CN114838532B - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
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- CN114838532B CN114838532B CN202210193339.2A CN202210193339A CN114838532B CN 114838532 B CN114838532 B CN 114838532B CN 202210193339 A CN202210193339 A CN 202210193339A CN 114838532 B CN114838532 B CN 114838532B
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- heat exchanger
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- plane
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- 239000003507 refrigerant Substances 0.000 claims abstract description 111
- 238000010438 heat treatment Methods 0.000 claims abstract description 36
- 239000007788 liquid Substances 0.000 claims description 95
- 238000000926 separation method Methods 0.000 claims description 29
- 230000001105 regulatory effect Effects 0.000 claims description 11
- 238000004891 communication Methods 0.000 claims description 5
- 238000005452 bending Methods 0.000 claims description 2
- 238000005057 refrigeration Methods 0.000 abstract description 16
- 239000003570 air Substances 0.000 description 47
- 238000000034 method Methods 0.000 description 10
- 230000005484 gravity Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000008569 process Effects 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
- 239000012080 ambient air Substances 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
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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
-
- 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
-
- 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
-
- 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, which 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. Through the arrangement of the first bypass pipeline and the first electromagnetic valve, the heat exchanger can respectively convey refrigerants through different flow paths under refrigeration and heating conditions, so that the performance requirements of the heat exchanger under different working modes can be simultaneously ensured. The application also discloses an air conditioner.
Description
The priority of chinese patent application No. 202111102392.9, entitled "knockout, one-way valve, heat exchanger, refrigeration cycle system, air conditioner," filed No. 2021, 9 and 19, is hereby incorporated by reference in its entirety.
The present application claims priority from chinese patent application No. 202111102583.5, entitled "knockout, one-way valve, heat exchanger, refrigeration cycle system, air conditioner," filed No. 2021, 9 and 20, the entire contents of which are incorporated herein by reference.
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 under heating working conditions, the outdoor heat exchanger of the air conditioner is used as an evaporator, the refrigerant in the pipe is in a low-temperature low-pressure area, the heat transfer performance is mainly constrained by the heat transfer coefficient and the pressure drop, and the more branches of the evaporator are required to be, the better the more, so that the low-temperature heating capacity of the air conditioner can be improved.
When the air conditioner operates under the refrigeration working condition, the outdoor heat exchanger of the air conditioner is used as a condenser, the refrigerant in the pipe is in a high-temperature and high-pressure area and is insensitive to pressure drop, at the moment, the heat transfer performance of the air conditioner is mainly influenced by the heat transfer coefficient, and the smaller and better the number of branches of the condenser is required, so that the high-temperature refrigerating capacity of the air conditioner can be 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, can not simultaneously meet the requirements of small number of refrigeration branches and large number of heating branches, and further can not enable the air conditioner to exert the best performance 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, and is intended to neither identify key/critical elements nor delineate the scope of such embodiments, but is intended as a prelude to the more detailed description that follows.
The embodiment of the disclosure provides a heat exchanger, and the flow path setting mode of the heat exchanger simultaneously meets the requirements of less refrigeration branches and more heating branches, so that the air conditioner can exert the best performance during refrigeration and heating.
In some embodiments, when the heat exchanger is used as an outdoor heat exchanger when the air conditioner is in a heating operation, 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 exchange portion comprises a first upper heat exchange leg and a second upper heat exchange leg, the second heat exchange portion comprises a first lower heat exchange leg and a second lower heat exchange leg, the heat exchanger further comprising: the first liquid distributor is arranged at the liquid inlet of the heat exchanger, and one liquid distribution branch pipe of the first liquid distributor is communicated with the refrigerant inlet end of the second lower heat exchange branch pipe; the plurality of 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 a second bypass pipeline which is communicated with the first liquid distributor and the second liquid distributor, and is provided with a second electromagnetic valve and an expansion valve.
In some embodiments, the expansion valve is disposed in an upper portion of the second solenoid valve.
In some embodiments, the heat exchanger further comprises a first control 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 limb, the second upper heat exchange limb, the first lower heat exchange limb, and the second lower heat exchange limb are disposed from top to bottom.
In some embodiments, the heat exchanger further comprises a second controller configured to: 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 of the expansion valve according to a difference value between the first temperature and the second temperature.
In some embodiments, the first dispenser comprises: the shell is internally provided with a liquid separating cavity, and a first liquid separating port and a second liquid separating port are formed in the shell; the collecting pipe comprises a first pipe section and a second pipe section which are in bending communication, and the first pipe section is directly communicated with the liquid separation cavity; the first liquid separation branch pipe is communicated with the liquid separation cavity through the first liquid separation port, and the first liquid separation branch pipe is communicated with the second bypass pipeline; and the second liquid separation branch pipe is communicated with the liquid separation cavity through the second liquid separation port, and the second liquid separation branch pipe is communicated with the second lower heat exchange branch pipe, wherein the planes of the axes of the first pipe section and the second pipe section are first planes, the planes of the axes of the first liquid separation branch pipe and the second liquid separation branch pipe are second planes, and the first planes are not perpendicular to the second planes.
In some embodiments, the first plane is at an angle to the second plane of 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 liquid-dividing branch tube has an inner diameter greater than or equal to 5.1mm and less than or equal to 6.1mm; the inner diameter of the second liquid branch pipe is larger than or equal to 3.1mm and smaller than or equal to 3.7mm.
The embodiment of the disclosure provides an air conditioner, which comprises the heat exchanger.
The heat exchanger and the air conditioner provided by the embodiment of the disclosure can realize the following technical effects:
the embodiment of the disclosure provides a heat exchanger, which is divided into a first heat exchange part and a second heat exchange part by upper and lower ends of a first bypass pipeline. Through the arrangement of the first bypass pipeline and the first electromagnetic valve, the heat exchanger can respectively convey refrigerants through different flow paths under refrigeration and heating conditions, so that the performance requirements of the heat exchanger under different working modes can be simultaneously ensured.
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 and not limitation in the figures of the accompanying drawings, in which like references indicate similar elements, and in which like reference numerals refer to similar elements, and in which:
FIG. 1 is a schematic view of a heat exchanger provided in an embodiment of the present disclosure;
FIG. 2 is a schematic view of another heat exchanger provided by an embodiment of the present disclosure;
FIG. 3 is a schematic view of another heat exchanger provided by an embodiment of the present disclosure;
FIG. 4 is a schematic view of another heat exchanger provided by an embodiment of the present disclosure;
FIG. 5 is a schematic view of a first dispenser according to an embodiment of the present disclosure;
fig. 6 is a schematic structural view of another first dispenser provided in an embodiment of the present disclosure.
Reference numerals:
111: a first upper heat exchange limb; 112: a second upper heat exchange limb; 113: a third upper heat exchange limb; 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 electromagnetic valve; 302: a second electromagnetic valve; 401: an expansion valve;
500: a first knockout; 511: a confluence cavity; 512: a first branch cavity; 513: a second branch cavity; 520: a manifold; 521: a first pipe section; 522: a second pipe section; 530: a first liquid-dividing branch pipe; 540: a second branch liquid pipe;
600: a second knockout; 700: a third knockout; 800: a fourth knockout;
901: a first sum-out; 902: and a second sum.
Detailed Description
So that the manner in which the features and techniques of the disclosed embodiments can be understood in more detail, a more particular description of the embodiments of the disclosure, briefly summarized below, may be had by reference to the appended drawings, which are not intended to be limiting of the embodiments of the disclosure. 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 still be practiced without these details. In other instances, well-known structures and devices may be shown simplified in order to simplify the drawing.
The terms first, second and the like in the description and in the claims of the embodiments of the disclosure and in the above-described figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate in order to describe embodiments of the present disclosure. Furthermore, the terms "comprise" and "have," as well as any variations thereof, are intended to cover a non-exclusive inclusion.
In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate an azimuth or a positional relationship based on that shown in the drawings. These terms are used primarily to better describe embodiments of the present disclosure and embodiments thereof and are not intended to limit the indicated device, element, or component to a particular orientation or to be constructed and operated in a particular orientation. Also, some of the terms described above may be used to indicate other meanings in addition to orientation or positional relationships, for example, the term "upper" may also be used to indicate some sort of attachment or connection in some cases. The specific meaning of these terms in the embodiments of the present disclosure will be understood by those of ordinary skill in the art in view of the specific circumstances.
In addition, the terms "disposed," "connected," "secured" and "affixed" are to be construed broadly. For example, "connected" may be in a fixed connection, a removable connection, or a unitary construction; may 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. The specific meaning of the above terms in the embodiments of the present disclosure may be understood by those of ordinary skill in the art according to specific circumstances.
The term "plurality" means two or more, unless otherwise indicated.
In the embodiment of the present disclosure, the character "/" indicates that the front and rear objects are an or relationship. For example, A/B represents: a or B.
The term "and/or" is an associative relationship that describes an object, meaning that there may be three relationships. For example, a and/or B, represent: a or B, or, A and B.
It should be noted that, without conflict, the embodiments of the present disclosure and features of the embodiments 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 by matching with 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.
Here, the indoor heat exchanger, the outdoor heat exchanger, the throttle valve, the compressor, the gas-liquid separator and other parts are connected through refrigerant pipelines to jointly form a refrigerant circulating system for circulating and conveying the refrigerant between the indoor machine and the outdoor machine; optionally, the refrigerant circulation system is at least limited with two refrigerant flows 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, 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 circulation system conveys the refrigerant in a second refrigerant flow direction, and after the refrigerant is discharged from the compressor, the refrigerant sequentially flows through the indoor heat exchanger, the throttle valve and the outdoor heat exchanger and then flows back to the compressor through the gas-liquid separator.
The following heat exchanger is described by taking an air conditioner operation heating working condition as an example when the heat exchanger is used as an outdoor heat exchanger. The description herein is made of the heat exchanger when it is used under specific working conditions, and it is not limited that the heat exchanger can only be used as an outdoor heat exchanger.
The embodiment of the disclosure provides a heat exchanger. As shown in fig. 1 to 4.
The heat exchanger includes a first heat exchange portion and a second heat exchange portion. The first heat exchange portion includes N upper heat exchange branches. The second heat exchange part is arranged at the lower part of the first heat exchange part, and the second heat exchange part comprises M lower heat exchange branches which are communicated in parallel. The first bypass pipe 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 greater than or equal to M-1, and M is greater than or equal to 2.
The heat exchange branch of the heat exchanger is divided into a first heat exchange part and a second heat exchange part by the upper end and the lower end of the first bypass pipeline 201. 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 may be an integer number of 1, 2, 3, 4, 5, 6, 7, etc. When the number of the upper heat exchange branches is multiple, similarly, the multiple upper heat exchange branches are communicated in parallel. M may be an integer number of 2, 3, 4, 5, 6, 7, etc. The plurality of upper heat exchange branches are communicated with the plurality of lower heat exchange branches in parallel.
As shown in fig. 1 to 4, the plurality of upper heat exchange branches of the first heat exchange portion are converged by the fourth dispenser 800, the plurality of lower heat exchange branches of the second heat exchange portion are converged by the third dispenser 700, and the first bypass pipeline 201 connects the third dispenser 700 and the fourth dispenser 800.
According to the heat exchanger provided by the embodiment of the disclosure, when the air conditioner is operated under the 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 exchange portion comprises a first upper heat exchange branch 111 and a second upper heat exchange branch 112, and the second heat exchange portion comprises a first lower heat exchange branch 121 and a second lower heat exchange branch 122. The heat exchanger further comprises a first knockout 500, a second knockout 600, a second bypass conduit 202. The first knockout 500 is disposed at the liquid inlet of the heat exchanger, and one knockout branch pipe of the first knockout 500 is communicated with the refrigerant inlet end of the second lower heat exchange branch 122. The plurality of liquid separating branches 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 with the first and second dispensers 500, 500. The second bypass line 202 is provided with a second solenoid valve 302 and an expansion valve 401.
By controlling the opening and closing states of the first electromagnetic valve 301 and the second electromagnetic valve 302, each heat exchange branch of the heat exchanger can be respectively in different refrigerant flow path forms under the refrigeration and heating conditions, and the performance requirements of the heat exchanger under different working modes can be simultaneously ensured.
Taking 3 heat exchange branches as an example, as shown in fig. 1 and 2, the first electromagnetic valve 301 and the second electromagnetic valve 302 are controlled to be closed when the air conditioner operates under a refrigeration condition. The refrigerant flows in through the first outlet 901, flows through the first upper heat exchange branch 111, the first lower heat exchange branch 121 and the second lower heat exchange branch 122 in sequence, flows out from the second outlet 902, and the number of heat exchange branches of the refrigerant flow path of the heat exchanger is small.
When the number of heat exchange branches of the heat exchanger is 4, as shown in fig. 3, under the refrigeration working condition, the first upper heat exchange branch 111 and the second upper heat exchange branch 112 are communicated in parallel; when the number of heat exchange branches of the heat exchanger is 6, as shown in fig. 4, under the refrigeration 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 communicated in parallel.
Taking 3 heat exchange branches as an example, as shown in fig. 1 and 2, when the air conditioner operates under 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 outlet 902, the first upper heat exchange branch 111, the first lower heat exchange branch 121 and the second lower heat exchange branch 122 are communicated in parallel, and flow out from the first outlet 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 electromagnetic valve 302.
When the air conditioner operates under a refrigeration condition, the pressure of the refrigerant in the second dispenser 600 is higher than that of the refrigerant in the first dispenser 500, and the valve core of the second electromagnetic valve 302 is impacted and sealed inaccurately. The expansion valve 401 is disposed at the upper part of the second electromagnetic valve 302, and the pressure difference between two ends of the second electromagnetic valve 302 can be reduced by controlling the expansion valve 401 to be closed, so that the closing reliability of the second electromagnetic valve 302 is ensured. Also, the expansion valve 401 may adjust the opening degree. Taking 3 heat exchange branches as shown in fig. 1 and fig. 2 as an example, when the air conditioner operates under a heating working condition, after the refrigerant passes through the throttling device of the air conditioner system, the circulation volume is further adjusted by the expansion valve 401, so that the number of heat exchange pipes 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 adjustment of the heat exchange volume of the heat exchanger is realized, and the energy efficiency of the air conditioner during different loads 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 disposed from top to bottom.
Optionally, the first knockout 500 includes a housing, a manifold 520, a first knockout leg 530, and a second knockout leg 540. The inside liquid chamber that divides that has of casing, first branch liquid mouth and second branch liquid mouth have been seted up to the casing. The manifold 520 includes a first leg 521 in bent communication with a second leg 522, the first leg 521 being in direct communication with the fluid distribution chamber. The first branch pipe 530 communicates with the liquid separating chamber through a first liquid separating opening, and the first branch pipe 530 communicates with the second bypass line 202. The second branch liquid pipe 540 is communicated with the liquid separating cavity through a second liquid separating opening, and the second branch liquid pipe 540 is communicated with a second lower heat exchanging branch. The axes of the first pipe segment 521 and the second pipe segment 522 are in a first plane, the axes of the first branch pipe 530 and the second branch pipe 540 are in a second plane, and the first plane is not perpendicular to the second plane. As shown in fig. 5 and 6.
Optionally, 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; 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. Optionally, the inner diameter of the first branch 530 is greater than or equal to 5.1mm and less than or equal to 6.1mm. The second branch pipe 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 liquid separating branch pipe 530 communicates with the first branch chamber 512 through a first liquid separating port, and the second liquid separating branch pipe 540 communicates with the second branch chamber 513 through a second liquid separating port.
The collecting pipe 520 comprises a first pipe section 521 and a second pipe section 522, wherein the plane where the axes of the first pipe section 521 and the second pipe section 522 are located 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 an acute angle formed by the two planes. The first plane is non-perpendicular to the second plane such that the amount of refrigerant entering the first branch 530 and the second branch 540 through the first pipe segment 521 is different. For example, when the angle between the first plane and the second plane is on the side of the first branch pipe 530, the flow rate of the refrigerant flowing to the second branch pipe 540 is greater than the flow rate flowing to the first branch pipe 530 by the gravity. Similarly, when the included angle between the first plane and the second plane is on the side of the second branch pipe 540, the flow rate of the refrigerant flowing to the first branch pipe 530 is greater than the flow rate of the second branch pipe 540 under the action of gravity.
Taking the heat exchanger shown in fig. 3 as an example, when the heat exchanger is used as an evaporator in a heating condition, the refrigerant flows into four parallel heat exchange branches, namely, 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 after being split by the first liquid splitter 500. The refrigerant flows into the second lower heat exchange branch 122 only after passing through the liquid separation branch pipe on the left side of the first liquid separator 500, and flows into the three heat exchange branches, namely the first upper heat exchange branch 111, the second upper heat exchange branch 112 and the first lower heat exchange branch 121, after passing through the liquid separation branch pipe on the right side of the first liquid separator 500. It can be seen that after the refrigerant passes through the first dispenser 500, the refrigerant amounts required by the two liquid-dividing branch pipes of the first dispenser 500 are different. The amount of refrigerant required by the liquid-separating branch pipe on the right side is 3 times that of the liquid-separating branch pipe on the left side. According to the liquid separator provided by the embodiment of the disclosure, by utilizing the gravity action of the refrigerant in the flowing process, through the arrangement of the included angle 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 first liquid separating branch pipe 530 and the second liquid separating branch pipe 540 are located, different refrigerant amounts flowing out of different liquid separating branch pipes of the liquid separator are realized, the different requirements of the refrigerant amounts required by the liquid separating branch pipes are met, and then the heat exchange efficiency of the heat exchanger is improved.
Optionally, the first plane and the second plane have an included angle of less than 90 degrees. Optionally, the included angle between the first plane and the second plane is 0 degrees, 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 flows through the first pipe section 521 of the collecting pipe 520, and then flows into the first liquid-separating branch pipe 530 and the second liquid-separating branch pipe 540 with different cold energy under the action of gravity.
Optionally, the inner diameter of the first branch 530 is larger than the inner diameter of the second branch 540. According to the liquid separator provided by the embodiment of the disclosure, through the arrangement of the included angle 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 liquid separation branch pipes are located, the difference of the inner diameters of the two liquid separation branch pipes is further matched, and the difference of the amounts of the refrigerants flowing into the two liquid separation branch pipes is further increased.
Optionally, the first pipe section 521 of the collecting pipe 520 is inclined towards the second branch pipe 540, and under the action of gravity, the inner diameter of the first branch pipe 530 is further matched to be larger than the inner diameter of the second branch pipe 540, so that more refrigerant flows into the first branch pipe 530, and the difference of refrigerant flows of the two branch pipes is further increased.
By merely defining the difference in the inner diameters of the first and second branch pipes 530 and 540, it is difficult to achieve refrigerant distribution in which the flow rate ratio of the first and second branch pipes 530 and 540 is 3:1 and even greater refrigerant flow rate difference is distributed. The reason is that the inner diameter of the liquid-dividing branch pipe has the limit of the minimum value, for example, the inner diameter of the liquid-dividing branch pipe cannot be lower than 3mm or even lower than 3.36mm, a copper pipe lower than the inner diameter is actually formed into a capillary pipe, the capillary pipe has larger flow resistance, and a throttling and depressurization effect is formed on the flow of the refrigerant, so that the power of a compressor is increased, and the performance of a system is reduced; even when the air conditioner runs under the heating working condition, the outdoor heat exchanger is seriously frosted, and the safety and the reliability of the system are affected. Because of the limitation of the minimum value of the inner diameter of the liquid-separating branch pipe, in order to realize the refrigerant distribution with the flow ratio of 3:1, the pipe diameter of the other liquid-separating branch pipe needs to be larger than 7mm, alternatively, the pipe diameter of the other liquid-separating branch pipe can be 7mm, and the outer diameter of the other liquid-separating branch pipe is generally larger than the inner diameter by 1.4mm, however, the inner diameter of a heat exchange pipe which is obviously beyond the actual use of the heat exchanger, and the common pipe diameter of the heat exchanger is 7mm, such as a fin-tube heat exchanger. Therefore, by limiting the difference in the inner diameters of the first branch pipe 530 and the second branch pipe 540, it is difficult to achieve refrigerant distribution of a refrigerant flow rate difference of even greater than that of the refrigerant distribution of the flow rate ratio of 3:1 of the first branch pipe 530 to the second branch pipe 540 within a range not exceeding the allowable pipe diameter of the heat exchange pipe in the heat exchanger.
According to the technical scheme, 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-separating branch pipes are located, and the inner diameter difference between the two liquid-separating branch pipes is further matched, so that the refrigerant flow ratio of the two liquid-separating branch pipes is 2:1-7:1, and even larger proportion refrigerant distribution requirements such as 2:1, 3:1, 4:1, 5:1, 6:1 and 7:1 can be realized within the allowable range of the heat exchange pipe diameter of the heat exchanger. The embodiment of the disclosure provides a refrigerant distribution scheme for realizing a larger flow ratio, and the inner diameter of the second liquid separation branch pipe 540 does not need to be designed too thin, and the flow of the refrigerant in the first liquid separation branch pipe 530 can be far greater than the flow of the refrigerant in the second liquid separation branch pipe 540. Therefore, the refrigerant distribution scheme of the liquid distributor provided by the embodiment of the disclosure avoids the problem that the total pressure drop of the liquid distribution branch pipe and the heat exchanger of the liquid distributor is overlarge when the refrigerant distribution ratio of the two liquid distribution branch pipes is relatively large.
Optionally, an included angle is set between a first plane where the axes of the first pipe segment 521 and the second pipe segment 522 of the manifold 520 are located and a second plane where the axes of the two branch pipes are located, where the included angle is greater than or equal to 50 degrees and less than or equal to 70 degrees. The difference in the flow rates of the refrigerants in the first and second tap branches 530 and 540 is improved.
Optionally, the inner diameter of the first liquid-dividing branch 530 is greater than or equal to 5.1mm and less than or equal to 6.1mm; the second branch pipe 540 has an inner diameter of 3.1mm or more and 3.7mm or less.
Optionally, the second pipe segment 522 of the manifold 520 is disposed obliquely to the second branch pipe 540.
When the heat exchanger is used as an evaporator in the operation heating working condition of the air conditioner, the heat exchanger can exert the optimal heat exchange capacity under the following conditions: during heating, heat in ambient air is continuously absorbed from a low-temperature liquid state, the temperature reaches a gas-liquid two-phase state along with the temperature rise, the temperature is kept at an evaporation temperature at the moment, only the phase change from the liquid state to the gas state continuously occurs, liquid refrigerants are less and less, gas refrigerants are more and more, and the temperature just becomes the gas state when reaching the outlet of the whole heat exchange branch and is 1-2 ℃ higher than the evaporation temperature. The heat exchange device is characterized in that when the outlet temperature of the heat exchange branch is overheated, all the heat exchange device is a gaseous refrigerant, the enthalpy difference of the gaseous refrigerant is small, the heat exchange capability is low, and when the overheat is too large, the heat exchange difference between the refrigerant and the ambient temperature is small, for example, when the evaporating temperature is about 0-1 ℃, if the overheat is more than 3 ℃, the temperature is above 4 ℃, and the ambient temperature in winter is about 7 ℃, the heat exchange capability of the heat exchanger is more difficult to develop.
The better the uniformity is, the easier each heat exchange branch has proper heat exchange, if the branch is uneven, the branches which are easy to have are overheated seriously, the back several hairpin tubes have no heat exchange effect, the more refrigerants of the heat exchange branch are, the more refrigerants of the whole heat exchange branch are, the more low-temperature liquid refrigerants still flow through the whole heat exchange branch, and the cold quantity is not exchanged, so that the heat exchange effect of the whole heat exchanger is poor and the capacity of the air conditioner is very low under the same refrigerant flow. Therefore, the judgment method for the good shunting of experience during heating is as follows: the outlet temperature difference of each branch is within 2 ℃, the outlet superheat degree is about 1 ℃, and the flow distribution is better under the condition.
TABLE 1
TABLE 2
Optionally, when the air conditioner is operated under heating conditions and 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 which are connected in parallel are communicated with the first liquid-dividing branch 530, and the second lower heat exchange branch 122 is communicated with the second liquid-dividing branch 540, as shown in fig. 3, the temperature of the refrigerant at the outlet of each heat exchange branch is shown in table 1 and table 2. Wherein, 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 the 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 of table 1, when the inner diameter of the first branch pipe 530 is 5.6mm and the inner diameter of the second branch pipe 540 is 3.36mm, the maximum temperature difference between the second lower heat exchanging branch 122 and the first three branches of the heat exchanger is minimum, 3.4 ℃, and the heating capacity of the air conditioner under the inner diameter is maximum, 4855.2W. Table 2 shows that when the inner diameter of the first branch pipe 530 is 5.6mm and the inner diameter of the second branch pipe 540 is 3.36mm, the included angle between the first plane and the second plane is different, and the maximum temperature difference between the second lower heat exchanging 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 1.2 ℃ and the heating capacity of the air conditioner is 5016.1W at the angle.
As can be seen from the data in tables 1 and 2, when the number of heat exchange branches communicating with the first liquid-dividing branch pipe 530 in the heat exchanger is 3, the number of heat exchange branches communicating with the second liquid-dividing branch pipe 540 is 1, for example, as in the heat exchanger shown in fig. 3, the inner diameter of the first liquid-dividing branch pipe 530 is 5.6mm, the inner diameter of the second liquid-dividing branch 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 heat exchange branch pipe 330 and the first three branch pipes is minimum, the uniformity of heat exchange capacity of the refrigerant in each heat exchange branch pipe is the best, and the heating capacity of the air conditioner is the largest. That is, the refrigerant amount ratio of the first branch pipe 530 to the second branch pipe 540 is 3:1.
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 liquid-dividing branch 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 liquid-dividing branch pipe 540 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant amount in the first liquid-dividing branch pipe 530 to the refrigerant amount in the second liquid-dividing branch pipe 540 can be better realized to be 3:1. The temperature difference and the heating capacity of the air conditioner achieved by other inner diameters and included angles in this embodiment are similar to those of the data in tables 1 and 2, and are not described in detail here.
Optionally, the heat exchanger further comprises a first control part configured to adjust 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.
When the humidity of the outdoor environment is lower, the current outdoor environment is not easy to frost, at the moment, the opening of the expansion valve can be increased, the number of heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the number of 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 increased, 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 humidity of the outdoor environment is higher, the current outdoor environment is considered to be easy to frosted, at the moment, the opening degree of the expansion valve can be reduced, the number of heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the number of 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 an air conditioning system is met.
Optionally, the heat exchanger further includes a second controller configured to obtain a first temperature of the refrigerant outlet end of the first upper heat exchange branch, and a second temperature of the refrigerant outlet end of the second lower heat exchange branch, and adjust the opening of the expansion valve according to a difference between the first temperature and the second temperature. Embodiments of the present disclosure provide an apparatus that may perform a method for adjusting a temperature of a refrigerant within a heat exchanger.
When the air conditioner is operated in winter and is in a heating working condition, the surface of the outdoor heat exchanger is easy to generate frosting when the relative humidity of the outdoor environment is high. When frosting occurs on only part of the surface of the outdoor heat exchanger, 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 refrigerant flow in the heat exchange branch with lower outlet temperature is more, the heat exchange capacity is high, and the outer surface frosts.
However, in the heat exchanger in which frosting occurs on only part of the outer surface, the wind of the outdoor fan easily passes through the frosted part with small wind resistance. As described above, the temperature of the refrigerant outlet of the heat exchange branch at the position where the outer surface is not frosted is higher, the refrigerant flow is small, the heat exchange capacity is low, and the frosted heat exchange branch at the outer surface with relatively higher heat exchange capacity is equivalent to being short-circuited because the air quantity flowing through is greatly reduced, and thus the heat exchange capacity of the heat exchange branch at the position is indirectly reduced, so that the overall heat exchange capacity of the heat exchanger is reduced.
According to the method for adjusting the temperature of the refrigerant in the heat exchanger, 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 rate and the flow rate 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.
Optionally, adjusting the opening of the expansion valve according to the difference between the first temperature T1 and the second temperature T2 includes: setting the initial opening of the expansion valve as S0, obtaining a first temperature T1 and a second temperature T2 in a period T after running for a period of time, and when T1-T2 is more than T x1 When the expansion valve is opened, the opening of the expansion valve is increased; when T1-T2 < -T x1 At the same time, the opening degree of the expansion valve is reduced, wherein T x1 Positive values.
The expansion valve is provided with an initial opening S0, and after 3 minutes of operation, the first temperature T1 and the second temperature T2 are obtained at fixed time. Alternatively, t is 30-60s. T (T) x1 =3℃。
When T1-T2 is more than 3 ℃, the first temperature T1 of the refrigerant outlet of the first upper 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 of the expansion valve is adjusted, the flow rate and the flow velocity of the refrigerant 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 then the heat exchange uniformity of the whole heat exchanger is improved. Optionally, the first temperature T1 and the second temperature T2 are obtained once every 60 seconds, and if each time T1-T2 is larger than 3 ℃, the opening of the expansion valve is regulated each time until the temperature is minus 1 ℃ and minus 1-T2 is minus 1 ℃.
When 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 flow rate and the flow velocity of the refrigerant 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 the heat exchange uniformity of the whole heat exchanger is further improved. Optionally, the first temperature T1 and the second temperature T2 are obtained once every 60 seconds, and if each time T1-T2 is smaller than-3 ℃, the opening of the expansion valve is adjusted to be smaller until the temperature is less than-1 ℃ and less than 1 ℃ at each time.
Optionally s0=a×f+b, where a, 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 running frequency of the compressor, so that the accuracy of the opening degree setting of the expansion valve is improved. Optionally, a has a value ranging from 0.8 to 1.2 and b has a value ranging from 150 to 250. The unit of S0 is a step, and the maximum opening of the expansion valve is 480 steps.
Alternatively, when T1-T2 > T x1 And when the opening degree of the expansion valve is increased, the method comprises the following steps: when T1-T2 > T x1 When T, the expansion valve is regulated to increase e every period T x2 ＜T1-T2≤T x1 And f is increased every period t of the regulating expansion valve. Wherein T is x2 Positive and e > f.
Alternatively T x1 =3℃，T x2 =1 ℃, t=60 seconds, e is 6 steps, f is 2 steps. Namely, when T1-T2 is more than 3 ℃, the difference between the first temperature T1 and the second temperature T2 is considered to be larger, and the expansion valve is regulated to be increased by 6 steps per cycle T; when the temperature T1-T2 is less than or equal to 3 ℃ and is more than 1 ℃, the difference between the first temperature T1 and the second temperature T2 is not large, and the expansion valve is regulated to increase 2 steps per cycle T until the temperature T1-T2 is less than 1 ℃ below zero.
Alternatively, when T1-T2 < -T x1 And 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 regulated, the E is reduced every period T, and when-T x1 ＜T1-T2≤-T x2 When the expansion valve is regulated, f is reduced every period t.
Alternatively T x1 =3℃，T x2 =1 ℃, t=60 seconds, e is 6 steps, 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 larger, and the expansion valve is regulated to be reduced by 6 steps per cycle T; when the temperature of T1-T2 is less than or equal to minus 3 ℃ and less than or equal to minus 1 ℃, the difference between the first temperature T1 and the second temperature T2 is not large, and the expansion valve is regulated to reduce 2 steps per cycle T until the temperature of T1-T2 is less than or equal to minus 1 ℃.
As shown in fig. 1 and 2, taking an example in which the heat exchanger includes a first upper heat exchange branch, a first lower heat exchange branch, and a second lower heat exchange branch, the indoor temperature is 20 c/-, and the outdoor temperature is 2 c/1 c, the heating capacity and power of the air conditioner are shown in table 3 below.
TABLE 3 Table 3
The outlet temperatures of the first upper heat exchange branch and the second lower heat exchange branch are obtained in the operation stability stage of the air conditioner, the temperature difference between the two outlet temperatures is larger when the heating capacity of the air conditioner is 3974W before the opening degree of the expansion valve is adjusted, and the temperature T1 is-6.4 ℃ and the temperature T2 is-3.4 ℃; after the opening degree of the expansion valve is regulated, T1 is-5.2 ℃, T2 is-5.5 ℃, the difference between the temperatures of 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 comprises: when-T x2 ＜T1-T2≤T x2 And controlling the opening degree of the expansion valve to be unchanged.
Alternatively T x2 =1 ℃. When the temperature T1-T2 is less than or equal to minus 1 ℃, the outlet temperature of the first upper heat exchange branch and the outlet temperature of the second lower heat exchange branch are considered to be slightly different, the whole heat exchange of the heat exchanger is considered to be uniform, and the opening of the expansion valve on the bypass pipeline is not required to be adjusted.
The above description and the drawings illustrate embodiments of the disclosure sufficiently to enable those skilled in the art to practice them. Other embodiments may include structural and other modifications. The embodiments represent only 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 (7)
1. A heat exchanger, wherein when the air conditioner is operating in a heating condition and the heat exchanger is an outdoor heat exchanger, the heat exchanger comprises:
the first heat exchange part comprises N upper heat exchange branches, and the first heat exchange part comprises a first upper heat exchange branch and a second upper heat exchange branch;
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 second heat exchange part comprises a first lower heat exchange branch and a second lower heat exchange branch; wherein N is more than or equal to M-1, and M is more than or equal to 2,
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;
the first liquid distributor is arranged at the liquid inlet of the heat exchanger, and one liquid distribution branch pipe of the first liquid distributor is communicated with the refrigerant inlet end of the second lower heat exchange branch pipe;
the plurality of 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, a step of, in the first embodiment,
a second bypass pipeline which is communicated with the first liquid distributor and the second liquid distributor, and is provided with a second electromagnetic valve and an expansion valve,
a first control part configured to adjust the opening degree of the expansion valve according to the current outdoor environment humidity 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,
a second control part configured to obtain a first temperature T1 of the refrigerant outlet end of the first upper heat exchange branch and a second temperature T2 of the refrigerant outlet end of the second lower heat exchange branch, adjust the opening of the expansion valve according to the difference between the first temperature T1 and the second temperature T2, set the initial opening of the expansion valve as S0, obtain the first temperature T1 and the second temperature T2 at a period T after a period of operation, and when T1-T2 > T x1 When T, the expansion valve is regulated to increase e every period T x2 ＜T1-T2≤T x1 Adjusting the expansion valve to increase f every cycle t; when T1-T2 < -T x1 And reducing the opening of the expansion valve, wherein T x1 Positive value, T x2 Positive and e > f.
2. A heat exchanger according to claim 1 wherein,
the expansion valve is arranged at the upper part of the second electromagnetic valve.
3. A heat exchanger according to claim 1 wherein,
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.
4. The heat exchanger of claim 1, wherein the first knockout comprises:
the shell is internally provided with a liquid separating cavity, and a first liquid separating port and a second liquid separating port are formed in the shell;
the collecting pipe comprises a first pipe section and a second pipe section which are in bending communication, and the first pipe section is directly communicated with the liquid separation cavity;
the first liquid separation branch pipe is communicated with the liquid separation cavity through the first liquid separation port, and the first liquid separation branch pipe is communicated with the second bypass pipeline; and, a step of, in the first embodiment,
the second liquid separation branch pipe is communicated with the liquid separation cavity through the second liquid separation port, and is communicated with the second lower heat exchange branch pipe,
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 liquid separation branch pipe and the second liquid separation branch pipe are located is a second plane, and the first plane is not perpendicular to the second plane.
5. The heat exchanger of claim 4, wherein the heat exchanger is configured to heat the heat exchanger,
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; or,
the included angle between the first plane and the second plane is larger than or equal to 30 degrees and smaller than or equal to 60 degrees.
6. The heat exchanger according to claim 5, wherein,
the inner diameter of the first liquid distribution branch pipe is larger than or equal to 5.1mm and smaller than or equal to 6.1mm;
the inner diameter of the second liquid branch pipe is larger than or equal to 3.1mm and smaller than or equal to 3.7mm.
7. An air conditioner comprising the heat exchanger according to any one of claims 1 to 6.
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| CN202111102392 | 2021-09-19 | ||
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| CN202111102583 | 2021-09-20 |
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| CN202111310195.6A Pending CN113932499A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296094.8A Pending CN113932496A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296049.2A Pending CN113932485A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger and refrigeration cycle system |
| CN202111294492.6A Pending CN113883758A (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 |
| CN202111296053.9A Pending CN113932491A (en) | 2021-09-19 | 2021-11-03 | One-way valve, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294553.9A Pending CN113899122A (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 |
| CN202111296098.6A Pending CN113932497A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294515.3A Pending CN113899121A (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 |
| CN202111296063.2A Pending CN113932492A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296100.XA Pending CN114165947A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294494.5A Pending CN113865156A (en) | 2021-09-19 | 2021-11-03 | One-way valve, 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 |
| CN202111296058.1A Pending CN113932486A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger and refrigeration cycle system |
| CN202111296108.6A Pending CN113932488A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296106.7A Pending CN113932487A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296122.6A Pending CN113932489A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296069.XA Pending CN113932494A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294510.0A Pending CN113899119A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
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| CN202210193339.2A Active CN114838532B (en) | 2021-09-19 | 2022-02-28 | Heat exchanger 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 |
| CN202111296049.2A Pending CN113932485A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger and refrigeration cycle system |
| CN202111294492.6A Pending CN113883758A (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 |
| CN202111296053.9A Pending CN113932491A (en) | 2021-09-19 | 2021-11-03 | One-way valve, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294553.9A Pending CN113899122A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, 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 |
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| CN202111296108.6A Pending CN113932488A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296106.7A Pending CN113932487A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296122.6A Pending CN113932489A (en) | 2021-09-19 | 2021-11-03 | Heat exchanger, refrigeration cycle system and air conditioner |
| CN202111296069.XA Pending CN113932494A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, heat exchanger, refrigeration cycle system and air conditioner |
| CN202111294510.0A Pending CN113899119A (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 |
| CN202111296068.5A Pending CN113932493A (en) | 2021-09-19 | 2021-11-03 | Liquid separator, 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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