence of gravity also decreases sequentially, which enables the flow of the liquid refrigerant that finally enters the first flat tubes 41 to the third flat tubes 43 to reach a consistent state.
  • the gas-liquid two-phase refrigerant enters the reflux chamber 200 through the first port 310 and flows to the second port 320, since the area of the second port 320 is smaller than that of the first port 310, a large amount of refrigerant is generated.
  • the refrigerant may accumulate in the return chamber 200 near the second port 320 . That is to say, the flow rate of the refrigerant on the side close to the second port 320 in the return chamber 200 is greater than the flow rate of the refrigerant on the side close to the first port 310 .
  • the inlet areas of the plurality of split sections 400 connected to the reflux chamber 200 are sequentially reduced and split.
  • the heights of the segments 400 increase sequentially.
  • the inlet of the fourth splitting section 404 is located on the side close to the first through port 310
  • the inlet of the seventh splitting section 407 is located on the side close to the second through port 320
  • the first The inlet area of the four-split section 404 to the seventh split section 407 decreases sequentially, and the height increases sequentially.
  • a plurality of flow splitting sections 400 (The total inlet area of the first splitting section 401 to the third splitting section 403) is S1, and the total area of the inlets of the plurality of splitting sections 400 (the fourth splitting section 404 to the seventh splitting section 407) communicating with the reflux chamber 200 is S2 , S1>S2, so that the refrigerant flows into the first flat tube 41 to the seventh flat tube 47 are consistent, and the uniform distribution of the refrigerant is realized, and the heat exchange uniformity of the heat exchanger is finally realized.
  • the first splitting section 401 to the third splitting section 403 are disposed on the first top wall 510 of the mixing chamber 100 at equal distances, and the inlet width of the first splitting section 401 is 4/5 times the width of the first
  • the width W1 of the top wall 510 is equal to the width W1 of the first top wall 510 .
  • the fourth split section 404 to the seventh split section 407 are equidistantly disposed on the second top wall 520 of the reflux chamber 200, and the inlet width of the fourth split section 404 is 1/2 times the width W2 of the second top wall 520.
  • the inlet width of the seven-split section 407 is 1/4 times the width W2 of the second top wall 520 .
  • the diversion section 400 includes a communication diversion vertical section 410 and a diversion horizontal section 420 , and the inlets of the diversion vertical section 410 are provided on the first top wall 510 and the second top wall On 520 , the outlet of the split horizontal section 420 is communicated with the corresponding flat tube 40 .
  • the plurality of split vertical sections 410 communicated with the mixing chamber 100 are arranged at equal intervals along the length direction of the mixing chamber 100 , and the multiple split vertical sections 410 communicated with the return chamber 200 are equally spaced along the length direction of the reflux chamber 200 . interval setting.
  • the relative magnitude of fluid inertial force and gravity is characterized.
  • Fr>1 the inertial force of the fluid in the split vertical section 410 can overcome its gravity and drive the fluid to flow upward, so the width of the split vertical section 410 needs to be limited.
  • the width of the diverting vertical section 410 is 0.2-1.5 mm.
  • the width of the diverting vertical section 410 is 1 mm.
  • the distance interval between two adjacent vertical splitting sections 410 is 1-10 times the width of the vertical splitting section 410 .
  • the distance interval between two adjacent vertical splitting sections 410 is three times the width of the vertical splitting section 410 .
  • the distance between the inlet of the fourth split section 404 and the refrigerant inlet 110 is 1-20 times the width of the split vertical section 410 .
  • the distance between the inlet of the fourth split section 404 and the refrigerant inlet 110 is 7 times the width of the split vertical section 410 .
  • the heat exchanger further has a plurality of gas pipes 70 , which are in one-to-one correspondence with the plurality of flat pipes 40 , and gaseous refrigerant circulates in the gas pipes 70 .
  • a gas collecting channel 600 is formed in the distributor 10 , and the gas collecting channel 600 communicates with the plurality of gas pipes 70 .
  • the refrigerant in each flat tube 40 changes into gaseous refrigerant after heat exchange, the gaseous refrigerant flows into the corresponding gas pipe 70 , and the gaseous refrigerant flows into the gas collecting channel 600 along the gas pipe 70 , and then flows from the gas collecting channel 600 discharge.
  • the distributor 10 integrates the gas collecting function, and it is unnecessary to configure an additional gas collecting pipe in the heat exchanger, which greatly reduces the overall volume of the heat exchanger, thereby helping to realize the miniaturized design of the air conditioner.
  • a plurality of flat tubes 40 and a plurality of air tubes 70 are arranged at equal intervals in the vertical direction, and the air tubes 70 are located above the corresponding flat tubes 40 communicated therewith.
  • the gaseous refrigerant floats up, and the gas pipe 70 is arranged above the flat tube 40 to facilitate the flow of the gaseous refrigerant.
  • the distributor 10 is provided with an air outlet line 80 , and the air collection channel 600 is communicated with the air outlet line 80 , so that the gaseous refrigerant in the air collection channel 600 can pass through the air outlet line 80 . discharge.
  • the gas collecting channel 600 includes a main channel 610 and a plurality of branch channels 620 communicating with the main channel 610 , the plurality of branch channels 620 are in one-to-one correspondence with the plurality of air pipes 70 , and the main channel 610 is connected with the air outlet pipeline. 80 is connected to facilitate the collection and discharge of gaseous refrigerant.
  • the processing technology of the distributor 10 is also improved.
  • the distributor 10 is formed by welding a plurality of laminations, and different laminations are formed with different contours.
  • the distributor is formed as a whole, and the mixing chamber 100 , the return chamber 200 , the baffle 300 , the first port 310 , the second port 320 , and the diverter section 400 are surrounded by different laminations to form the internal related structures of the distributor.
  • the width of each lamination is 0.5-2 mm.
  • the width of each lamination is 1 mm.
  • the processing technology of stacking and welding a plurality of laminations can eliminate the problem of easy deformation of the dispenser made by the stamping process in the prior art.
  • the laminations are made of aluminum alloy laminations with solder, and surface welding is used during welding, which can effectively eliminate problems such as refrigerant leakage caused by poor welding.

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Abstract

一种空调器，其内设置的换热器包括有分配器（10），分配器（10）用于将气液两相制冷剂均匀分配至多个扁管（40）内。分配器（10）内形成有混合腔（100）、回流腔（200）以及多个分流段（400），混合腔（100）内流通由制冷管路（60）输入的气液两相制冷剂，回流腔（200）与混合腔（100）连通，混合腔（100）内的部分制冷剂可经回流腔（200）回流至混合腔（100），多个分流段（400）与多个扁管（40）一一对应连通，与靠下设置的多个扁管（40）所连通的多个分流段（400）的入口与混合腔（100）连通，与靠上设置的多个扁管（40）所连通的多个分流段（400）的入口与回流腔（200）连通。上述结构能够提高制冷剂在换热器内的均衡分配，提高换热器的换热效果。

Description

一种空调器
本申请要求在2020年8月20日提交中国专利局、申请号为202010843452.1、发明名称为“一种空调器”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及制冷设备技术领域，尤其涉及一种制冷剂分配均匀的空调器。
背景技术
目前，热泵型空调是经常使用的一种冷暖空调。在夏季制冷时，空调在室内制冷，室外散热，而在冬季制热时，方向同夏季相反，即室内制热，室外制冷。空调通过热泵在不同环境之间进行冷热交换。比如在冬季，室外的空气、地面水、地下水等等就是低温热源，而室内空气就是高温热源，热泵式空调制热的作用就是把室外环境的热量输送到室内环境里。
发明内容
本申请提供了一种空调器，包括：
换热回路，用于进行室内与室外的热量交换，所述换热回路上设有换热器，所述换热器包括：
多个扁管，其内流通制冷剂，多个所述扁管沿竖直方向依次间隔设置；
分配器，用于将气液两相制冷剂均匀分配至多个所述扁管内，所述分配器内形成有：
混合腔，其内流通由制冷管路输入的气液两相制冷剂；
回流腔，其与所述混合腔连通，所述混合腔内的部分制冷剂可经所述回流腔回流至所述混合腔；
多个分流段，其与多个所述扁管一一对应连通，与靠下设置的多个所述扁管所连通的多个所述分流段的入口与所述混合腔连通，与靠上设置的多个 所述扁管所连通的多个所述分流段的入口与所述回流腔连通。
附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作一简单地介绍，显而易见地，下面描述中的附图是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动性的前提下，还可以根据这些附图获得其他的附图。
图1为一种空调器的原理示意图；
图2为根据本申请一些实施例的换热器的结构示意图；
图3为根据本申请一些实施例的分配器的结构示意图；
图4为图3所示结构将外壁做透明处理后的示意图；
图5为图4从Q向观察到的示意图；
图6为图3中A-A向剖视图；
图7为图6中C部放大图；
图8为图3中B-B向剖视图；
图9为图8中D部放大图；
图10为根据本申请一些实施例的混合腔、回流腔以及隔板部分的剖视示意图；
图11为根据本申请一些实施例的混合腔、回流腔以及隔板部分的制冷剂循环示意图。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
本申请的一些实施例中的空调器包括换热回路，用于进行室内与室外的 热量交换，以实现空调器对室内温度的调节。
参照图1所示，示出了一种热泵的制热循环原理图。该热泵包括：蒸发器1、压缩机2、冷凝器3、膨胀阀4和四通换向阀5。该热泵制热的具体工作过程为：首先，蒸发器1内低压两相制冷剂(液相制冷剂和气相制冷剂的混合体)从低温环境吸收热量；经压缩机2吸入后被压缩为高温高压的气体制冷剂；然后，高温高压的气体制冷剂在冷凝器3将热能释放给室内环境，同时自身温度降低；最后，经过膨胀阀机构4节流，变为低温低压的两相制冷剂，再次进入蒸发器1，重复上述循环的制热过程。
热泵空调通过该四通换向阀5来改变工况模式。在夏季制冷工况下，室内换热器作为蒸发器1，室外热交换器作为冷凝器3。室内空气经过蒸发器1表面被冷却降温，达到使室内温度下降的目的，通过冷凝器3将热量输送到室外。冬季供热的时候，转换四通换向阀5阀块的位置，使制冷剂的流向发生转换，此时，制冷剂通过室外换热器吸收环境中的热量，并向室内环境放热，实现制热的目的。
蒸发器1是输出冷量的设备，它的作用是使经膨胀阀4流入的制冷剂液体蒸发，以吸收被冷却物体的热量，达到制冷的目的。冷凝器3是输出热量的设备，从蒸发器1中吸收的热量连同压缩机2消耗功所转化的热量在冷凝器3中被冷却介质带走，达到制热的目的。微通道换热器用作蒸发器时，当气液两相制冷剂从分配器的内腔进入多根扁管时，由于气相和液相的密度与粘度存在差异，流动的制冷剂容易在重力和粘性力作用下发生分离，导致进入多根扁管的制冷剂不均匀。特别是插片式微通道换热器，分配器设计成竖直或者竖直倾斜的安装方向，使得分流难度增大。制冷剂不均匀不仅恶化换热效率，而且会引起制冷系统的波动。因此，实现两相制冷剂在同一流程不同扁管内部的均匀分配是一个重要课题。
在本申请的一些实施例中，换热回路可采用图1中所示的换热原理，也即，换热回路包括蒸发器1、压缩机2、冷凝器3、膨胀阀4以及四通换向阀5，蒸发器1和冷凝器3内的制冷剂相变过程相反，将蒸发器1和冷凝器 3统称为换热器。
本申请的目的之一在于对换热器进行结构改进，提高制冷剂在换热器内的均衡分配，提高换热器的换热效果，进而提高空调器整体的换热效果。
[换热器]
参照图2和图3，本申请的一些实施例中的换热器为微通道换热器，换热器包括有若干等距排布的扁管40和翅片50，扁管40内形成有多个用于流通制冷剂的微通道，翅片50设于相邻的两个扁管40之间，流经翅片50的空气流动方向与流经扁管40的制冷剂的流动方向相互垂直，通过散热翅片和空气流带走扁管40内制冷剂释放的热量/冷量。
扁管40采样多孔微通道铝合金，翅片50为表面具有钎焊复合层的铝合金，质量轻、换热效率高。
换热器还包括分流器20、集流管30以及分配器40，从分流器20进入的制冷剂液体均匀地分配至第一流程中的扁管40，之后由集流管30收集。集流管30收集到的气液两相制冷剂由分配器10进入到第二流程中的扁管40内。在第二流程中，由分配器10将气液两相制冷剂均匀分配至第二流程各个扁管40内，并通过翅片50进行换热。第二流程扁管40内的制冷剂换热后变为气态制冷剂，气态制冷剂经气管70排出。
[分配器]
本申请着重对换热器中的分配器10进行结构改进，提高进入第二流程扁管40内制冷剂的均匀性。
参照图4至图11，分配器10内形成有混合腔100、回流腔200以及多个分流段400。
混合腔100与外部制冷管路60连通，制冷管路60内的气液两相制冷剂流入混合腔100内。
回流腔200与混合腔100连通，混合腔100内的部分制冷剂可经回流腔200回流至混合腔100。
多个分流段400与第二流程内的多个扁管40一一对应连通。
多个扁管40沿竖直方向间隔设置，与靠下设置的多个扁管40所连通的多个分流段400的入口与混合腔100连通，与靠上设置的多个扁管40所连通的多个分流段400的入口与回流腔200连通。
本申请的一些实施例中的分配器10能够搭载的扁管数量为2-100个，为了便于描述，下文以及相关附图中以7个扁管为例进行阐述。
参照图3，7个扁管依次标记为第一扁管41、第二扁管42、第三扁管43、第四扁管44、第五扁管45、第六扁管46以及第七扁管47。
沿竖直方向，第一扁管41至第七扁管47依次向上间隔设置，第一扁管41位于最低位，第七扁管47位于最高位。
参照图4和图5，与7个扁管对应连通的分流段400依次标记为第一分流段401、第二分流段402、第三分流段403、第四分流段404、第五分流段405、第六分流段406以及第七分流段407。
本申请的一些实施例中，与靠下设置的第一扁管41至第三扁管43所连通的第一分流段401至第三分流段403与混合腔100连通，与靠上设置的第四扁管44至第七扁管47所连通的第四分流段404至第七分流段407与回流腔200连通。
该分配器10采用回流的方法，使气液两相制冷剂在混合腔100内得到冲击、混合、循环，避免产生气液分离现象。
具体的，当气液两相制冷剂在换热器内蒸发时，由制冷管路60输入到混合腔100内的气液两相制冷剂，一部分直接向上流动进入第一分流段401至第三分流段403内，再进入位于低位的第一扁管41至第三扁管43内；另一部分回流到回流腔200内。
而回流腔200内的气液两相制冷剂，一部分直接向上流动进入第四分流段404至第七分流段407内，再进入位于高位的第四扁管44至第七扁管47内；另一部分则回流到混合腔100内，该部分制冷剂对混合腔100内的制冷剂起到冲击作用，与混合腔100内的制冷剂进行混合，促使气液两相制冷剂在混合腔100内实现均匀混合，不发生气液分离现象，使进入各个分流段 400及扁管40内的制冷剂为气液混合均匀的制冷剂。
通过分流段400将混合腔100和回流腔200内的混合均匀的气液两相制冷剂输送到对应扁管40的过程中，对于不同分流段400内的气液两相制冷剂而言，分流段400的高度越高，分流段400内的制冷剂(主要指液态制冷剂)受重力影响而产生的流动阻力越大。
也即，液态制冷剂在沿分流段400向上流动的过程中，液态制冷剂受重力影响流速会逐渐降低。这就会导致进入到不同分流段400内的等流量的混合均匀的气液两相制冷剂在重力影响下，最终进入不同扁管40内的液态制冷剂的流量是不同的，进入低位的扁管40内的液态制冷剂流量要大于位于高位的扁管40内的液态制冷剂流量，由于换热器的换热主要靠液态制冷剂，这就最终仍会导致换热器的换热不均匀性。
为了解决并避免上述情况的发生，该分配器10在采样上述回流方法的基础上，根据与不同高度位置扁管40所连通的分流段400内制冷剂(主要指液态制冷剂)的流动阻力不同而采用不同的流道(指混合腔100和回流腔200)，以消除重力对液态制冷剂沿分流段400向上流动时的阻力影响，保证进入不同高度位置上的扁管40内的制冷剂流量的一致性。
具体的：由于制冷管路60输入到混合腔100内的气液两相制冷剂流速较快，导致混合腔100内的气液两相制冷剂流量要小于回流腔200内的气液两相制冷剂流量。
将与靠下设置的多个扁管40(第一扁管41至第三扁管43)所连通的多个分流段400(第一分流段401至第三分流段403)与混合腔100连通，将与靠上设置的多个扁管40(第四扁管44至第七扁管47)所连通的多个分流段400(第四分流段404至第七分流段407)与回流腔200连通。
那么在混合腔100和回流腔200内的气液两相制冷剂混合均匀的情况下，进入第一分流段401至第三分流段403内的气液两相制冷剂流量要小于进入第四分流段404至第七分流段407内的气液两相制冷剂流量。由于第一分流段401至第三分流段403的高度要小于第四分流段404至第七分流段407的 高度，那么受重力影响，使得最终进入第一扁管41至第七扁管47内的液态制冷剂流量是一致的。
图4和图5为将图3所示分配器10的外侧壁做透明化处理后的示意图，图6和图8为图3所示分配器10在不同位置处的剖视示意图，以对混合腔100、回流腔200以及分流段400的结构进行清晰、直观地示意。
本申请一些实施例中，参照图9至图11，混合腔100和回流腔200之间通过隔板300分隔开，隔板300上设有第一通口310和第二通口320。
混合腔100内的制冷剂可经第一通口310流入回流腔200内，回流腔200内的制冷剂可经第二通口320流入混合腔100内，如此形成制冷剂在混合腔100100和回流腔200之间的循环流动。
本申请的一些实施例中，第二通口320的面积小于第一通口310的面积，使得从第二通口320流向混合腔100的制冷剂得到加速，增强对混合腔100内制冷剂的冲击作用，提高混合的均匀性效果。
本申请的一些实施例中，第一通口310的底部与第二通孔320的底部平齐，有助于提高制冷剂的回流效果。
本申请的一些实施例中，混合腔100和回流腔200为相对于隔板300对称设置的腔体结构，混合腔100具有第一顶壁510，回流腔200具有第二顶壁520，第一顶壁510和第二顶壁520均自隔板300的顶端向下倾斜。
本申请一些实施例中，参照图7和图11，混合腔100的侧壁上设有制冷剂入口110，制冷管路60与制冷剂入口110连通。
制冷剂入口110的轴心与第二通口320的轴心处于同一水平面上，制冷剂从制冷剂入口110流入的方向与制冷剂从第二通口320流入的方向垂直。
这样，从第二通口320流入混合腔100的制冷剂对从制冷剂入口110流入混合腔100的制冷剂起到最大程度地射流冲击作用，有助于进一步提高制冷剂的混合均匀性。
本申请一些实施例中，参照图7和图9，混合腔100和回流腔200所围腔体沿水平方向延伸。
隔板300沿腔体的长度方向延伸，隔板300远离制冷剂入口110的一端与腔体的侧壁之间形成第一通口310，隔板300靠近制冷剂入口110的一端与腔体的侧壁之间形成第二通口320。
与靠下设置的多个扁管40所连通的多个分流段的入口430等距地设于混合腔100的第一顶壁510上，与靠上设置的多个扁管40所连通的多个分流段的入口430等距地设于回流腔200的第二顶壁520上。
在本申请的一些实施例中也即，第一分流段401至第三分流段403的入口等距地设于混合腔100的第一顶壁510上，第四分流段404至第七分流段407的入口设于回流腔200的第二顶壁520上。
本申请一些实施例中，参照图5、图10以及图11，沿着混合腔100内气液两相制冷剂的流动方向，与混合腔100所连通的多个分流段400的入口面积依次减小、分流段400的高度依次减小。
在本申请的一些实施例中也即，第一分流段401的入口设于远离制冷剂入口110的一侧，第三分流段403设于靠近制冷剂入口110的一侧，第三分流段403、第二分流段402以及第一分流段401的入口面积依次减小、高度依次减小。
这样，进入第三分流段403、第二分流段402以及第一分流段401内的制冷剂流量依次减小，而第三分流段403、第二分流段402以及第一分流段401内的液态制冷剂受重力的流动阻力影响也依次减小，这就使得最终进入第一扁管41至第三扁管43内的液态制冷剂的流量能够到达一致的状态。
气液两相制冷剂经第一通口310进入回流腔200内、并向第二通口320流动的过程中，由于第二通口320的面积小于第一通口310的面积，使得大量的制冷剂会在回流腔200内靠近第二通口320的位置处堆积。也就是说，回流腔200内靠近第二通口320侧的制冷剂流量大于靠近第一通口310侧的制冷剂流量。
基于此，参照图4、图10以及图11，沿着回流腔200内气液两相制冷剂的流动方向，设置与回流腔200所连通的多个分流段400的入口面积依次减 小、分流段400的高度依次增大。
在本申请的一些实施例中也即，第四分流段404的入口设于靠近第一通口310的一侧，第七分流段407的入口设于靠近第二通口320的一侧，第四分流段404至第七分流段407的入口面积依次减小、高度依次增大。
这样，通过第四分流段404至第七分流段407的入口面积的变化来抵消掉一部分因回流腔200内不同位置处制冷剂分布不均而导致进入不同分流段400内制冷剂流量不均的情况，再辅助结合分流段400高度的变化，使得最终进入第四扁管44至第七扁管47内的液态制冷剂的流量能够到达一致的状态。
本申请一些实施例中，考虑混合腔100内的气液两相制冷剂流量要小于回流腔200内的气液两相制冷剂流量，设定与混合腔100所连通的多个分流段400(第一分流段401至第三分流段403)的入口总面积为S1，与回流腔200所连通的多个分流段400(第四分流段404至第七分流段407)的入口总面积为S2，S1＞S2，以使得最终进入第一扁管41至第七扁管47内的制冷剂流量一致，实现制冷剂的均匀分配，最终实现换热器的换热均匀性。
本申请的一些实施例中，第一分流段401至第三分流段403等距地设于混合腔100的第一顶壁510上，第一分流段401的入口宽度为4/5倍的第一顶壁510宽度W1，第三分流段403的入口宽度等于第一顶壁510宽度W1。
第四分流段404至第七分流段407等距地设于回流腔200的第二顶壁520上，第四分流段404的入口宽度为1/2倍的第二顶壁520宽度W2，第七分流段407的入口宽度为1/4倍的第二顶壁520宽度W2。
本申请一些实施例中，参照图6至图9，分流段400包括连通的分流竖直段410和分流水平段420，分流竖直段410的入口设于第一顶壁510和第二顶壁520上，分流水平段420的出口与对应的扁管40连通。
与混合腔100所连通的多个分流竖直段410沿混合腔100的长度方向等距间隔设置，与回流腔200所连通的多个分流段竖直段410沿回流腔200的长度方向等距间隔设置。
根据弗劳德数Fr＝U2/gL，表征流体惯性力和重力相对大小。当Fr>1时，分流竖直段410内的流体惯性力可克服其重力，带动流体向上流动，因此需要限制分流竖直段410的宽度。
本申请的一些实施例中，分流竖直段410的宽度为0.2-1.5mm。
本申请的一些实施例中，分流竖直段410的宽度为1mm。
本申请的一些实施例中，相邻两个分流竖直段410之间的距离间隔为1-10倍的分流竖直段410的宽度。
本申请一些实施例中，相邻两个分流竖直段410之间的距离间隔为3倍的分流竖直段410的宽度。
本申请的一些实施例中，第四分流段404的入口与制冷剂入口110之间的距离为1-20倍的分流竖直段410的宽度。
本申请一些实施例中，第四分流段404的入口与制冷剂入口110之间的距离为7倍的分流竖直段410的宽度。
本申请一些实施例中，参照图2至图5，换热器还具有多个气管70，多个气管70与多个扁管40一一对应连通，气管70内流通气态制冷剂。
本申请的一些实施例中的分配器10内形成有集气通道600，集气通道600与多个气管70连通。
第二流程各个扁管40内的制冷剂换热后变为气态制冷剂，气态制冷剂流入相对应的气管70内，气态制冷剂沿气管70流入集气通道600内，然后从集气通道600排出。
分配器10集成了集气功能，无需在换热器中额外配置集气管，大大降低了换热器整体的体积，从而有助于实现空调器的小型化设计。
本申请一些实施例中，参照图3，多个扁管40和多个气管70沿竖直方向等距间隔设置，气管70位于与其连通的对应扁管40的上方。
制冷剂沿第二流程扁管流动时，当流动到扁管40的端部时，气态制冷剂上浮，将气管70设置在扁管40的上方，便于气态制冷剂的流动。
本申请一些实施例中，继续参照图3，分配器10上设有出气管路80，集 气通道600与出气管路80连通，以便将集气通道600内的气态制冷剂经出气管路80排出。
本申请一些实施例中，集气通道600包括主通道610和与主通道610连通的多个分支通道620，多个分支通道620与多个气管70一一对应连通，主通道610与出气管路80连通，便于气态制冷剂的汇集及排出。
本申请一些实施例中，对分配器10的加工工艺也进行了改进，该分配器10由多个叠片焊接而成，不同的叠片上形成有不同的轮廓，通过多个叠片的堆叠焊接形成分配器整体，由不同叠片围成混合腔100、回流腔200、隔板300、第一通口310、第二通口320、分流段400等分配器内部相关结构。
本申请一些实施例中，每一叠片的宽度为0.5-2mm。
本申请一些实施例中，每一叠片的宽度为1mm。
多个叠片堆叠焊接的加工工艺可以消除现有技术中采用冲压工艺制作分配器容易产生变形的问题。
本申请的一些实施例中，叠片采用带有焊料的铝合金叠片，焊接时采用面焊接，可有效消除因焊接不良造成制冷剂泄漏等问题。
以上仅为本申请的具体实施方式，但本申请的保护范围并不局限于此，任何熟悉本技术领域的技术人员在本申请揭露的技术范围内，可轻易想到的变化或替换，都应涵盖在本申请的保护范围之内。因此，本申请的保护范围应以权利要求的保护范围为准。

Claims (13)

  1. 一种空调器，包括换热器，其特征在于，所述换热器包括：
    多个扁管，其内流通制冷剂，多个所述扁管沿竖直方向依次间隔设置；
    分配器，用于将气液两相制冷剂均匀分配至多个所述扁管内，所述分配器内形成有：
    混合腔，其内流通由制冷管路输入的气液两相制冷剂；
    回流腔，其与所述混合腔连通，所述混合腔内的部分制冷剂可经所述回流腔回流至所述混合腔；
    多个分流段，其与多个所述扁管一一对应连通，与靠下设置的多个所述扁管所连通的多个所述分流段的入口与所述混合腔连通，与靠上设置的多个所述扁管所连通的多个所述分流段的入口与所述回流腔连通。
  2. 根据权利要求1所述的空调器，其特征在于，
    沿着所述混合腔内制冷剂的流动方向，与所述混合腔所连通的多个所述分流段的入口面积依次减小、所述分流段的高度依次减小；
    沿着所述回流腔内制冷剂的流动方向，与所述回流腔所连通的多个所述分流段的入口面积依次减小、所述分流段的高度依次增大。
  3. 根据权利要求2所述的空调器，其特征在于，
    与所述混合腔所连通的多个所述分流段的入口总面积为S1，与所述回流腔所连通的多个所述分流段的入口总面积为S2，S1＞S2。
  4. 根据权利要求1所述的空调器，其特征在于，
    所述混合腔和所述回流腔之间通过隔板分隔开，所述隔板上设有第一通口和第二通口，所述混合腔内的制冷剂可经所述第一通口流入所述回流腔内，所述回流腔内的制冷剂可经所述第二通口流入所述混合腔内；
    与靠下设置的多个所述扁管所连通的多个所述分流段的入口设于所述混合腔的顶壁上，与靠上设置的多个所述扁管所连通的多个所述分流段的入口设于所述回流腔的顶壁上。
  5. 根据权利要求4所述的空调器，其特征在于，
    所述第二通口的面积小于所述第一通口的面积。
  6. 根据权利要求4所述的空调器，其特征在于，
    所述混合腔的侧壁上设有制冷剂入口，所述制冷剂入口的轴心与所述第二通口的轴心处于同一水平面上，制冷剂从所述制冷剂入口流入的方向与制冷剂从所述第二通口流入的方向垂直。
  7. 根据权利要求4所述的空调器，其特征在于，
    所述第一通口的底部与所述第二通孔的底部平齐。
  8. 根据权利要求1所述的空调器，其特征在于，
    所述分流段包括连通的分流竖直段和分流水平段，所述分流竖直段的入口设于所述混合腔和所述回流腔的顶壁上，所述分流水平段的出口与对应的所述扁管连通，与所述混合腔所连通的多个所述分流竖直段沿所述混合腔的长度方向间隔设置，与所述回流腔所连通的多个所述分流段竖直段沿所述回流腔的长度方向间隔设置。
  9. 根据权利要求1至8中任一项所述的空调器，其特征在于，所述换热器还包括：
    多个气管，多个所述气管与多个所述扁管一一对应连通，所述气管内流通气态制冷剂；
    所述分配器内还形成有集气通道，所述集气通道与多个所述气管连通。
  10. 根据权利要求9所述的空调器，其特征在于，
    多个所述扁管和多个所述气管沿竖直方向间隔设置，所述气管位于与其连通的所述扁管的上方。
  11. 根据权利要求9所述的空调器，其特征在于，所述集气通道包括主通道和与所述主通道连通的多个分支通道，多个所述分支通道与多个所述气管一一对应连通，所述主通道与所述出气管路连通。
  12. 根据权利要求1所述的空调器，其特征在于，所述分配器由多个叠片堆叠焊接而成。
  13. 根据权利要求12所述的空调器，其特征在于，所述叠片采用带有焊料的铝合金叠片。
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