CN114838529A

CN114838529A - Method and device for adjusting heat exchange volume of heat exchanger and air conditioner

Info

Publication number: CN114838529A
Application number: CN202210190739.8A
Authority: CN
Inventors: 张心怡; 王飞; 许文明; 李阳
Original assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Current 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
Priority date: 2021-09-19
Filing date: 2022-02-28
Publication date: 2022-08-02
Anticipated expiration: 2042-02-28
Also published as: WO2023040280A1; WO2023040275A1; CN113932489A; CN114838529B; CN113932488A; WO2023040317A1; CN114838532A; WO2023040351A1; WO2023040346A1; CN113932492A; WO2023040294A1; CN114838531B; WO2023040260A1; WO2023040347A1; CN113899118A; WO2023040297A1; WO2023040296A1; CN113932494A; WO2023040293A1; WO2023040295A1

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. The opening degree of an expansion valve arranged on the bypass pipeline is adjusted according to the outdoor environment humidity, and 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 and an air conditioner for adjusting the heat exchange volume of the heat exchanger.

Description

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

The priority of chinese patent application entitled "dispenser, check valve, heat exchanger, refrigeration cycle system, air conditioner," filed in 2021, No. 9/19, application No. 202111102392.9, is hereby incorporated by reference in its entirety.

The priority of the chinese patent application entitled "dispenser, check valve, heat exchanger, refrigeration cycle system, air conditioner," filed on 2021, No. 9/20, application No. 202111102583.5, is incorporated herein by reference in its entirety.

Technical Field

The present application relates to the field of air conditioning technology, 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 an indoor unit and an outdoor heat exchanger arranged in an outdoor unit. A heat exchanger is usually provided with a specific refrigerant flow path form to improve heat exchange capacity of the heat exchanger under a cooling working condition or a heating working condition, and the like.

When the air conditioner is in a refrigerating working condition, the outdoor heat exchanger is used as a condenser, and the number of the refrigerant branches of the outdoor heat exchanger is smaller and better, so that the high-temperature refrigerating capacity of the air conditioner is improved; in the heating condition, the outdoor heat exchanger is used as an evaporator, and the more the number of the refrigerant branches of the outdoor heat exchanger is, the better the refrigerant branches are, so as to improve the low-temperature heating capacity of the air conditioner.

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, the heat exchange volume of the heat exchanger is fixed and unchanged, and the high-efficiency 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 nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides a method and a device for adjusting heat exchange volume of a heat exchanger and an air conditioner.

In some embodiments, when the air conditioner operates in a heating condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises: a first heat exchange section comprising 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 separator is arranged at the liquid inlet of the heat exchanger and communicated with the refrigerant inlet end of the second lower heat exchange branch; the second liquid separators are 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 the bypass pipeline is communicated with the first liquid separator and the second liquid separator and is provided with an expansion valve, and the method for adjusting the heat exchange volume of the heat exchanger 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.

In some embodiments, the adjusting the expansion valve to a set opening degree according to the outdoor ambient humidity includes: and if the recent outdoor environment humidity is less than the outdoor environment humidity statistic value in the past year, adjusting the expansion valve to the maximum opening degree so as to enable the first upper heat exchange branch and the first lower heat exchange branch to operate at the maximum heat exchange volume.

In some embodiments, after adjusting the expansion valve to the maximum opening degree, the method further comprises: and determining the maximum operation frequency Fmax of the compressor according to the current outdoor environment temperature Tao, and determining the minimum operation frequency lim _ L of the compressor according to the difference value between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operation frequency Fmax of the compressor.

In some embodiments, lim _ L is a Fmax when Tr-Tao ≦ Δ T1, lim _ L is b Fmax when Δ T1 < Tr-Tao ≦ Δ T2, and lim _ L is c Fmax when Tr-Tao > - Δ T2, wherein 0 < a < b < c < 1.

In some embodiments, the adjusting the expansion valve to a set opening degree according to the outdoor ambient humidity includes: and if the recent outdoor environment humidity is greater than or equal to the outdoor environment humidity statistical value in the past year, the opening degree of the expansion valve is reduced to Sx so as to reduce the heat exchange volume 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 decreasing the opening degree of the expansion valve to Sx, the method further includes: under the condition that the difference of the surface temperatures of the heat exchangers in unit time is larger than or equal to a temperature threshold value, lim _ L is equal to x and Fmax when Tr-Tao is less than or equal to delta T1, lim _ L is equal to y and Fmax when delta T1 is less than Tr-Tao is less than or equal to delta T2, and lim _ L is equal to z and Fmax when Tr-Tao is greater than delta T2; or, under the condition that the surface temperature difference of the heat exchanger in unit time is smaller than a temperature threshold value, lim _ L is m Fmax when Tr-Tao is less than or equal to delta T1, lim _ L is n Fmax when delta T1 is less than Tr-Tao is less than or equal to delta T2, or lim _ L is p Fmax when Tr-Tao is greater than delta T2, wherein 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.

In some embodiments, y > n, and/or z > p.

In some embodiments, when the air conditioner operates in a heating condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises: a first heat exchange section comprising 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 separator is arranged at the liquid inlet of the heat exchanger and communicated with the refrigerant inlet end of the second lower heat exchange branch; the second liquid separators are 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, communicate first knockout and second knockout, just, the bypass line is provided with the expansion valve, a device for adjusting the heat transfer volume of heat exchanger includes: and 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.

In some embodiments, the means for adjusting the heat exchange volume of the heat exchanger comprises a processor and a memory storing program instructions, the processor being configured to, when executing the program instructions, perform a method for adjusting the heat exchange volume of the heat exchanger as previously described.

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:

the opening degree of an expansion valve arranged on the bypass pipeline is adjusted according to the outdoor environment humidity, and 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 the 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 in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

FIG. 1 is a schematic 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 diagram of a heat exchanger according to an embodiment of the present disclosure;

FIG. 3 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;

FIG. 4 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;

FIG. 5 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

FIG. 6 is a schematic structural view of a first liquid separator according to an embodiment of the present disclosure;

fig. 7 is a schematic structural view of another first liquid separator according to an embodiment of the present disclosure.

Reference numerals:

111: a first upper heat exchange branch; 112: a second upper heat exchange branch; 113: a third upper heat exchange branch; 114: a fourth upper heat exchange branch; 121: a first lower heat exchange branch; 122: a second lower heat exchange branch;

201: a first bypass line; 202: a second bypass line;

301: a first solenoid valve; 302: a second solenoid valve; 401: an expansion valve;

500: a first liquid separator; 511: a converging cavity; 512: a first branch chamber; 513: a second branch chamber; 520: a collector pipe; 521: a first tube section; 522: a second tube section; 530: a first branch liquid-separating pipe; 540: a second branch pipe;

600: a second liquid separator; 700: a third liquid distributor; 800: a fourth liquid distributor;

901: a first sum; 902: and a second sum.

Detailed Description

So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.

The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the present disclosure described herein may be made. Furthermore, the terms "comprising" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their embodiments, and are not used to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.

In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.

The term "plurality" means two or more unless otherwise specified.

In the embodiment of the present disclosure, the character "/" indicates that the preceding and following objects are in an or relationship. For example, A/B represents: a or B.

The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. E.g., a and/or B, represents: a or B, or A and B.

It should be noted that, in the case of no conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

The air conditioner comprises an indoor unit and an outdoor unit, wherein the indoor unit is provided with an indoor heat exchanger, an indoor fan and the like and can be used for realizing the functions of heat exchange and the like between a refrigerant and an indoor environment; the outdoor unit is provided with an outdoor heat exchanger, an outdoor fan, a throttle valve, a compressor, a gas-liquid separator and the like, and can be used for realizing the functions of heat exchange, refrigerant compression, refrigerant throttling and the like by matching with a refrigerant and an outdoor environment.

The indoor heat exchanger, the outdoor heat exchanger, the throttle valve, the compressor, the gas-liquid separator and other components are connected through refrigerant pipelines to form a refrigerant circulating system for circularly conveying the refrigerant between the indoor unit and the outdoor unit; optionally, the refrigerant circulation system is at least limited to two refrigerant flow directions respectively used for a refrigeration mode or a heating mode, specifically, when the air conditioner operates in the refrigeration mode, the refrigerant circulation system conveys the refrigerant in a first refrigerant flow direction, and after being discharged from the compressor, the refrigerant sequentially flows through the outdoor heat exchanger, the throttle valve and the indoor heat exchanger, and then flows back to the compressor through the gas-liquid separator; when the air conditioner operates in a heating mode, the refrigerant circulating system conveys the refrigerant in a second refrigerant flow direction, and the refrigerant flows through the indoor heat exchanger, the throttle valve and the outdoor heat exchanger in sequence after being discharged from the compressor and then flows back to the compressor through the gas-liquid separator.

The following heat exchanger is described by taking the air conditioner as an example of a heating condition and taking the heat exchanger as an outdoor heat exchanger. The description is given here when the heat exchanger is used in a specific operating condition, and the heat exchanger is not limited to be used only as an outdoor heat exchanger.

The disclosed embodiments provide a method 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 separator, a second liquid separator 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 separator is arranged at the liquid inlet of the heat exchanger and 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. The bypass pipeline is communicated with the first liquid separator and the second liquid separator and is provided with an expansion valve.

As shown in fig. 1, a method for adjusting a heat exchange volume of a heat exchanger includes:

and S1, adjusting the expansion valve to a set opening according to the outdoor environment humidity so as to adjust the heat exchange volume of the first upper heat exchange branch and the first lower heat exchange branch.

When the outdoor environment humidity is lower, the current outdoor environment is considered to be not easy to frost, at the moment, the opening degree of the expansion valve can be increased, the number of the heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the number of the heat exchange tubes participating in heat exchange in the first lower heat exchange branch are increased, the heat exchange volume of the heat exchanger is further improved, the heat exchange capacity of the heat exchanger is improved, and the requirement of high-load operation of an air conditioning system is met.

When the outdoor environment humidity is higher, the current outdoor environment is considered to be easy to frost, at the moment, the opening degree of the expansion valve can be reduced, the number of the heat exchange tubes participating in heat exchange in the first upper heat exchange branch and the number of the heat exchange tubes participating in heat exchange in the first lower heat exchange branch are reduced, the effective heat exchange volume of the heat exchanger is further reduced, and the requirement of low-load operation of the air conditioning system is met.

The humidity of the outdoor environment may be relative humidity, and the humidity of both recent outdoor environment and past outdoor environment described below may be relative humidity.

Optionally, adjusting the expansion valve to a set opening degree according to the outdoor environment humidity comprises: if the recent outdoor environment humidity is smaller than the outdoor environment humidity statistical value of the past year, the expansion valve is adjusted to the maximum opening degree, so that the first upper heat exchange branch and the first lower heat exchange branch operate in the maximum heat exchange volume.

The moisture content in the air is related to the relative humidity and temperature, wherein recent outdoor ambient temperatures are generally comparable to the outdoor ambient temperatures of the past year. Optionally, if the recent statistical value of the outdoor environment humidity is smaller than the historical statistical value of the outdoor environment humidity, the moisture content in the recent air is considered to be smaller, and at this time, while the historical defrosting frequency is used, the expansion valve can be adjusted to the maximum opening degree, 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 is operated with the maximum heat exchange volume, and the heat exchange capacity of the heat exchanger is improved.

Alternatively, the maximum opening degree of the electromagnetic valve is 480 steps. Alternatively, the annual defrost frequency, as well as the defrost frequency that occurs as described below, may be defrost every 1-3 hours.

Alternatively, the recent outdoor environment humidity statistics may be recent daily average humidity statistics, recent monthly average humidity statistics, recent quarterly average humidity statistics, or the like. The outdoor environment humidity statistic of the previous year can be the average humidity statistic of the previous year and this day, the average humidity statistic of the previous year and the month, the average humidity statistic of the previous year and the quarter, and the like. The calendar year may be approximately 3-5 years. The average humidity statistics of the recent day may be compared with the average humidity statistics of the current year and the current year, the average humidity statistics of the recent month may be compared with the average humidity statistics of the month of the recent year, or the average humidity statistics of the recent quarter may be compared with the average humidity statistics of the quarter of the recent year. For example, if the average outdoor ambient humidity is 35% today and the average outdoor ambient humidity is 40% 3 years ago today, the expansion valve may be adjusted to the maximum opening degree.

Optionally, after adjusting the expansion valve to the maximum opening degree, the method further includes: and determining the maximum operation frequency Fmax of the compressor according to the current outdoor environment temperature Tao, and determining the minimum operation frequency lim _ L of the compressor according to the difference value between the current indoor environment temperature Tr and the current outdoor environment temperature Tao and the maximum operation frequency Fmax of the compressor.

After the expansion valve is adjusted to the maximum opening degree, the maximum operation frequency Fmax and the minimum operation frequency lim _ L of the compressor under the maximum opening degree of the current expansion valve are further adjusted, so that the compressor can operate between the maximum operation frequency Fmax and the minimum operation frequency lim _ L, and the operation capacity of the whole air-conditioning system is further adjusted. Under the condition of defrosting frequency along with the use of the whole year, if the humidity of the outdoor environment is relatively low recently, the opening degree of the expansion valve can be adjusted to the maximum opening degree, and meanwhile, the minimum operation frequency of the compressor is increased, so that the operation capacity of the whole air conditioning system is improved, and the requirement of a user on indoor temperature adjustment is further met.

Alternatively, lim _ L is a Fmax when Tr-Tao ≦ Δ T1, lim _ L is b Fmax when Δ T1 < Tr-Tao ≦ Δ T2, and lim _ L is c Fmax when Tr-Tao > - Δ T2, wherein 0 < a < b < c < 1.

Alternatively, Δ T1 may be 3 ℃,. Δ T2 may be 10 ℃, a ═ 0.3, b ═ 0.5, and c ═ 0.6. Under the condition of the defrosting frequency of the past year, the minimum operation 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 operation frequency Fmax of the compressor, and the energy efficiency of the whole air conditioning system is further adjusted.

Optionally, adjusting the expansion valve to a set opening degree according to the outdoor environment humidity comprises: if the recent outdoor environment humidity is larger than or equal to the outdoor environment humidity statistical value in the past year, the opening degree of the expansion valve is reduced to Sx so as to reduce the heat exchange volume of the first upper heat exchange branch and the first lower heat exchange branch.

If the recent outdoor environment humidity statistic value is larger than or equal to the historical outdoor environment humidity statistic value, the moisture content in the recent air is considered to be larger, at the moment, the opening degree of the expansion valve can be reduced to Sx while the historical defrosting frequency is used, and 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 both include 6 heat exchange tubes, and after the opening degree of the expansion valve is adjusted to Sx, 4 heat exchange tubes are involved in heat exchange in the first upper heat exchange branch and the first lower heat exchange branch. Therefore, the air conditioner can normally operate under the condition that frequent defrosting is not needed and the air conditioner still keeps the defrosting frequency of the whole year.

Alternatively, 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, Sx is 200 steps and 300 steps.

Optionally, after the opening degree of the expansion valve is decreased to Sx, the method for adjusting the heat exchange volume of the heat exchanger further includes:

under the condition that the surface temperature difference of the heat exchanger in unit time is greater than or equal to the temperature threshold value,

when Tr-Tao is less than or equal to Delta T1, lim _ L is x Fmax,

when the delta T1 is less than Tr-Tao and less than delta T2, lim _ L is y and Fmax,

when Tr-Tao >. Δ T2, lim _ L ═ z × Fmax.

Alternatively, Δ T1 may be 3 ℃,. Δ T2 may be 10 ℃, x ═ 0.3, y ═ 0.5, and z ═ 0.6. And further adjusting the minimum operating frequency lim _ L of the compressor 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 under the condition of continuously using the defrosting frequency of the years, thereby adjusting the energy efficiency of the whole air-conditioning system.

when Tr-Tao is less than or equal to Delta T1, lim _ L is m × Fmax,

when DeltaT 1 < Tr-Tao ≦ DeltaT 2, lim _ L ═ n × Fmax, or,

when Tr-Tao >. Δ T2, lim _ L ═ p × Fmax.

And lim _ L is the minimum operating frequency of the compressor, and Fmax is the maximum operating frequency of the compressor.

X is more than 0 and less than y and less than z and less than 1, m is more than 0 and less than n and less than p and less than 1, and x is more than m.

Alternatively, Δ T1 may be 3 ℃,. Δ T2 may be 10 ℃, m ═ 0.2, n ═ 0.3, and p ═ 0.4. And under the condition of the defrosting frequency of the past year, further reducing the minimum operating frequency lim _ L of the compressor 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 further adjusting the energy efficiency of the whole air conditioning system.

The disclosed embodiment simultaneously provides a device for adjusting heat transfer volume of heat exchanger, includes:

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 will be appreciated that the embodiments of the method for adjusting the heat exchange volume of a heat exchanger described above are applicable to the apparatus herein and will not be described in detail herein.

The disclosed embodiments also provide an apparatus for adjusting a heat exchange volume of a heat exchanger, including a processor and a memory storing program instructions, where the processor is configured to execute the method for adjusting the heat exchange volume of the heat exchanger as described above when executing the program instructions.

The embodiment of the disclosure also provides an air conditioner, which comprises the device for adjusting the heat exchange volume of the heat exchanger.

The disclosed embodiments also provide a heat exchanger, which can be used in the aforementioned method, device and air conditioner for adjusting the heat exchange volume of the heat exchanger, as shown in fig. 2-7.

It can be understood that the aforementioned method, device and bypass line in the air conditioner for adjusting the heat exchange volume of the 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 exchanging part comprises N upper heat exchanging branches. The second heat exchange part is arranged at the lower part of the first heat exchange part and comprises M lower heat exchange branches communicated in parallel. The first bypass line 201 communicates the refrigerant outlet end of the first heat exchange portion with the refrigerant outlet end of the second heat exchange portion. The first bypass line 201 is provided with a first solenoid valve 301. Wherein N is more than or equal to M-1, and M is more than or equal to 2.

The upper end and the lower end of the first bypass pipeline 201 are used for dividing the heat exchange branch of the heat exchanger into a first heat exchange part and a second heat exchange part. When the heat exchanger is in a vertical installation and use state, the first heat exchange part is positioned at the upper part of the second heat exchange part. N can be an integer number of 1, 2, 3, 4, 5, 6, 7, and the like. When the number of the upper heat exchange branches is multiple, similarly, the multiple upper heat exchange branches are communicated in parallel. M can be an integer number of 2, 3, 4, 5, 6, 7, etc. The upper heat exchange branches are communicated with the lower heat exchange branches in parallel.

As shown in fig. 2 to 5, a plurality of upper heat exchange branches of the first heat exchange portion adopt a fourth liquid separator 800 to converge, a plurality of lower heat exchange branches of the second heat exchange portion adopt a third liquid separator confluence 700, and the first bypass line 201 connects the third liquid separator 700 and the fourth liquid separator 800.

According to the heat exchanger provided by the embodiment of the disclosure, when the air conditioner operates in a heating working condition, all heat exchange branches of the heat exchanger are communicated in parallel, so that the heating performance of the air conditioner is met, and the low-temperature heating capacity of the air conditioner is improved.

Optionally, the first heat exchanging part comprises a first upper heat exchanging branch 111 and a second upper heat exchanging branch 112, and the second heat exchanging part comprises a first lower heat exchanging branch 121 and a second lower heat exchanging branch 122. The heat exchanger further comprises a first liquid separator 500, a second liquid separator 600, and a second bypass line 202. The first liquid separator 500 is disposed at the liquid inlet of the heat exchanger, and a branch liquid pipe of the first liquid separator 500 is communicated with the refrigerant inlet end of the second lower heat exchange branch 122. The plurality of branch liquid pipes of the second liquid separator are respectively communicated with the refrigerant inlet ends of the first upper heat exchange branch 111, the second upper heat exchange branch 112 and the first lower heat exchange branch 121 one by one. The second bypass line 202 communicates the first and

second dividers

500 and 202. The second bypass line 202 is provided with a second solenoid valve 302 and an expansion valve 401.

By controlling the open and close states of the first electromagnetic valve 301 and the second electromagnetic valve 302, each heat exchange branch of the heat exchanger can be in different refrigerant flow path forms under the working conditions of refrigeration and heating, and the performance requirements of the heat exchanger under different working modes can be simultaneously ensured.

Taking 3 heat exchange branches shown in fig. 2 and 3 as an example, when the air conditioner operates in a refrigeration condition, the first electromagnetic valve 301 and the second electromagnetic valve 302 are controlled to be closed. The refrigerant flows in through the first header 901, sequentially flows through the first upper heat exchange branch 111, the first lower heat exchange branch 121 and the second lower heat exchange branch 122, and flows out through the second header 902, and the number of the heat exchange branches of the refrigerant flow path of the heat exchanger is small.

When the number of the heat exchange branches of the heat exchanger is 4, as shown in fig. 4, under the refrigeration condition, the first upper heat exchange branch 111 is in parallel communication with the second upper heat exchange branch 112; when the number of the heat exchange branches of the heat exchanger is 6, as shown in fig. 5, under the cooling condition, the first upper heat exchange branch 111, the second upper heat exchange branch 112, the third upper heat exchange branch 113, and the fourth upper heat exchange branch 114 are in parallel communication.

Taking 3 heat exchange branches shown in fig. 2 and 3 as an example, when the air conditioner operates in a heating condition, the first electromagnetic valve 301 and the second electromagnetic valve 302 are controlled to be opened. The refrigerant flows in through the second header 902, the first upper heat exchange branch 111, the first lower heat exchange branch 121, and the second lower heat exchange branch 122 are connected in parallel and communicated, and flow out from the first header 901, and the number of heat exchange branches of the refrigerant flow path of the heat exchanger is large.

Alternatively, the expansion valve 401 is provided at an upper portion of the second solenoid valve 302.

When the air conditioner operates in a refrigeration working condition, the pressure of the refrigerant in the second liquid separator 600 is higher than that of the refrigerant in the first liquid separator 500, and the second electromagnetic valve 302 has the risks of impact on the valve core and poor sealing. The expansion valve 401 is disposed on the upper portion of the second solenoid valve 302, and the expansion valve 401 can be controlled to close, so that the pressure difference between the two ends of the second solenoid valve 302 can be reduced, and the reliability of closing the second solenoid valve 302 can be ensured. Also, the expansion valve 401 may adjust the opening degree. Taking the 3 heat exchange branches shown in fig. 2 and fig. 3 as an example, when the air conditioner operates in a heating working condition, the circulation amount of the refrigerant is further adjusted by the expansion valve 401 after passing through the throttling device of the air conditioner system, so that the number of heat exchange tubes participating in refrigerant circulation in the first upper heat exchange branch 111, the second upper heat exchange branch 112 and the first lower heat exchange branch 121 is adjusted, the heat exchange volume of the heat exchanger is adjusted, and the energy efficiency of the air conditioner during different load operations is improved.

Optionally, the first upper heat exchange branch 111, the second upper heat exchange branch 112, the first lower heat exchange branch 121 and the second lower heat exchange branch 122 are sequentially arranged from top to bottom.

Optionally, the first liquid separator 500 includes a housing, a manifold 520, a first branch liquid separator 530, and a second branch liquid separator 540. The shell is internally provided with a liquid separation cavity, and the shell is provided with a first liquid separation port and a second liquid separation port. The manifold 520 comprises a first pipe section 521 and a second pipe section 522 which are communicated in a bending mode, and the first pipe section 521 is directly communicated with the liquid dividing cavity. The first branch liquid-separating pipe 530 is communicated with the liquid-separating chamber through the first liquid-separating port, and the first branch liquid-separating pipe 530 is communicated with the second bypass line 202. The second branch liquid distribution pipe 540 is communicated with the liquid distribution cavity through a second liquid distribution port, and the second branch liquid distribution pipe 540 is communicated with the third heat exchange part. The axes of first pipe section 521 and second pipe section 522 lie in a first plane and the axes of first branch 530 and second branch 540 lie in a second plane, the first plane being non-perpendicular to the second plane. As shown in fig. 6 and 7.

Optionally, an included angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees; or the included angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees. Alternatively, the inner diameter of first branch liquid-dividing line 530 is greater than or equal to 5.1mm and less than or equal to 6.1 mm. The second branch liquid take-off 540 has an inner diameter of 3.1mm or more and 3.7mm or less.

Optionally, the liquid separating chamber includes a confluence chamber 511, a first branch chamber 512 and a second branch chamber 513, the first branch liquid separating pipe 530 is communicated with the first branch chamber 512 through a first liquid separating port, and the second branch liquid separating pipe 540 is communicated with the second branch chamber 513 through a second liquid separating port.

The manifold 520 comprises a first pipe segment 521 and a second pipe segment 522, the plane of the axes of the first pipe segment 521 and the second pipe segment 522 is a first plane, and the included angle between the first plane and the second plane is e. As shown in fig. 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 the acute angle formed by the two. The first plane is not perpendicular to the second plane, so that the amount of refrigerant entering the first branch liquid-separating pipe 530 and the second branch liquid-separating pipe 540 through the first pipe section 521 is different. For example, when the included angle between the first plane and the second plane is on the side of the first branch liquid-dividing pipe 530, the flow rate of the refrigerant flowing to the second branch liquid-dividing pipe 540 is greater than the flow rate flowing to the first branch liquid-dividing pipe 530 under the action of gravity. Similarly, when the angle between the first plane and the second plane is on the side of the second branch liquid dividing pipe 540, the flow rate of the refrigerant flowing to the first branch liquid dividing pipe 530 is greater than the flow rate of the refrigerant flowing to the second branch liquid dividing pipe 540 under the action of gravity.

Taking the heat exchanger shown in fig. 4 as an example, in a heating condition, when the heat exchanger is used as an evaporator, the refrigerant is divided by the first liquid separator 500 and then flows into four heat exchange branches connected in parallel, that is, the first upper heat exchange branch 111, the second upper heat exchange branch 112, the first lower heat exchange branch 121, and the second lower heat exchange branch 122. The refrigerant flows through the liquid separating branch pipe on the left side of the first liquid separator 500 and then flows into only the second lower heat exchange branch 122, and the refrigerant flows through the liquid separating branch pipe on the right side of the first liquid separator 500 and then flows into three heat exchange branches, namely a first upper heat exchange branch 111, a second upper heat exchange branch 112 and a first lower heat exchange branch 121. It can be seen that after the refrigerant passes through the first liquid separator 500, the refrigerant amount required by the two liquid separating branch pipes of the first liquid separator 500 is different. The refrigerant quantity required by the right branch liquid separating pipe is 3 times of that of the left branch liquid separating pipe. The knockout that this disclosure provided utilizes the coolant at the action of gravity of flow in-process, through the setting of the contained angle between the first plane at the axis place of first pipeline section 521 and second pipeline section 522 of collecting pipe 520 and the second plane at the axis place of first branch liquid pipe 530 and second branch liquid pipe 540, has realized that the refrigerant volume that different branch liquid pipes of knockout flow is different, has satisfied the demand that the required refrigerant volume of branch liquid pipe is different, and then has improved the heat exchange efficiency of heat exchanger.

Optionally, an angle between the first plane and the second plane is less than 90 degrees. Optionally, the included angle between the first plane and the second plane is 0 degree, 30 degrees, 60 degrees, 70 degrees, 80 degrees, or the like. The included angle between the first plane and the second plane is smaller than 90 degrees, so that the refrigerant can bias under the action of gravity after flowing through the first pipe section 521 of the collecting pipe 520, and further the cold energy flowing into the first liquid-dividing branch pipe 530 and the second liquid-dividing branch pipe 540 is different.

Optionally, the inner diameter of first branch splitter 530 is greater than the inner diameter of second branch splitter 540. According to the liquid distributor provided by the embodiment of the disclosure, an included angle is formed between a first plane where the axes of the first pipe section 521 and the second pipe section 522 of the collecting pipe 520 are located and a second plane where the axes of the two liquid distributing branch pipes are located, and the difference of the refrigerant amount flowing into the two liquid distributing branch pipes is further increased by further matching with the inner diameter difference between the two liquid distributing branch pipes.

Optionally, the first pipe segment 521 of the collecting pipe 520 is inclined toward the second branch liquid-separating pipe 540, and further, under the action of gravity, the inner diameter of the first branch liquid-separating pipe 530 is larger than the inner diameter of the second branch liquid-separating pipe 540, so that more refrigerant flows into the first branch liquid-separating pipe 530, and the refrigerant flow rate difference between the two branch liquid-separating pipes is further increased.

Refrigerant distribution with a refrigerant flow difference of 3:1 or more in the flow ratio of the first branch liquid dividing pipe 530 to the second branch liquid dividing pipe 540 is difficult to achieve only by limiting the difference in the inner diameters of the first branch liquid dividing pipe 530 and the second branch liquid dividing pipe 540. The reason is that the inner diameter of the branch liquid-separating pipe is limited to the minimum value, for example, the inner diameter of the branch liquid-separating pipe cannot be less than 3mm, even not less than 3.36mm, the copper pipe below the inner diameter actually becomes a capillary pipe, the capillary pipe has larger flow resistance, and forms a throttling and pressure reducing effect on the flow of the refrigerant, so that the power of the compressor can be increased, and the performance of the system can be reduced; even when the air conditioner operates in a heating working condition, the outdoor heat exchanger is frosted seriously, and the safety and reliability of the system are affected. Due to the limitation of the minimum value of the inner diameters of the branch liquid-separating pipes, in order to realize refrigerant distribution with a flow ratio of 3:1, the pipe diameter of the other branch liquid-separating pipe needs to be larger than 7mm, and optionally, the 7mm can be an outer diameter which is 1.4mm larger than the inner diameter, however, the pipe diameter obviously exceeds the inner diameter of a heat exchange pipe which is actually used in the heat exchanger, and the general pipe diameter of the heat exchanger is 7mm, such as a pipe fin type heat exchanger. Therefore, it is difficult to achieve refrigerant distribution with a refrigerant distribution ratio of 3:1 or even a larger refrigerant flow difference between the first branch liquid-dividing pipe 530 and the second branch liquid-dividing pipe 540 within a range not exceeding the allowable pipe diameter of the heat exchange pipe in the heat exchanger, merely by limiting the difference in the inner diameters of the first branch liquid-dividing pipe 530 and the second branch liquid-dividing pipe 540.

According to the technical scheme that the included angle is formed between the first plane where the axes of the first pipe section 521 and the second pipe section 522 of the collecting pipe 520 are located and the second plane where the axes of the two branch liquid pipes are located, and the inner diameter difference between the two branch liquid pipes is further matched, the refrigerant distribution requirements of the two branch liquid pipes with the refrigerant flow ratio of 2:1-7:1 and even a larger proportion, such as 2:1, 3:1, 4:1, 5:1, 6:1 and 7:1, can be realized within the range allowed by the pipe diameter of a heat exchange pipe of the heat exchanger. According to the refrigerant distribution scheme for realizing the large flow ratio provided by the embodiment of the disclosure, the inner diameter of the second branch liquid-separating pipe 540 does not need to be designed to be too small, and the flow rate of the refrigerant in the first branch liquid-separating pipe 530 is much larger than that of the refrigerant in the second branch liquid-separating pipe 540. Therefore, the refrigerant distribution scheme of the liquid separator provided by the embodiment of the disclosure avoids the problem of overlarge total pressure drop of the liquid separating branch pipes and the heat exchanger of the liquid separator when the refrigerant distribution ratio of the two liquid separating branch pipes is large.

Optionally, an included angle between a first plane where the axes of the first pipe section 521 and the second pipe section 522 of the collecting pipe 520 are located and a second plane where the axes of the two branch liquid pipes are located is greater than or equal to 50 degrees and less than or equal to 70 degrees. The difference in the flow rates of the refrigerant in the first branch 530 and the second branch 540 is increased.

Alternatively, the inner diameter of first branch liquid-dividing line 530 is greater than or equal to 5.1mm and less than or equal to 6.1 mm; the second branch liquid take-off 540 has an inner diameter of 3.1mm or more and 3.7mm or less.

Optionally, the second pipe section 522 of the collecting pipe 520 is inclined toward the second branch liquid pipe 540 side.

When the air conditioner operates in a heating working condition and the heat exchanger is used as an evaporator, the heat exchanger can exert the optimal heat exchange capacity under the following conditions: when heating, constantly absorb the heat in the surrounding environment air from low temperature liquid state, reached gas-liquid two-phase state along with the temperature rise, the temperature keeps unchanged at evaporating temperature this time, only constantly takes place the liquid phase change to gaseous state, and liquid refrigerant is less and less, and gaseous refrigerant is more and more, just all becomes gaseous state and the temperature is higher than evaporating temperature 1 ~ 2 ℃ when the export of whole heat transfer branch road. The reason is that when the outlet temperature of the heat exchange branch is overheated, all the gas-state refrigerants are gaseous refrigerants, the enthalpy difference of the gaseous refrigerants is small, the heat exchange capacity is low, and when the superheat degree is overlarge, the heat exchange temperature difference between the refrigerants and the ambient temperature is small, for example, when the evaporation temperature is about 0-1 ℃, if the superheat degree is greater than 3 ℃, the temperature is above 4 ℃, and the ambient temperature in winter is about 7 ℃, the heat exchange temperature difference is small, and the heat exchange capacity of the heat exchanger is more difficult to be exerted.

The better the uniformity is, the easier each heat exchange branch has a proper heat exchange, if not uniform, some branches are too hot, the back hairpin tubes have no heat exchange effect, some heat exchange branch refrigerants are too many, and the whole heat exchange branch still has a lot of low-temperature liquid refrigerants to exchange cold energy, so, under the same refrigerant flow, the heat exchange effect of the whole heat exchanger is poor, and the capacity of the air conditioner is very low. Therefore, the method for judging good shunting of experience in heating comprises the following steps: the temperature difference of the outlets of the branches is within 2 ℃, the superheat degree of the outlets is about 1 ℃, and the shunting is better under the condition.

TABLE 2

TABLE 3

Alternatively, when the air conditioner is operated in a heating mode, the heat exchanger is used as an evaporator, and the first upper heat exchange branch 111, the second upper heat exchange branch 112, and the first lower heat exchange branch 121 connected in parallel are communicated with the first liquid-dividing branch pipe 530, and the second lower heat exchange branch 122 is communicated with the second liquid-dividing branch pipe 540, as shown in fig. 4, the refrigerant temperature at the outlet of each heat exchange branch is as shown in tables 2 and 3. Table 2 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 under different inner diameters of the first liquid-dividing branch 530 and the second liquid-dividing branch 540 when the included angle between the first plane and the second plane is 90 degrees. As can be seen from the data in table 2, when the inner diameter of the first branch liquid-dividing pipe 530 is 5.6mm, and the inner diameter of the second branch liquid-dividing pipe 540 is 3.36mm, the maximum temperature difference between the second lower heat exchange branch 122 and the first three branches of the heat exchanger is 3.4 ℃ which is the smallest, and the heating capacity of the air conditioner is 4855.2W which is the largest at the inner diameter. Table 3 shows that when the inner diameter of the first branch liquid-dividing pipe 530 is 5.6mm, and the inner diameter of the second branch liquid-dividing pipe 540 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the second lower heat exchange branch 122 and the first three branches and the heating capacity of the air conditioner are different. As can be seen from table 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 minimum and is 1.2 ℃, and the heating capacity of the air conditioner is maximum and is 5016.1W at this angle.

As can be seen from the data in tables 2 and 3, when the number of the heat exchange branches in the heat exchanger, which are communicated with the first branch liquid pipe 530, is 3, and the number of the heat exchange branches in the heat exchanger, which are communicated with the second branch liquid pipe 540, is 1, for example, as shown in the heat exchanger shown in fig. 4, the inner diameter of the first branch liquid pipe 530 is 5.6mm, the inner diameter of the second branch liquid pipe 540 is 3.36mm, and the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth branch heat exchange branch 330 and the first three branches is the smallest, the uniformity of the heat exchange capacity of the refrigerant in each branch heat exchange branch is the best, and the heating capacity of the air conditioner is the largest. That is, a ratio of the amount of refrigerant in the first branch liquid-dividing pipe 530 to the amount of refrigerant in the second branch liquid-dividing pipe 540 of 3:1 is achieved.

Similarly, when the included angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees, the inner diameter of the first branch liquid dividing pipe 530 is greater than or equal to 5.1mm and less than or equal to 6.1mm, and the inner diameter of the second branch liquid dividing pipe 540 is greater than or equal to 3.1mm and less than or equal to 3.7mm, the ratio of the refrigerant quantity in the first branch liquid dividing pipe 530 to the refrigerant quantity in the second branch liquid dividing pipe 540 can be preferably realized to be 3: 1. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in the embodiment are similar to the data in tables 2 and 3, and are not repeated here.

The flowchart 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 disclosed in the description, and sometimes there is no specific order between the different operations or steps. For example, two sequential operations or steps may in fact be executed substantially concurrently, or they may sometimes be executed in the reverse order, depending upon the functionality involved. Each block of the block diagrams and/or flowchart illustrations, and combinations of blocks in the block diagrams and/or flowchart illustrations, can be implemented by special purpose hardware-based systems that perform the specified functions or acts, or combinations of special purpose hardware and computer instructions.

Claims

1. A method for adjusting a heat exchange volume of a heat exchanger, wherein when an air conditioner is operated in a heating condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises:

a first heat exchange section comprising 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 separator is arranged at the liquid inlet of the heat exchanger and communicated with the refrigerant inlet end of the second lower heat exchange branch;

the second liquid separators are 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 the combination of (a) and (b),

a bypass pipeline which is communicated with the first liquid separator and the second liquid separator and is provided with an expansion valve,

the method for adjusting the heat exchange volume of the heat exchanger 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.

2. The method of claim 1, wherein adjusting the expansion valve to a set opening based on outdoor ambient humidity comprises:

and if the recent outdoor environment humidity is less than the outdoor environment humidity statistic value in the past year, adjusting the expansion valve to the maximum opening degree so as to enable the first upper heat exchange branch and the first lower heat exchange branch to operate at the maximum heat exchange volume.

3. The method of claim 2, further comprising, after adjusting the expansion valve to a maximum opening degree:

determining the maximum operation frequency Fmax of the compressor according to the current outdoor environment temperature Tao,

and determining the minimum operating frequency lim _ L of the compressor 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.

4. The method of claim 3,

when Tr-Tao is less than or equal to Delta T1, lim _ L is a multiplied by Fmax,

when the delta T1 is more than Tr-Tao and less than delta T2, lim _ L is b and Fmax,

when Tr-Tao >. DELTA.T 2, lim _ L ═ c × Fmax,

wherein a is more than 0 and less than b and less than c and less than 1.

5. The method of claim 1, wherein adjusting the expansion valve to a set opening based on outdoor ambient humidity comprises:

and if the recent outdoor environment humidity is greater than or equal to the outdoor environment humidity statistical value in the past year, the opening degree of the expansion valve is reduced to Sx so as to reduce the heat exchange volume of the first upper heat exchange branch and the first lower heat exchange branch.

6. The method of claim 5,

sx is 0.4-0.7 times of the maximum opening value of the expansion valve.

7. The method of claim 6, further comprising, after reducing the opening degree of the expansion valve to Sx:

when Tr-Tao is less than or equal to Delta T1, lim _ L is x Fmax,

when Tr-Tao >. Δ T2, lim _ L ═ z × Fmax;

alternatively, the first and second electrodes may be,

under the condition that the surface temperature difference of the heat exchanger in unit time is less than the temperature threshold value,

when Tr-Tao is less than or equal to Delta T1, lim _ L is m × Fmax,

when DeltaT 1 < Tr-Tao ≦ DeltaT 2, lim _ L ═ n × Fmax, or,

when Tr-Tao >. DELTA.T 2, lim _ L ═ p × Fmax,

wherein lim _ L is the minimum operating frequency of the compressor, Fmax is the maximum operating frequency of the compressor,

8. The method of claim 7,

y > n, and/or, z > p.

9. A device for adjusting heat exchange volume of a heat exchanger is characterized in that when an air conditioner operates in a heating working condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises:

a first heat exchange section comprising a first upper heat exchange branch;

the device for adjusting the heat exchange volume of the heat exchanger comprises:

and 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.

10. An apparatus for adjusting the heat exchange volume of a heat exchanger comprising a processor and a memory having stored thereon program instructions, wherein the processor is configured to perform the method for adjusting the heat exchange volume of a heat exchanger of any one of claims 1 to 8 when executing the program instructions.

11. An air conditioner characterized by comprising the device for adjusting the heat exchange volume of a heat exchanger according to claim 9 or 10.