CN114838529B - Method and device for adjusting heat exchange volume of heat exchanger and air conditioner - Google Patents

Method and device for adjusting heat exchange volume of heat exchanger and air conditioner Download PDF

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Publication number
CN114838529B
CN114838529B CN202210190739.8A CN202210190739A CN114838529B CN 114838529 B CN114838529 B CN 114838529B CN 202210190739 A CN202210190739 A CN 202210190739A CN 114838529 B CN114838529 B CN 114838529B
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China
Prior art keywords
heat exchange
branch
heat exchanger
fmax
tao
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CN202210190739.8A
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Chinese (zh)
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CN114838529A (en
Inventor
劳春峰
张心怡
王飞
许文明
李阳
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HEFEI HAIER AIR CONDITIONER CO Ltd
Qingdao Haier Air Conditioner Gen Corp Ltd
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
Original Assignee
HEFEI HAIER AIR CONDITIONER CO Ltd
Qingdao Haier Air Conditioner Gen Corp Ltd
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The application relates to the technical field of air conditioners, and discloses a method for adjusting heat exchange volume of a heat exchanger, which comprises the following steps: and adjusting the expansion valve to a set opening degree according to the outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch. According to the opening degree of the expansion valve arranged on the bypass pipeline and adjusted according to the outdoor environment humidity, the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch of the heat exchanger are adjusted, so that the heat exchange volume of the whole heat exchanger is adjusted, and the heat exchanger can enable an air conditioning system to have better energy efficiency under different loads. The application also discloses a device for adjusting the heat exchange volume of the heat exchanger and an air conditioner.

Description

Method and device for adjusting heat exchange volume of heat exchanger and air conditioner
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 present application relates to the technical field of air conditioners, and for example, to a method and an apparatus for adjusting a heat exchange volume of a heat exchanger, and an air conditioner.
Background
The air conditioner comprises an indoor heat exchanger arranged in the indoor unit and an outdoor heat exchanger arranged in the outdoor unit. A specific refrigerant flow path is generally arranged on the heat exchanger so as to improve the heat exchange capability of the heat exchanger under refrigeration working conditions or heating working conditions.
When the outdoor heat exchanger is used as a condenser under the refrigeration working condition, the smaller the branch number of the refrigerant of the outdoor heat exchanger is, the better the branch number is, so that the high-temperature refrigeration capacity of the air conditioner is improved; when in heating working condition, the outdoor heat exchanger is used as an evaporator, and the more and better the branch quantity of the refrigerant of the outdoor heat exchanger is needed, the lower temperature heating quantity of the air conditioner is 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, the heat exchange volume of the heat exchanger is fixed, and the efficient energy-saving operation of the air conditioner under different loads cannot be met.
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 method and device for adjusting heat exchange volume of a heat exchanger and an air conditioner.
In some embodiments, when the air conditioner is operating in a heating operating condition and the heat exchanger is an outdoor heat exchanger, the heat exchanger comprises: a first heat exchange portion including a first upper heat exchange branch; the second heat exchange part is communicated with the first heat exchange part in parallel and comprises a first lower heat exchange branch and a second lower heat exchange branch which are communicated in parallel; the first liquid distributor is arranged at the liquid inlet of the heat exchanger and is communicated with the refrigerant inlet end of the second lower heat exchange branch; the second liquid separator is respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch and the first lower heat exchange branch one by one; and a bypass line communicating the first and second dispensers, and provided with an expansion valve, the method for adjusting the heat exchange volume of the heat exchanger comprising: and adjusting the expansion valve to a set opening degree according to the outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch.
In some embodiments, the adjusting the expansion valve to a set opening according to the outdoor environment humidity includes: and if the recent outdoor environment humidity is smaller than the outdoor environment humidity statistic value of the past year, adjusting the expansion valve to the maximum opening degree so that the first upper heat exchange branch and the first lower heat exchange branch operate with the maximum heat exchange volume.
In some embodiments, after adjusting the expansion valve to a maximum opening, further comprising: the maximum operating frequency Fmax of the compressor is determined according to the current outdoor environment temperature Tao, and the minimum operating frequency lim_l of the compressor is determined according to the difference between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operating frequency Fmax of the compressor.
In some embodiments, lim_l=a×fmax when Tr-tao+.Δt1, lim_l=b×fmax when Δt1 < Tr-tao+.Δt2, lim_l=c×fmax when Tr-Tao > - Δt2, where 0 < a < b < c < 1.
In some embodiments, the adjusting the expansion valve to a set opening according to the outdoor environment humidity includes: and if the recent outdoor environment humidity is greater than or equal to the outdoor environment humidity statistic value of the past year, reducing the opening degree of the expansion valve to Sx so as to reduce the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch.
In some embodiments, sx is 0.4-0.7 times the maximum opening value of the expansion valve.
In some embodiments, after adjusting the opening of the expansion valve to Sx, the method further includes: when Tr-Tao is less than or equal to DeltaT 1, lim_L=x and Fmax are equal to or greater than a temperature threshold value, when DeltaT 1 is less than Tr-Tao is less than DeltaT 2, lim_L=y and Fmax are equal to or greater than a temperature threshold value, and when Tr-Tao is greater than DeltaT 2, lim_L=z and Fmax are equal to or greater than a temperature threshold value; or when the surface temperature difference of the heat exchanger in unit time is smaller than a temperature threshold value, lim_l=m×fmax when Tr-Tao is less than or equal to Δt1, lim_l=n×fmax when Δt1 is less than or equal to Tr-Tao is less than or equal to Δt2, or lim_l=p×fmax when Tr-Tao is more than Δt2, wherein lim_l is the minimum operation frequency of the compressor, fmax is the maximum operation frequency of the compressor, 0 < x < y < z < 1,0 < m < n < p < 1, and x > m.
In some embodiments, y > n, and/or z > p.
In some embodiments, when the air conditioner is operating in a heating operating condition and the heat exchanger is an outdoor heat exchanger, the heat exchanger comprises: a first heat exchange portion including a first upper heat exchange branch; the second heat exchange part is communicated with the first heat exchange part in parallel and comprises a first lower heat exchange branch and a second lower heat exchange branch which are communicated in parallel; the first liquid distributor is arranged at the liquid inlet of the heat exchanger and is communicated with the refrigerant inlet end of the second lower heat exchange branch; the second liquid separator is respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch and the first lower heat exchange branch one by one; and a bypass line communicating the first and second dispensers, and provided with an expansion valve, the means for adjusting the heat exchange volume of the heat exchanger comprising: and the volume adjusting module is configured to adjust the expansion valve to a set opening degree according to the outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch.
In some embodiments, an apparatus for adjusting the heat exchange volume of a heat exchanger includes a processor and a memory storing program instructions, the processor being configured to perform a method for adjusting the heat exchange volume of a heat exchanger as previously described when the program instructions are executed.
In some embodiments, the air conditioner comprises a device for adjusting the heat exchange volume of the heat exchanger as previously described.
The method and the device for adjusting the heat exchange volume of the heat exchanger and the air conditioner provided by the embodiment of the disclosure can realize the following technical effects:
according to the opening degree of the expansion valve arranged on the bypass pipeline and adjusted according to the outdoor environment humidity, the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch of the heat exchanger are adjusted, so that the heat exchange volume of the whole heat exchanger is adjusted, and the heat exchanger can enable an air conditioning system to have better energy efficiency under different loads.
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 flow diagram of a method for adjusting a heat exchange volume of a heat exchanger provided by an embodiment of the present disclosure;
FIG. 2 is a schematic view of a heat exchanger provided in 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 another heat exchanger provided by an embodiment of the present disclosure;
FIG. 6 is a schematic view of a first dispenser provided in an embodiment of the disclosure;
fig. 7 is a schematic structural view of another first dispenser provided in an embodiment of the 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.
Embodiments of the present disclosure provide methods for adjusting a heat exchange volume of a heat exchanger.
When the air conditioner operates in a heating working condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises a first heat exchange part, a second heat exchange part, a first liquid distributor, a second liquid distributor and a bypass pipeline. The first heat exchange portion includes a first upper heat exchange branch. The second heat exchange part is communicated with the first heat exchange part in parallel, and comprises a first lower heat exchange branch and a second lower heat exchange branch which are communicated in parallel. The first liquid distributor is arranged at the liquid inlet of the heat exchanger and is communicated with the refrigerant inlet end of the second lower heat exchange branch. The second liquid distributor is respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch and the first lower heat exchange branch one by one. The bypass pipeline is communicated with the first liquid distributor and the second liquid distributor, and the bypass pipeline is provided with an expansion valve.
As shown in fig. 1, the method for adjusting the heat exchange volume of the heat exchanger includes:
S1, adjusting an expansion valve to a set opening degree according to outdoor environment humidity so as to adjust heat exchange volumes of a first upper heat exchange branch and a 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.
The humidity of the outdoor environment may be relative humidity, and the humidity of both the recent outdoor environment and the past year outdoor environment described below may be relative humidity.
Optionally, adjusting the expansion valve to a set opening according to the outdoor environment humidity includes: and if the recent outdoor environment humidity is smaller than the outdoor environment humidity statistic value of the past year, adjusting the expansion valve to the maximum opening degree so that the first upper heat exchange branch and the first lower heat exchange branch operate with the maximum heat exchange volume.
The moisture content in air is related to relative humidity and temperature, where recent outdoor ambient temperatures generally do not differ much from ambient outdoor temperatures over the years. Optionally, if the statistics value of the recent outdoor environment humidity is smaller than the statistics value of the outdoor environment humidity of the past year, the moisture content in the recent air is considered to be smaller, at this time, the expansion valve can be adjusted to the maximum opening degree while the defrosting frequency of the past year is used, so that all the heat exchange tubes in the first upper heat exchange branch and the first lower heat exchange branch participate in heat exchange, the heat exchanger operates with the maximum heat exchange volume, and the heat exchange capacity of the heat exchanger is improved.
Alternatively, the maximum opening of the solenoid valve is 480 steps. Alternatively, the defrost frequency over the years and the defrost frequency that occurs below may each defrost every 1-3 hours.
Alternatively, the recent outdoor environmental humidity statistic may be a recent daily average humidity statistic, a recent month average humidity statistic, a recent quarter average humidity statistic, or the like. The outdoor environmental humidity statistics of the past year can be the average humidity statistics of the present day of the past year, the average humidity statistics of the month of the past year, the average humidity statistics of the quarter of the past year, and the like. The calendar year may be approximately 3-5 years. The near future average humidity statistics may be compared to the past year today average humidity statistics, the near future month average humidity statistics may be compared to the past year month average humidity statistics, or the near future quarter average humidity statistics may be compared to the past year quarter average humidity statistics. For example, the average outdoor environment humidity is 35% today, and the average outdoor environment humidity is 40% today for 3 years, so that the expansion valve can be adjusted to the maximum opening.
Optionally, after adjusting the expansion valve to the maximum opening degree, the method further includes: the maximum operating frequency Fmax of the compressor is determined according to the current outdoor environment temperature Tao, and the minimum operating frequency lim_l of the compressor is determined according to the difference between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operating frequency Fmax of the compressor.
After the expansion valve is regulated to the maximum opening degree, the maximum operation frequency Fmax and the minimum operation frequency lim_l of the compressor under the current maximum opening degree of the expansion valve are further regulated, so that the compressor operates between the maximum operation frequency Fmax and the minimum operation frequency lim_l, and the operation capacity of the whole air conditioning system is regulated. Under the condition of defrosting frequency in the past years, if the recent outdoor environment humidity is relatively low, the opening degree of the expansion valve can be adjusted to the maximum opening degree, and meanwhile, the minimum operating frequency of the compressor is adjusted to be high, so that the operating capacity of the whole air conditioning system is improved, and the requirement of a user on indoor temperature adjustment is further met.
Optionally, lim_l=a×fmax when Tr-Tao is less than or equal to Δt1, lim_l=b×fmax when Δt1 < Tr-Tao is less than or equal to Δt2, and lim_l=c×fmax when Tr-Tao is > - Δt2, wherein 0 < a < b < c < 1.
Alternatively, Δt1 may be 3 ℃, Δt2 may be 10 ℃, a=0.3, b=0.5, c=0.6. Under the condition that the defrosting frequency is used for a long time, the minimum operating frequency lim_L of the compressor is further improved according to the difference value between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operating frequency Fmax of the compressor, and then the energy efficiency of the whole air conditioning system is adjusted.
Optionally, adjusting the expansion valve to a set opening according to the outdoor environment humidity includes: and if the recent outdoor environment humidity is greater than or equal to the outdoor environment humidity statistic value of the past year, the opening degree of the expansion valve is adjusted to Sx so as to reduce the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch.
If the statistic value of the recent outdoor environment humidity is greater than or equal to the statistic value of the outdoor environment humidity of the past year, the moisture content in the recent air is considered to be large, and at the moment, the opening degree of the expansion valve can be reduced to Sx while the defrosting frequency of the past year is used, so that 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. For example, the first upper heat exchange branch and the first lower heat exchange branch each include 6 heat exchange tubes, and after the opening degree of the expansion valve is adjusted to Sx, the number of the heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the first lower heat exchange branch is 4. Therefore, the air conditioner still can normally operate under the defrosting frequency of the air conditioner for years without frequent defrosting.
Optionally, sx is 0.4-0.7 times the maximum opening value of the expansion valve.
For example, the maximum opening of the expansion valve is 480 steps, and Sx is 200-300 steps.
Optionally, after adjusting the opening of the expansion valve to Sx, the method for adjusting the heat exchange volume of the heat exchanger further includes:
under the condition that the difference value of the surface temperature of the heat exchanger in unit time is larger than or equal to the temperature threshold value,
when Tr-Tao is less than or equal to DeltaT 1, lim_L=x.times.fmax,
when DeltaT 1 < Tr-Tao < DeltaT 2, lim_L=y.fmax,
when Tr-Tao > - Δt2, lim_l=z×fmax.
Alternatively, Δt1 may be 3 ℃, Δt2 may be 10 ℃, x=0.3, y=0.5, z=0.6. Under the condition that the defrosting frequency is used for a long time, the minimum operating frequency lim_L of the compressor is further adjusted according to the difference value between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operating frequency Fmax of the compressor, and then the energy efficiency of the whole air conditioning system is adjusted.
Optionally, after adjusting the opening of the expansion valve to Sx, the method for adjusting the heat exchange volume of the heat exchanger further includes:
under the condition that the difference value of the surface temperature of the heat exchanger in unit time is larger than or equal to the temperature threshold value,
when Tr-Tao is less than or equal to DeltaT 1, lim_L=m.times.fmax,
When DeltaT 1 < Tr-Tao < DeltaT 2, lim_L=n.fmax, or,
when Tr-Tao > - Δt2, lim_l=p×fmax.
Where lim_l is the minimum operating frequency of the compressor and Fmax is the maximum operating frequency of the compressor.
0 < x < y < z < 1,0 < m < n < p < 1, and x > m.
Alternatively, Δt1 may be 3 ℃, Δt2 may be 10 ℃, m=0.2, n=0.3, p=0.4. Under the condition that the defrosting frequency is used for a long time, the minimum operating frequency lim_L of the compressor is further reduced according to the difference value between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operating frequency Fmax of the compressor, and then the energy efficiency of the whole air conditioning system is adjusted.
Embodiments of the present disclosure also provide an apparatus for adjusting a heat exchange volume of a heat exchanger, comprising:
and the volume adjusting module is configured to adjust the expansion valve to a set opening degree according to the outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch.
It is to be understood that the foregoing embodiments of the method for adjusting the heat exchange volume of the heat exchanger are applicable to the apparatus herein, and will not be described herein.
Embodiments of the present disclosure also provide an apparatus for adjusting a heat exchange volume of a heat exchanger, comprising a processor and a memory storing program instructions, the processor being configured to perform a method for adjusting a heat exchange volume of a heat exchanger as previously described when the program instructions are executed.
Embodiments of the present disclosure also provide an air conditioner including a device for adjusting a heat exchange volume of a heat exchanger as described above.
The embodiment of the disclosure also provides a heat exchanger, which can be used for the method, the device and the air conditioner for adjusting the heat exchange volume of the heat exchanger, as shown in fig. 2-7.
It will be appreciated that the aforementioned method, apparatus and bypass line in an air conditioner for adjusting the heat exchange volume of a heat exchanger is a second bypass line in the heat exchanger.
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. 2 to 5, 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. 2 and 3, 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. 4, 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. 5, 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. 2 and 3, when the air conditioner is in a heating working 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. 2 and 3 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 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 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 pipe 540 is communicated with the liquid separating cavity through a second liquid separating port, and the second branch pipe 540 is communicated with the third heat exchanging part. 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. 6 and 7.
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. 7. 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. 4 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 capacity of the heat exchanger is more difficult to develop because the refrigerant and the ambient temperature exchange temperature difference is small when the outlet temperature of the heat exchange branch is overheated, the refrigerant is all the gaseous refrigerant, the enthalpy difference of the gaseous refrigerant is small, the heat exchange capacity is low, and the refrigerant and the ambient temperature exchange temperature difference is small when the overheat is too large, 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 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 2
TABLE 3 Table 3
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. 4, the temperatures of the refrigerants at the outlets of the heat exchange branches are shown in tables 2 and 3. Wherein, table 2 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 when the included angle between the first plane and the second plane is 90 degrees, and the inner diameters of the first liquid-dividing branch 530 and the second liquid-dividing branch 540 are different. As can be seen from the data of table 2, 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 3 shows 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 when the inner diameter of the first branch 530 is 5.6mm and the inner diameter of the second branch 540 is 3.36 mm. As can be seen from table 3, 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 2 and 3, 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. 4, 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 2 and 3, and are not described in detail here.
The flowcharts and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of systems, methods and computer program products according to embodiments of the present disclosure. In this regard, each block in the flowchart or block diagrams may represent a module, segment, or portion of code, which comprises one or more executable instructions for implementing the specified logical function(s). In some alternative implementations, the functions noted in the block may occur out of the order noted in the figures. For example, two blocks shown in succession may, in fact, be executed substantially concurrently, or the blocks may sometimes be executed in the reverse order, depending upon the functionality involved. In the description corresponding to the flowcharts and block diagrams in the figures, operations or steps corresponding to different blocks may also occur in different orders than that disclosed in the description, and sometimes no specific order exists between different operations or steps. For example, two consecutive operations or steps may actually be performed substantially in parallel, they may sometimes be performed in reverse order, which may be dependent on the functions involved. Each block of the block diagrams and/or flowchart illustration, and combinations of blocks in the block diagrams and/or flowchart illustration, can be implemented by special purpose hardware-based systems which perform the specified functions or acts, or combinations of special purpose hardware and computer instructions.

Claims (8)

1. A method for adjusting the heat exchange volume of a heat exchanger, wherein when the air conditioner is operating in a heating operating condition and the heat exchanger is an outdoor heat exchanger, the heat exchanger comprises:
a first heat exchange portion including a first upper heat exchange branch;
the second heat exchange part is communicated with the first heat exchange part in parallel and comprises a first lower heat exchange branch and a second lower heat exchange branch which are communicated in parallel;
the first liquid distributor is arranged at the liquid inlet of the heat exchanger and is communicated with the refrigerant inlet end of the second lower heat exchange branch;
the second liquid separator is respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch and the first lower heat exchange branch one by one; and, a step of, in the first embodiment,
a bypass pipeline which is communicated with the first liquid distributor and the second liquid distributor and is provided with an expansion valve,
the method for adjusting the heat exchange volume of the heat exchanger comprises the following steps:
adjusting the expansion valve to a set opening degree according to outdoor environment humidity so as to adjust heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch, and adjusting the expansion valve to a maximum opening degree if the recent outdoor environment humidity is smaller than an outdoor environment humidity statistic value of the past year so that the first upper heat exchange branch and the first lower heat exchange branch run at the maximum heat exchange volume;
Determining a compressor maximum operating frequency Fmax according to the current outdoor environment temperature Tao, determining a compressor minimum operating frequency lim_l according to a difference between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the compressor maximum operating frequency Fmax,
when Tr-Tao is less than or equal to Δt1, lim_l=a×fmax,
when DeltaT 1 < Tr-Tao < DeltaT 2, lim_L=b.fmax,
when Tr-Tao > - Δt2, lim_l=c x Fmax,
wherein, a is more than 0 and b is more than 0 and c is more than 1.
2. The method of claim 1, wherein the adjusting the expansion valve to a set opening degree according to the outdoor environment humidity comprises:
and if the recent outdoor environment humidity is greater than or equal to the outdoor environment humidity statistic value of the past year, reducing the opening degree of the expansion valve to Sx so as to reduce the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch.
3. The method of claim 2, wherein the step of determining the position of the substrate comprises,
sx is 0.4-0.7 times of the maximum opening value of the expansion valve.
4. A method according to claim 3, further comprising, after decreasing the opening of the expansion valve to Sx:
under the condition that the difference value of the surface temperature of the heat exchanger in unit time is greater than or equal to a temperature threshold value,
When Tr-Tao is less than or equal to DeltaT 1, lim_L=x.times.fmax,
when DeltaT 1 < Tr-Tao < DeltaT 2, lim_L=y.fmax,
when Tr-Tao > - Δt2, lim_l=z×fmax;
or,
under the condition that the difference value of the surface temperature of the heat exchanger in unit time is smaller than a temperature threshold value,
when Tr-Tao is less than or equal to DeltaT 1, lim_L=m.times.fmax,
when DeltaT 1 < Tr-Tao < DeltaT 2, lim_L=n.fmax, or,
when Tr-Tao > - Δt2, lim_l=p x Fmax,
where lim-L is the minimum operating frequency of the compressor, fmax is the maximum operating frequency of the compressor,
0 < x < y < z < 1,0 < m < n < p < 1, and x > m.
5. The method of claim 4, wherein the step of determining the position of the first electrode is performed,
y > n, and/or z > p.
6. An apparatus for adjusting a heat exchange volume of a heat exchanger, wherein when an air conditioner is operating in a heating operating condition and the heat exchanger is an outdoor heat exchanger, the heat exchanger comprises:
a first heat exchange portion including a first upper heat exchange branch;
the second heat exchange part is communicated with the first heat exchange part in parallel and comprises a first lower heat exchange branch and a second lower heat exchange branch which are communicated in parallel;
the first liquid distributor is arranged at the liquid inlet of the heat exchanger and is communicated with the refrigerant inlet end of the second lower heat exchange branch;
The second liquid separator is respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch and the first lower heat exchange branch one by one; and, a step of, in the first embodiment,
a bypass pipeline which is communicated with the first liquid distributor and the second liquid distributor and is provided with an expansion valve,
the device for adjusting the heat exchange volume of a heat exchanger comprises:
the volume adjusting module is configured to adjust the expansion valve to a set opening according to the outdoor environment humidity so as to adjust the heat exchange volumes of the first upper heat exchange branch and the first lower heat exchange branch, and if the recent outdoor environment humidity is smaller than the outdoor environment humidity statistic value of the past year, the expansion valve is adjusted to the maximum opening so that the first upper heat exchange branch and the first lower heat exchange branch operate with the maximum heat exchange volume;
determining a compressor maximum operating frequency Fmax according to the current outdoor environment temperature Tao, determining a compressor minimum operating frequency lim_l according to a difference between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the compressor maximum operating frequency Fmax,
when Tr-Tao is less than or equal to Δt1, lim_l=a×fmax,
when DeltaT 1 < Tr-Tao < DeltaT 2, lim_L=b.fmax,
when Tr-Tao > - Δt2, lim_l=c x Fmax,
Wherein, a is more than 0 and b is more than 0 and c is more than 1.
7. An apparatus for adjusting the heat exchange volume of a heat exchanger comprising a processor and a memory storing program instructions, wherein the processor is configured to perform the method for adjusting the heat exchange volume of a heat exchanger according to any one of claims 1 to 5 when the program instructions are run.
8. An air conditioner comprising the device for adjusting the heat exchange volume of the heat exchanger according to claim 6 or 7.
CN202210190739.8A 2021-09-19 2022-02-28 Method and device for adjusting heat exchange volume of heat exchanger and air conditioner Active CN114838529B (en)

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