CN114838532A - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
- Publication number
- CN114838532A CN114838532A CN202210193339.2A CN202210193339A CN114838532A CN 114838532 A CN114838532 A CN 114838532A CN 202210193339 A CN202210193339 A CN 202210193339A CN 114838532 A CN114838532 A CN 114838532A
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- heat exchange
- branch
- liquid
- heat exchanger
- pipe
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- 239000003507 refrigerant Substances 0.000 claims abstract description 111
- 238000010438 heat treatment Methods 0.000 claims abstract description 37
- 239000007788 liquid Substances 0.000 claims description 135
- 238000000926 separation method Methods 0.000 claims description 16
- 238000005452 bending Methods 0.000 claims description 2
- 238000005057 refrigeration Methods 0.000 description 14
- 238000000034 method Methods 0.000 description 9
- 230000009471 action Effects 0.000 description 5
- 230000005484 gravity Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000004891 communication Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 239000012071 phase Substances 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001603 reducing effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
Images
Classifications
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
- F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
- F24F11/42—Defrosting; Preventing freezing of outdoor units
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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
- F25B39/02—Evaporators
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The application relates to the technical field of air conditioners, and discloses a heat exchanger, including: the first heat exchange part comprises N upper heat exchange branches; the second heat exchange part is arranged at the lower part of the first heat exchange part and comprises M lower heat exchange branches which are communicated in parallel; and the first bypass pipeline is communicated with the refrigerant outlet end of the first heat exchange part and the refrigerant outlet end of the second heat exchange part, and is provided with a first electromagnetic valve, wherein N is more than or equal to M-1, and M is more than or equal to 2. Through the arrangement of the first bypass pipeline and the first electromagnetic valve, the heat exchanger can respectively carry out refrigerant conveying with different flow paths under the refrigerating and heating working conditions, and therefore the performance requirements of the heat exchanger under different working modes can be simultaneously met. The application also discloses an air conditioner.
Description
The priority of chinese patent application entitled "dispenser, check valve, heat exchanger, refrigeration cycle system, air conditioner," filed in 2021, No. 9/19, application No. 202111102392.9, is hereby incorporated by reference in its entirety.
The priority of the chinese patent application entitled "dispenser, check valve, heat exchanger, refrigeration cycle system, air conditioner," filed on 2021, No. 9/20, application No. 202111102583.5, is incorporated herein by reference in its entirety.
Technical Field
The application relates to the technical field of air conditioners, for example to a heat exchanger and an air conditioner.
Background
When the air conditioner operates in a heating working condition, an outdoor heat exchanger of the air conditioner serves as an evaporator, a refrigerant in a pipe of the air conditioner is in a low-temperature low-pressure area, heat transfer performance is mainly restrained by a heat transfer coefficient and pressure drop together, the more branches of the evaporator are required to be, the better the branch number is, and therefore the low-temperature heating capacity of the air conditioner can be improved.
When the air conditioner operates in a refrigeration working condition, the outdoor heat exchanger of the air conditioner serves as a condenser, refrigerant in the pipe of the air conditioner is in a high-temperature high-pressure area and is insensitive to pressure drop, at the moment, the heat transfer performance of the air conditioner is mainly influenced by a heat transfer coefficient, the smaller the number of branches of the condenser is, the better the number of the branches is, and the high-temperature refrigeration capacity of the air conditioner can be further improved.
In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:
the existing heat exchanger adopts a fixed refrigerant flow path arrangement, and can not simultaneously meet the requirements of small number of refrigeration branches and large number of heating branches, thereby further not enabling the air conditioner to exert the best performance of the air conditioner during refrigeration and heating.
Disclosure of Invention
The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.
The embodiment of the disclosure provides a heat exchanger, and the flow path arrangement form of the heat exchanger simultaneously meets the requirements of small number of refrigeration branches and large number of heating branches, so that an air conditioner can exert the optimal performance of the air conditioner during refrigeration and heating.
In some embodiments, when the air conditioner operates in a heating condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises: the first heat exchange part comprises N upper heat exchange branches; the second heat exchange part is arranged at the lower part of the first heat exchange part and comprises M lower heat exchange branches which are communicated in parallel; and the first bypass pipeline is communicated with the refrigerant outlet end of the first heat exchange part and the refrigerant outlet end of the second heat exchange part, and is provided with a first electromagnetic valve, wherein N is more than or equal to M-1, and M is more than or equal to 2.
In some embodiments, the first heat exchanging portion comprises a first upper heat exchanging branch and a second upper heat exchanging branch, the second heat exchanging portion comprises a first lower heat exchanging branch and a second lower heat exchanging branch, the heat exchanger further comprises: the first liquid separator is arranged at the liquid inlet of the heat exchanger, and one liquid separating branch pipe of the first liquid separator is communicated with the refrigerant inlet end of the second lower heat exchange branch pipe; the liquid separating branch pipes of the second liquid separator are respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch pipe, the second upper heat exchange branch pipe and the first lower heat exchange branch pipe one by one; and the second bypass pipeline is communicated with the first liquid separator and the second liquid separator and is provided with a second electromagnetic valve and an expansion valve.
In some embodiments, the expansion valve is disposed at an upper portion of the second solenoid valve.
In some embodiments, the heat exchanger further comprises a first control portion configured to: and adjusting the opening degree of the expansion valve according to the current outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch, the second upper heat exchange branch and the first lower heat exchange branch.
In some embodiments, the first upper heat exchange branch, the second upper heat exchange branch, the first lower heat exchange branch, and the second lower heat exchange branch are arranged from top to bottom.
In some embodiments, the heat exchanger further comprises a second controller configured to: and acquiring a first temperature of a refrigerant outlet end of the first upper heat exchange branch and a second temperature of a refrigerant outlet end of the second lower heat exchange branch, and adjusting the opening degree of the expansion valve according to the difference value of the first temperature and the second temperature.
In some embodiments, the first dispenser comprises: the liquid separation device comprises a shell, a liquid separation device and a liquid separation device, wherein a liquid separation cavity is formed in the shell, and a first liquid separation port and a second liquid separation port are formed in the shell; the collecting pipe comprises a first pipe section and a second pipe section which are connected in a bent mode, and the first pipe section is directly connected with the liquid separating cavity; the first liquid dividing branch pipe is communicated with the liquid dividing cavity through the first liquid dividing port and communicated with the second bypass pipeline; and the second branch liquid distribution pipe is communicated with the liquid distribution cavity through the second liquid distribution port and communicated with the third heat exchange part, wherein the plane where the axes of the first pipe section and the second pipe section are located is a first plane, the plane where the axes of the first branch liquid distribution pipe and the second branch liquid distribution pipe are located is a second plane, and the first plane and the second plane are not vertical.
In some embodiments, the first plane and the second plane form an angle greater than or equal to 50 degrees and less than or equal to 70 degrees; or the included angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees.
In some embodiments, the first branch knock-out tube has an inner diameter greater than or equal to 5.1mm and less than or equal to 6.1 mm; the inner diameter of the second branch liquid-dividing pipe is more than or equal to 3.1mm and less than or equal to 3.7 mm.
The embodiment of the present disclosure provides an air conditioner, which includes the heat exchanger as described above.
The heat exchanger and the air conditioner provided by the embodiment of the disclosure can realize the following technical effects:
the heat exchanger provided by the embodiment of the disclosure is divided into a first heat exchange part and a second heat exchange part by dividing the upper end and the lower end of a first bypass pipeline up and down. Through the arrangement of the first bypass pipeline and the first electromagnetic valve, the heat exchanger can respectively carry out refrigerant conveying with different flow paths under the refrigerating and heating working conditions, and therefore the performance requirements of the heat exchanger under different working modes can be simultaneously met.
The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.
Drawings
One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:
FIG. 1 is a schematic diagram of a heat exchanger according to an embodiment of the present disclosure;
FIG. 2 is a schematic structural diagram of another heat exchanger provided by an embodiment of the disclosure;
FIG. 3 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;
FIG. 4 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;
FIG. 5 is a schematic structural view of a first liquid separator according to an embodiment of the present disclosure;
fig. 6 is a schematic structural view of another first liquid separator according to an embodiment of the present disclosure.
Reference numerals:
111: a first upper heat exchange branch; 112: a second upper heat exchange branch; 113: a third upper heat exchange branch; 114: a fourth upper heat exchange branch; 121: a first lower heat exchange branch; 122: a second lower heat exchange branch;
201: a first bypass line; 202: a second bypass line;
301: a first solenoid valve; 302: a second solenoid valve; 401: an expansion valve;
500: a first liquid separator; 511: a converging cavity; 512: a first branch chamber; 513: a second branch chamber; 520: a collector pipe; 521: a first tube section; 522: a second tube section; 530: a first branch liquid-separating pipe; 540: a second branch pipe;
600: a second liquid separator; 700: a third liquid distributor; 800: a fourth liquid distributor;
901: a first sum; 902: and a second sum.
Detailed Description
So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.
The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the present disclosure described herein may be made. Furthermore, the terms "comprising" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions.
In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their examples and are not intended to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used in other meanings besides orientation or positional relationship, for example, the term "upper" may also be used in some cases to indicate a certain attaching or connecting relationship. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.
In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.
The term "plurality" means two or more unless otherwise specified.
In the embodiment of the present disclosure, the character "/" indicates that the preceding and following objects are in an or relationship. For example, A/B represents: a or B.
The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. For example, a and/or B, represents: a or B, or A and B.
It should be noted that, in the case of no conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.
The air conditioner comprises an indoor unit and an outdoor unit, wherein the indoor unit is provided with an indoor heat exchanger, an indoor fan and the like and can be used for realizing the functions of heat exchange and the like between a refrigerant and an indoor environment; the outdoor unit is provided with an outdoor heat exchanger, an outdoor fan, a throttle valve, a compressor, a gas-liquid separator and the like, and can be used for realizing the functions of heat exchange, refrigerant compression, refrigerant throttling and the like by matching with a refrigerant and an outdoor environment.
The indoor heat exchanger, the outdoor heat exchanger, the throttle valve, the compressor, the gas-liquid separator and other components are connected through refrigerant pipelines to form a refrigerant circulating system for circularly conveying the refrigerant between the indoor unit and the outdoor unit; optionally, the refrigerant circulation system is at least limited to two refrigerant flow directions respectively used for a refrigeration mode or a heating mode, specifically, when the air conditioner operates in the refrigeration mode, the refrigerant circulation system conveys the refrigerant in a first refrigerant flow direction, and after being discharged from the compressor, the refrigerant sequentially flows through the outdoor heat exchanger, the throttle valve and the indoor heat exchanger, and then flows back to the compressor through the gas-liquid separator; when the air conditioner operates in a heating mode, the refrigerant circulating system conveys the refrigerant in a second refrigerant flow direction, and the refrigerant flows through the indoor heat exchanger, the throttle valve and the outdoor heat exchanger in sequence after being discharged from the compressor and then flows back to the compressor through the gas-liquid separator.
The following heat exchanger is described by taking an air conditioner to operate in a heating working condition and taking the heat exchanger as an outdoor heat exchanger as an example. The description is given here when the heat exchanger is used in a specific operating condition, and the heat exchanger is not limited to be used only as an outdoor heat exchanger.
The embodiment of the disclosure provides a heat exchanger. As shown in fig. 1-4.
The heat exchanger includes a first heat exchange portion and a second heat exchange portion. The first heat exchanging part comprises N upper heat exchanging branches. The second heat exchange part is arranged at the lower part of the first heat exchange part and comprises M lower heat exchange branches communicated in parallel. The first bypass line 201 communicates the refrigerant outlet end of the first heat exchange portion with the refrigerant outlet end of the second heat exchange portion. The first bypass line 201 is provided with a first solenoid valve 301. Wherein N is more than or equal to M-1, and M is more than or equal to 2.
The upper end and the lower end of the first bypass pipeline 201 are used for dividing the heat exchange branch of the heat exchanger into a first heat exchange part and a second heat exchange part. When the heat exchanger is in a vertical installation and use state, the first heat exchange part is positioned at the upper part of the second heat exchange part. N can be an integer number of 1, 2, 3, 4, 5, 6, 7, and the like. When the number of the upper heat exchange branches is multiple, similarly, the multiple upper heat exchange branches are communicated in parallel. M can be an integer number of 2, 3, 4, 5, 6, 7, etc. The upper heat exchange branches are communicated with the lower heat exchange branches in parallel.
As shown in fig. 1 to 4, a plurality of upper heat exchange branches of the first heat exchange portion adopt a fourth liquid separator 800 to converge, a plurality of lower heat exchange branches of the second heat exchange portion adopt a third liquid separator confluence 700, and a first bypass line 201 connects the third liquid separator 700 and the fourth liquid separator 800.
According to the heat exchanger provided by the embodiment of the disclosure, when the air conditioner operates in a heating working condition, all heat exchange branches of the heat exchanger are communicated in parallel, so that the heating performance of the air conditioner is met, and the low-temperature heating capacity of the air conditioner is improved.
Optionally, the first heat exchanging part comprises a first upper heat exchanging branch 111 and a second upper heat exchanging branch 112, and the second heat exchanging part comprises a first lower heat exchanging branch 121 and a second lower heat exchanging branch 122. The heat exchanger further comprises a first liquid separator 500, a second liquid separator 600, and a second bypass line 202. The first liquid separator 500 is disposed at the liquid inlet of the heat exchanger, and a branch liquid pipe of the first liquid separator 500 is communicated with the refrigerant inlet end of the second lower heat exchange branch 122. The plurality of branch liquid pipes of the second liquid separator are respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch 111, the second upper heat exchange branch 112 and the first lower heat exchange branch 121 one by one. The second bypass line 202 communicates the first and second dividers 500 and 202. The second bypass line 202 is provided with a second solenoid valve 302 and an expansion valve 401.
By controlling the open and close states of the first electromagnetic valve 301 and the second electromagnetic valve 302, each heat exchange branch of the heat exchanger can be in different refrigerant flow path forms under the working conditions of refrigeration and heating, and the performance requirements of the heat exchanger under different working modes can be simultaneously ensured.
Taking 3 heat exchange branches shown in fig. 1 and 2 as an example, when the air conditioner operates in a refrigeration condition, the first electromagnetic valve 301 and the second electromagnetic valve 302 are controlled to be closed. The refrigerant flows in through the first header 901, sequentially flows through the first upper heat exchange branch 111, the first lower heat exchange branch 121 and the second lower heat exchange branch 122, and flows out through the second header 902, and the number of the heat exchange branches of the refrigerant flow path of the heat exchanger is small.
When the number of the heat exchange branches of the heat exchanger is 4, as shown in fig. 3, under the refrigeration condition, the first upper heat exchange branch 111 is in parallel communication with the second upper heat exchange branch 112; when the number of the heat exchange branches of the heat exchanger is 6, as shown in fig. 4, under the cooling condition, the first upper heat exchange branch 111, the second upper heat exchange branch 112, the third upper heat exchange branch 113, and the fourth upper heat exchange branch 114 are in parallel communication.
Taking 3 heat exchange branches shown in fig. 1 and 2 as an example, when the air conditioner operates in a heating condition, the first electromagnetic valve 301 and the second electromagnetic valve 302 are controlled to be opened. The refrigerant flows in through the second header 902, the first upper heat exchange branch 111, the first lower heat exchange branch 121, and the second lower heat exchange branch 122 are connected in parallel and communicated, and flow out from the first header 901, and the number of heat exchange branches of the refrigerant flow path of the heat exchanger is large.
Alternatively, the expansion valve 401 is provided at an upper portion of the second solenoid valve 302.
When the air conditioner operates in a refrigeration working condition, the pressure of the refrigerant in the second liquid separator 600 is higher than that of the refrigerant in the first liquid separator 500, and the second electromagnetic valve 302 has the risks of impact on the valve core and poor sealing. The expansion valve 401 is disposed on the upper portion of the second solenoid valve 302, and the expansion valve 401 can be controlled to close, so that the pressure difference between the two ends of the second solenoid valve 302 can be reduced, and the reliability of closing the second solenoid valve 302 can be ensured. Also, the expansion valve 401 may adjust the opening degree. Taking the 3 heat exchange branches shown in fig. 1 and 2 as an example, when the air conditioner operates in a heating working condition, the circulation amount of the refrigerant is further adjusted by the expansion valve 401 after passing through the throttling device of the air conditioner system, so that the number of heat exchange tubes participating in refrigerant circulation in the first upper heat exchange branch 111, the second upper heat exchange branch 112 and the first lower heat exchange branch 121 is adjusted, the heat exchange volume of the heat exchanger is adjusted, and the energy efficiency of the air conditioner during different load operations is improved.
Optionally, the first upper heat exchange branch 111, the second upper heat exchange branch 112, the first lower heat exchange branch 121 and the second lower heat exchange branch 122 are sequentially arranged from top to bottom.
Optionally, the first liquid separator 500 includes a housing, a manifold 520, a first branch liquid separator 530, and a second branch liquid separator 540. The shell is internally provided with a liquid separation cavity, and the shell is provided with a first liquid separation port and a second liquid separation port. The collecting pipe 520 comprises a first pipe section 521 and a second pipe section 522 which are communicated in a bending mode, and the first pipe section 521 is directly communicated with the liquid dividing cavity. The first branch liquid-separating pipe 530 is communicated with the liquid-separating chamber through the first liquid-separating port, and the first branch liquid-separating pipe 530 is communicated with the second bypass line 202. The second branch liquid distribution pipe 540 is communicated with the liquid distribution cavity through a second liquid distribution port, and the second branch liquid distribution pipe 540 is communicated with the third heat exchange part. The axes of first pipe section 521 and second pipe section 522 lie in a first plane and the axes of first branch 530 and second branch 540 lie in a second plane, the first plane being non-perpendicular to the second plane. As shown in fig. 5 and 6.
Optionally, an included angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees; or the included angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees. Alternatively, the inner diameter of first branch liquid-dividing line 530 is greater than or equal to 5.1mm and less than or equal to 6.1 mm. The second branch liquid take-off 540 has an inner diameter of 3.1mm or more and 3.7mm or less.
Optionally, the liquid separating chamber includes a confluence chamber 511, a first branch chamber 512 and a second branch chamber 513, the first branch liquid separating pipe 530 is communicated with the first branch chamber 512 through a first liquid separating port, and the second branch liquid separating pipe 540 is communicated with the second branch chamber 513 through a second liquid separating port.
The manifold 520 comprises a first pipe segment 521 and a second pipe segment 522, the plane of the axes of the first pipe segment 521 and the second pipe segment 522 is a first plane, and the included angle between the first plane and the second plane is e. As shown in fig. 6. The first plane is non-perpendicular to the second plane, it being understood that the angle e between the first plane and the second plane is less than 90 °. Optionally, the angle between the first plane and the second plane is measured as the acute angle formed by the two. The first plane is not perpendicular to the second plane, so that the amount of refrigerant entering the first branch liquid-separating pipe 530 and the second branch liquid-separating pipe 540 through the first pipe section 521 is different. For example, when the included angle between the first plane and the second plane is on the side of the first branch liquid-dividing pipe 530, the flow rate of the refrigerant flowing to the second branch liquid-dividing pipe 540 is greater than the flow rate flowing to the first branch liquid-dividing pipe 530 under the action of gravity. Similarly, when the angle between the first plane and the second plane is on the side of the second branch liquid dividing pipe 540, the flow rate of the refrigerant flowing to the first branch liquid dividing pipe 530 is greater than the flow rate of the refrigerant flowing to the second branch liquid dividing pipe 540 under the action of gravity.
Taking the heat exchanger shown in fig. 3 as an example, in a heating condition, when the heat exchanger is used as an evaporator, the refrigerant is divided by the first liquid separator 500 and then flows into four heat exchange branches connected in parallel, that is, the first upper heat exchange branch 111, the second upper heat exchange branch 112, the first lower heat exchange branch 121, and the second lower heat exchange branch 122. The refrigerant flows through the liquid distributing branch pipe on the left side of the first liquid separator 500 and then flows into only the second lower heat exchanging branch 122, and the refrigerant flows through the liquid distributing branch pipe on the right side of the first liquid separator 500 and then flows into three heat exchanging branches, namely a first upper heat exchanging branch 111, a second upper heat exchanging branch 112 and a first lower heat exchanging branch 121. It can be seen that after the refrigerant passes through the first liquid separator 500, the refrigerant amount required by the two liquid separating branch pipes of the first liquid separator 500 is different. The refrigerant quantity required by the right branch liquid separating pipe is 3 times of that of the left branch liquid separating pipe. The knockout that this disclosure provided utilizes the coolant at the action of gravity of flow in-process, through the setting of the contained angle between the first plane at the axis place of first pipeline section 521 and second pipeline section 522 of collecting pipe 520 and the second plane at the axis place of first branch liquid pipe 530 and second branch liquid pipe 540, has realized that the refrigerant volume that different branch liquid pipes of knockout flow is different, has satisfied the demand that the required refrigerant volume of branch liquid pipe is different, and then has improved the heat exchange efficiency of heat exchanger.
Optionally, an angle between the first plane and the second plane is less than 90 degrees. Optionally, the included angle between the first plane and the second plane is 0 degree, 30 degrees, 60 degrees, 70 degrees, 80 degrees, or the like. The included angle between the first plane and the second plane is smaller than 90 degrees, so that the refrigerant can bias under the action of gravity after flowing through the first pipe section 521 of the collecting pipe 520, and further the cold energy flowing into the first liquid-dividing branch pipe 530 and the second liquid-dividing branch pipe 540 is different.
Optionally, the inner diameter of first branch splitter 530 is greater than the inner diameter of second branch splitter 540. According to the liquid distributor provided by the embodiment of the disclosure, an included angle is formed between a first plane where the axes of the first pipe section 521 and the second pipe section 522 of the collecting pipe 520 are located and a second plane where the axes of the two liquid distributing branch pipes are located, and the difference of the refrigerant amount flowing into the two liquid distributing branch pipes is further increased by further matching with the inner diameter difference between the two liquid distributing branch pipes.
Alternatively, if the first pipe segment 521 of the collecting pipe 520 is inclined toward the second branch liquid-separating pipe 540, under the action of gravity, more refrigerant flows into the first branch liquid-separating pipe 530 in accordance with the fact that the inner diameter of the first branch liquid-separating pipe 530 is larger than that of the second branch liquid-separating pipe 540, thereby further increasing the refrigerant flow rate difference between the two branch liquid-separating pipes.
Refrigerant distribution with a refrigerant flow difference of 3:1 or more in the flow ratio of the first branch liquid dividing pipe 530 to the second branch liquid dividing pipe 540 is difficult to achieve only by limiting the difference in the inner diameters of the first branch liquid dividing pipe 530 and the second branch liquid dividing pipe 540. The reason is that the inner diameter of the branch liquid-separating pipe is limited to the minimum value, for example, the inner diameter of the branch liquid-separating pipe cannot be less than 3mm, even not less than 3.36mm, the copper pipe below the inner diameter actually becomes a capillary pipe, the capillary pipe has larger flow resistance, and forms a throttling and pressure reducing effect on the flow of the refrigerant, so that the power of the compressor can be increased, and the performance of the system can be reduced; even when the air conditioner operates in a heating working condition, the outdoor heat exchanger is frosted seriously, and the safety and reliability of the system are affected. Due to the limitation of the minimum value of the inner diameters of the branch liquid-separating pipes, in order to realize refrigerant distribution with a flow ratio of 3:1, the pipe diameter of the other branch liquid-separating pipe needs to be larger than 7mm, and optionally, the 7mm can be an outer diameter which is 1.4mm larger than the inner diameter, however, the pipe diameter obviously exceeds the inner diameter of a heat exchange pipe which is actually used in the heat exchanger, and the general pipe diameter of the heat exchanger is 7mm, such as a pipe fin type heat exchanger. Therefore, it is difficult to achieve refrigerant distribution with a refrigerant distribution ratio of 3:1 or even a larger refrigerant flow difference between the first branch liquid-dividing pipe 530 and the second branch liquid-dividing pipe 540 within a range not exceeding the allowable pipe diameter of the heat exchange pipe in the heat exchanger, merely by limiting the difference in the inner diameters of the first branch liquid-dividing pipe 530 and the second branch liquid-dividing pipe 540.
According to the technical scheme that the included angle is formed between the first plane where the axes of the first pipe section 521 and the second pipe section 522 of the collecting pipe 520 are located and the second plane where the axes of the two branch liquid pipes are located, and the inner diameter difference between the two branch liquid pipes is further matched, the refrigerant distribution requirements of the two branch liquid pipes with the refrigerant flow ratio of 2:1-7:1 and even a larger proportion, such as 2:1, 3:1, 4:1, 5:1, 6:1 and 7:1, can be realized within the range allowed by the pipe diameter of a heat exchange pipe of the heat exchanger. According to the refrigerant distribution scheme for realizing the large flow ratio provided by the embodiment of the disclosure, the inner diameter of the second branch liquid-dividing pipe 540 does not need to be designed to be too small, and the flow rate of the refrigerant in the first branch liquid-dividing pipe 530 is much larger than that of the refrigerant in the second branch liquid-dividing pipe 540. Therefore, the refrigerant distribution scheme of the liquid separator provided by the embodiment of the disclosure avoids the problem of overlarge total pressure drop of the liquid separating branch pipes and the heat exchanger of the liquid separator when the refrigerant distribution ratio of the two liquid separating branch pipes is large.
Optionally, an included angle between a first plane where the axes of the first pipe section 521 and the second pipe section 522 of the collecting pipe 520 are located and a second plane where the axes of the two branch liquid pipes are located is greater than or equal to 50 degrees and less than or equal to 70 degrees. The difference in the flow rates of the refrigerant in the first branch 530 and the second branch 540 is increased.
Alternatively, the inner diameter of first branch liquid-dividing line 530 is greater than or equal to 5.1mm and less than or equal to 6.1 mm; the second branch liquid take-off 540 has an inner diameter of 3.1mm or more and 3.7mm or less.
Optionally, the second pipe section 522 of the collecting pipe 520 is inclined toward the second branch liquid pipe 540 side.
When the air conditioner operates in a heating working condition and the heat exchanger is used as an evaporator, the heat exchanger can exert the optimal heat exchange capacity under the following conditions: when heating, constantly absorb the heat in the surrounding environment air from low temperature liquid state, reached gas-liquid two-phase state along with the temperature rise, the temperature keeps unchanged at evaporating temperature this time, only constantly takes place the liquid phase change to gaseous state, and liquid refrigerant is less and less, and gaseous refrigerant is more and more, just all becomes gaseous state and the temperature is higher than evaporating temperature 1 ~ 2 ℃ when the export of whole heat transfer branch road. The reason is that when the outlet temperature of the heat exchange branch is overheated, all the gas-state refrigerants are gaseous refrigerants, the enthalpy difference of the gaseous refrigerants is small, the heat exchange capacity is low, and when the superheat degree is overlarge, the heat exchange temperature difference between the refrigerants and the ambient temperature is small, for example, when the evaporation temperature is about 0-1 ℃, if the superheat degree is greater than 3 ℃, the temperature is above 4 ℃, and the ambient temperature in winter is about 7 ℃, the heat exchange temperature difference is small, and the heat exchange capacity of the heat exchanger is more difficult to be exerted.
The better the uniformity is, the easier each heat exchange branch has a proper heat exchange, if not uniform, some branches are too hot, the back hairpin tubes have no heat exchange effect, some heat exchange branch refrigerants are too many, and the whole heat exchange branch still has a lot of low-temperature liquid refrigerants to exchange cold energy, so, under the same refrigerant flow, the heat exchange effect of the whole heat exchanger is poor, and the capacity of the air conditioner is very low. Therefore, the method for judging good shunting of experience in heating comprises the following steps: the temperature difference of the outlets of the branches is within 2 ℃, the superheat degree of the outlets is about 1 ℃, and the shunting is better under the condition.
TABLE 1
TABLE 2
Alternatively, when the air conditioner is operated in a heating mode, the heat exchanger is used as an evaporator, and the first upper heat exchange branch 111, the second upper heat exchange branch 112, and the first lower heat exchange branch 121 connected in parallel are communicated with the first liquid-dividing branch pipe 530, and the second lower heat exchange branch 122 is communicated with the second liquid-dividing branch pipe 540, as shown in fig. 3, the refrigerant temperature at the outlet of each heat exchange branch is as shown in tables 1 and 2. Table 1 shows the maximum temperature difference between the second lower heat exchange branch 122 and the first three branches and the heating capacity of the air conditioner under different inner diameters of the first liquid-dividing branch 530 and the second liquid-dividing branch 540 when the included angle between the first plane and the second plane is 90 degrees. As can be seen from the data in table 1, when the inner diameter of the first branch liquid-dividing pipe 530 is 5.6mm, and the inner diameter of the second branch liquid-dividing pipe 540 is 3.36mm, the maximum temperature difference between the second lower heat exchange branch 122 and the first three branches of the heat exchanger is 3.4 ℃ which is the smallest, and the heating capacity of the air conditioner is 4855.2W which is the largest at the inner diameter. Table 2 shows that when the inner diameter of the first branch liquid-dividing pipe 530 is 5.6mm and the inner diameter of the second branch liquid-dividing pipe 540 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the second lower heat exchange branch 122 and the first three branches and the heating capacity of the air conditioner are different. As can be seen from table 2, when the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the second lower heat exchange branch 122 and the first three branches is minimum and is 1.2 ℃, and the heating capacity of the air conditioner is maximum and is 5016.1W at this angle.
As can be seen from the data in tables 1 and 2, when the number of the heat exchange branches in the heat exchanger, which are communicated with the first branch liquid pipe 530, is 3, and the number of the heat exchange branches in the heat exchanger, which are communicated with the second branch liquid pipe 540, is 1, for example, as shown in the heat exchanger shown in fig. 3, the inner diameter of the first branch liquid pipe 530 is 5.6mm, the inner diameter of the second branch liquid pipe 540 is 3.36mm, and the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth branch heat exchange branch 330 and the first three branches is the smallest, the uniformity of the heat exchange capacity of the refrigerant in each branch heat exchange branch is the best, and the heating capacity of the air conditioner is the largest. That is, a ratio of the amount of refrigerant in the first branch liquid-dividing pipe 530 to the amount of refrigerant in the second branch liquid-dividing pipe 540 of 3:1 is achieved.
Similarly, when the included angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees, the inner diameter of the first branch liquid dividing pipe 530 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 540 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant quantity in the first branch liquid dividing pipe 530 to the refrigerant quantity in the second branch liquid dividing pipe 540 can be preferably realized to be 3: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in the embodiment are similar to the data in tables 1 and 2, and are not repeated here.
Optionally, the heat exchanger further includes a first control part configured to adjust an opening degree of the expansion valve according to the current outdoor environment humidity, so as to adjust heat exchange volumes of the first upper heat exchange branch, the second upper heat exchange branch and the first lower heat exchange branch.
When the outdoor environment humidity is lower, the current outdoor environment is considered to be not easy to frost, at the moment, the opening degree of the expansion valve can be increased, the number of the heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the number of the heat exchange tubes participating in heat exchange in the first lower heat exchange branch are increased, the heat exchange volume of the heat exchanger is further improved, the heat exchange capacity of the heat exchanger is improved, and the requirement of high-load operation of an air conditioning system is met.
When the outdoor environment humidity is higher, the current outdoor environment is considered to be easy to frost, at the moment, the opening degree of the expansion valve can be reduced, the number of the heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the number of the heat exchange tubes participating in heat exchange in the first lower heat exchange branch are reduced, the effective heat exchange volume of the heat exchanger is further reduced, and the requirement of low-load operation of the air conditioning system is met.
Optionally, the heat exchanger further includes a second controller configured to obtain a first temperature at a refrigerant outlet end of the first upper heat exchange branch and a second temperature at a refrigerant outlet end of the second lower heat exchange branch, and adjust an opening degree of the expansion valve according to a difference between the first temperature and the second temperature. The disclosed embodiments provide an apparatus that can perform a method for adjusting a temperature of a refrigerant in a heat exchanger.
When the air conditioner operates in a heating working condition in winter and the relative humidity of the outdoor environment is high, the surface of the outdoor heat exchanger is easy to frost. When only part of the surface of the outdoor heat exchanger is frosted, the temperature of the refrigerant outlet of each heat exchange branch of the heat exchanger is different. The refrigerant flow in the heat exchange branch with higher outlet temperature is less, the heat exchange capacity is low, and the outer surface is not frosted; the heat exchange branch with lower outlet temperature has more cooling medium flow, high heat exchange capacity and frosted outer surface.
However, it has been studied that in the heat exchanger in which frost is formed only on a part of the outer surface, the wind of the outdoor fan easily passes through the frost-free portion having a small wind resistance. As mentioned above, the temperature of the refrigerant outlet of the heat exchange branch at the non-frosted part of the outer surface is higher, the refrigerant flow is small, the heat exchange capacity is low, and the heat exchange branch at the frosted part of the outer surface with relatively higher heat exchange capacity is equivalent to short-circuited due to the greatly reduced air volume flowing through, so that the heat exchange capacity of the heat exchange branch is indirectly reduced, and therefore, the whole heat exchange capacity of the heat exchanger is reduced.
According to the method for adjusting the temperature of the refrigerant in the heat exchanger, provided by the embodiment of the disclosure, the opening degree of the expansion valve is adjusted according to the difference value between the first temperature T1 and the second temperature T2, so that the flow speed and the flow of the refrigerant in the heat exchange branch are adjusted, the difference between the first temperature T1 and the second temperature T2 is reduced, the heat exchange uniformity of each heat exchange branch of the heat exchanger is improved, and the overall heat exchange capacity of the heat exchanger is further improved.
Alternatively, adjusting the opening degree of the expansion valve according to the difference between the first temperature T1 and the second temperature T2 includes: setting the initial opening degree of the expansion valve to S0After a period of time, a first temperature T1 and a second temperature T2 are obtained with a period T, when T1-T2 > T x1 When the opening degree of the expansion valve is increased, the opening degree of the expansion valve is increased; when T1-T2 < -T x1 While decreasing the opening degree of the expansion valve, wherein T x1 Positive values.
The expansion valve is set to an initial opening degree S0, and after the operation is carried out for 3 minutes, the first temperature T1 and the second temperature T2 are obtained at regular time. Alternatively, t is 30-60 s. T is x1 ＝3℃。
When the temperature T1-T2 is higher than 3 ℃, the first temperature T1 of the refrigerant outlet of the first upper heat exchange branch is relatively higher, the refrigerant flow is relatively lower, and the heat exchange capacity is relatively lower, at the moment, the opening degree of the expansion valve is increased, the refrigerant flow and the flow speed in the first upper heat exchange branch are increased, the heat exchange capacity of the first upper heat exchange branch is improved, the difference between the first temperature T1 and the second temperature T2 is reduced, and the heat exchange uniformity of the whole heat exchanger is improved. Optionally, the first temperature T1 and the second temperature T2 are obtained every 60 seconds, and if each time T1-T2 is greater than 3 ℃, the opening degree of the expansion valve is increased each time until-1 ℃ < T1-T2 < 1 ℃.
When the temperature T1-T2 is less than-3 ℃, the first temperature T2 of the refrigerant outlet of the second lower heat exchange branch is relatively large, the refrigerant flow is relatively small, and the heat exchange capacity is relatively low, at the moment, the opening degree of the expansion valve is reduced, the refrigerant flow and the flow speed in the second lower heat exchange branch are increased, the heat exchange capacity of the second lower heat exchange branch is improved, the difference between the first temperature T1 and the second temperature T2 is reduced, and further the heat exchange uniformity of the whole heat exchanger is improved. Optionally, the first temperature T1 and the second temperature T2 are obtained every 60 seconds, and if each time T1-T2 is less than-3 ℃, the opening degree of the expansion valve is adjusted to be small each time until-1 ℃ < T1-T2 < 1 ℃.
Optionally, S0 ═ a × F + b, where a and b are constants and F is the compressor operating frequency.
The initial setting of the opening degree of the expansion valve is carried out according to the real-time operation frequency of the compressor, and the accuracy of the setting of the opening degree of the expansion valve is improved. Optionally, the value range of a is 0.8-1.2, and the value range of b is 150-250. The unit of S0 is step, and the maximum opening degree of the expansion valve is 480 steps.
Alternatively, when T1-T2 > T x1 In the meantime, the method for increasing the opening degree of the expansion valve comprises the following steps: when T1-T2 > T x1 When the expansion valve is adjusted, the expansion valve is increased by e every period T, and when T is x2 ＜T1-T2≤T x1 At this time, the expansion valve is adjusted to increase f per period t. Wherein, T x2 Is positive, and e > f.
Alternatively, T x1 ＝3℃，T x2 At 1 deg.c, t is 60 seconds, e is 6 steps, and f is 2 steps. That is, when T1-T2 > 3 ℃, the difference between the first temperature T1 and the second temperature T2 is considered to be large, and the expansion valve is adjusted to increase by 6 steps per cycle T; when the temperature is more than 1 ℃ and less than T1-T2 and less than or equal to 3 ℃, the difference between the first temperature T1 and the second temperature T2 is considered to be not great, and the expansion valve is adjusted to increase 2 steps per period T until the temperature is more than-1 ℃ and less than T1-T2 and less than 1 ℃.
Alternatively, when T1-T2 < -T x1 When the opening degree of the expansion valve is reduced, the method comprises the following steps: when T1-T2 < -T x1 When the expansion valve is adjusted to decrease e per period T, when-T x1 ＜T1-T2≤-T x2 The expansion valve is adjusted to decrease f every period t.
Alternatively, T x1 ＝3℃，T x2 At 1 deg.c, t is 60 seconds, e is 6 steps, and f is 2 steps. That is, when T1-T2 < -3 ℃, the difference between the first temperature T1 and the second temperature T2 is considered to be large, and the expansion valve is adjusted to be reduced by 6 steps per cycle T; when the temperature is more than-3 ℃ and less than T1 and less than or equal to-1 ℃ from T2, the difference between the first temperature T1 and the second temperature T2 is considered to be not great, and the T of the expansion valve is adjusted to be reduced by 2 steps every period until the temperature is more than-1 ℃ and less than T1 and less than T2 and less than 1 ℃.
As shown in fig. 1 and 2, taking an example that the heat exchanger includes a first upper heat exchange branch, a first lower heat exchange branch and a second lower heat exchange branch, and the indoor temperature is 20 ℃/, and the outdoor temperature is 2 ℃/1 ℃, the heating capacity and power of the air conditioner are shown in table 3 below.
TABLE 3
| Stabilization phase | T1(℃) | T2(℃) | Heating power (W) | Power (W) |
| Before the expansion valve is adjusted | -6.4 | -3.4 | 3974 | 1835 |
| After the expansion valve is adjusted | -5.2 | -5.5 | 4289 | 1776 |
The outlet temperatures of the first upper heat exchange branch and the second lower heat exchange branch are obtained in the stable operation stage of the air conditioner, before the opening of the expansion valve is adjusted, the temperature T1 is-6.4 ℃, the temperature T2 is-3.4 ℃, the temperature difference between the two outlets is large, and the heating capacity of the air conditioner is 3974W at this time; after the opening degree of the expansion valve is adjusted, the T1 is-5.2 ℃, the T2 is-5.5 ℃, the temperature difference between the two outlets is not large, the heat exchange capacity of each heat exchange branch of the heat exchanger is uniform, and the heating capacity of the air conditioner is 4289W. Therefore, the method provided by the embodiment of the disclosure improves the heating capacity of the air conditioner.
Optionally, the method for adjusting the temperature of the refrigerant in the heat exchanger further includes: when is-T x2 ＜T1-T2≤T x2 The opening degree of the expansion valve is controlled to be unchanged.
Alternatively, T x2 1 ℃ is set. When the temperature is between-1 ℃ and T1 and T2 are less than or equal to 1 ℃, the first upper heat exchange branch is considered to beThe difference between the outlet temperature of the first lower heat exchange branch and the outlet temperature of the second lower heat exchange branch is small, the heat exchanger is considered to have uniform heat exchange, and the opening degree of an expansion valve on a bypass pipeline does not need to be adjusted.
The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.
Claims (10)
1. A heat exchanger is characterized in that when an air conditioner operates in a heating working condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises:
the first heat exchange part comprises N upper heat exchange branches;
the second heat exchange part is arranged at the lower part of the first heat exchange part and comprises M lower heat exchange branches which are communicated in parallel; and the combination of (a) and (b),
a first bypass pipeline for communicating the refrigerant outlet end of the first heat exchange part with the refrigerant outlet end of the second heat exchange part, the first bypass pipeline being provided with a first solenoid valve,
wherein N is more than or equal to M-1, and M is more than or equal to 2.
2. The heat exchanger of claim 1, wherein the first heat exchanging portion comprises a first upper heat exchanging branch and a second upper heat exchanging branch, and the second heat exchanging portion comprises a first lower heat exchanging branch and a second lower heat exchanging branch, the heat exchanger further comprising:
the first liquid separator is arranged at the liquid inlet of the heat exchanger, and one liquid separating branch pipe of the first liquid separator is communicated with the refrigerant inlet end of the second lower heat exchange branch pipe;
the liquid separating branch pipes of the second liquid separator are respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch pipe, the second upper heat exchange branch pipe and the first lower heat exchange branch pipe one by one; and the combination of (a) and (b),
and the second bypass pipeline is communicated with the first liquid separator and the second liquid separator and is provided with a second electromagnetic valve and an expansion valve.
3. The heat exchanger of claim 2,
the expansion valve is arranged at the upper part of the second electromagnetic valve.
4. The heat exchanger according to claim 2 or 3, further comprising a first control portion configured to:
and adjusting the opening degree of the expansion valve according to the current outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch, the second upper heat exchange branch and the first lower heat exchange branch.
5. The heat exchanger according to claim 2 or 3,
the first upper heat exchange branch, the second upper heat exchange branch, the first lower heat exchange branch and the second lower heat exchange branch are arranged from top to bottom.
6. The heat exchanger of claim 5, further comprising a second controller configured to:
obtaining a first temperature of a refrigerant outlet end of the first upper heat exchange branch and a second temperature of a refrigerant outlet end of the second lower heat exchange branch,
and adjusting the opening degree of the expansion valve according to the difference value of the first temperature and the second temperature.
7. The heat exchanger of claim 2, wherein the first liquid separator comprises:
the liquid separation device comprises a shell, a liquid separation device and a liquid separation device, wherein a liquid separation cavity is formed in the shell, and a first liquid separation port and a second liquid separation port are formed in the shell;
the collecting pipe comprises a first pipe section and a second pipe section which are communicated in a bending mode, and the first pipe section is directly communicated with the liquid separation cavity;
the first liquid dividing branch pipe is communicated with the liquid dividing cavity through the first liquid dividing port and communicated with the second bypass pipeline; and the combination of (a) and (b),
a second branch liquid dividing pipe communicated with the liquid dividing cavity through the second liquid dividing port and communicated with the third heat exchange part,
the plane of the axes of the first pipe section and the second pipe section is a first plane, the plane of the axes of the first branch liquid distribution pipe and the second branch liquid distribution pipe is a second plane, and the first plane is not perpendicular to the second plane.
8. The heat exchanger of claim 7,
the included angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees; alternatively, the first and second electrodes may be,
the included angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees.
9. The heat exchanger of claim 8,
the inner diameter of the first liquid-splitting branch pipe is greater than or equal to 5.1mm and less than or equal to 6.1 mm;
the inner diameter of the second branch liquid-dividing pipe is more than or equal to 3.1mm and less than or equal to 3.7 mm.
10. An air conditioner characterized by comprising the heat exchanger according to any one of claims 1 to 9.
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| CN202111296069.XA Pending CN113932494A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296071.7A Pending CN113932495A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296063.2A Pending CN113932492A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294514.9A Pending CN113899120A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296058.1A Pending CN113932486A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger and refrigeration cycle system |
| CN202111294515.3A Pending CN113899121A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
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| CN202111296094.8A Pending CN113932496A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
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| CN202111294506.4A Pending CN113899116A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger and refrigeration cycle system |
| CN202111294553.9A Pending CN113899122A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294475.2A Pending CN113899118A (en) | 2021-09-19 | 2021-11-03 | Refrigeration cycle system and air conditioner |
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| CN202111296098.6A Pending CN113932497A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296116.0A Pending CN113932498A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296068.5A Pending CN113932493A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296053.9A Pending CN113932491A (en) | 2021-09-19 | 2021-11-03 | One-way valve, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294565.1A Pending CN113932484A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
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| CN202210190720.3A Active CN114838531B (en) | 2021-09-19 | 2022-02-28 | Method and device for adjusting temperature of refrigerant in heat exchanger and air conditioner |
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Effective date of registration: 20231107 Address after: No. 118 Jinliu South Road, Zhengzhou Economic and Technological Development Zone, Henan Province, 450048 Applicant after: ZHENGZHOU HAIER AIR CONDITIONER Co.,Ltd. Applicant after: QINGDAO HAIER AIR CONDITIONER GENERAL Corp.,Ltd. Applicant after: Haier Zhijia Co.,Ltd. Address before: 266101 Haier Industrial Park, 1 Haier Road, Laoshan District, Shandong, Qingdao Applicant before: QINGDAO HAIER AIR CONDITIONER GENERAL Corp.,Ltd. Applicant before: QINGDAO HAIER AIR-CONDITIONING ELECTRONIC Co.,Ltd. Applicant before: Haier Zhijia Co.,Ltd. |
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