CN218296023U - Heat exchanger and air conditioner - Google Patents

Abstract

The utility model relates to an air conditioner technical field discloses a heat exchanger, at the air conditioner operation refrigeration operating mode, just when the heat exchanger is as outdoor heat exchanger, the heat exchanger is including first heat transfer part, second heat transfer part and the third heat transfer part that concatenates the intercommunication in proper order, second heat transfer part include with the first end that first heat transfer part is linked together and with the second end that third heat transfer part is linked together, the heat exchanger still includes: the first bypass pipeline is communicated with the second end of the second heat exchange part and the liquid inlet end of the first heat exchange part; and the second bypass pipeline is communicated with the first end of the second heat exchange part and the liquid outlet end of the third heat exchange part, wherein the first bypass pipeline is provided with a first electromagnetic valve, and the second bypass pipeline is provided with a second electromagnetic valve. Adopt the heat exchanger of this application, through the switching of controlling first solenoid valve and second solenoid valve, improve the defrosting homogeneity of heat exchanger effectively. The application also discloses an air conditioner.

Description

Heat exchanger and air conditioner

Technical Field

The application relates to the technical field of air conditioners, for example to a heat exchanger and an air conditioner.

Background

With the continuous improvement of the living standard of people, the air conditioner gradually becomes one of the indispensable household appliances in life. Most of the existing air-conditioning product models are of split structures and comprise indoor units arranged indoors and outdoor units arranged outdoors. When the heat exchanger of the air conditioner outdoor unit is respectively used as a condenser and an evaporator, different performance requirements exist, and in order to realize 'less-branch-condensation evaporation multi-branch', a variable flow dividing technology is provided.

In the existing air conditioner adopting the variable flow dividing technology, the outdoor heat exchanger usually adopts a one-way valve to realize variable flow dividing, and refrigerant flow paths are connected in series during refrigeration to prolong the length of the flow path, so that the aim of fully exchanging heat is fulfilled, and the refrigeration effect is improved; during heating, the refrigerant flow paths are connected in parallel to shorten the length of the flow path, so that pressure loss is avoided, and the heating effect 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:

when the outdoor unit is defrosting, the refrigerant flowing way is the same as the refrigerant flowing way during refrigeration, and the temperature of the refrigerant flowing through the bottom pipe section of the heat exchanger is lower than that of the top pipe section, so that the defrosting effect of the bottom pipe section of the heat exchanger is poor, and the defrosting is uneven.

SUMMERY OF THE UTILITY MODEL

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides a heat exchanger and an air conditioner, which improve the defrosting uniformity of the heat exchanger.

In some embodiments, when the air conditioner operates in a cooling condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises: the heat exchanger comprises a first heat exchange part, a second heat exchange part and a third heat exchange part which are sequentially communicated in series, wherein the second heat exchange part comprises a first end communicated with the first heat exchange part and a second end communicated with the third heat exchange part, and the heat exchanger further comprises: the first bypass pipeline is communicated with the second end of the second heat exchange part and the liquid inlet end of the first heat exchange part; and the second bypass pipeline is communicated with the first end of the second heat exchange part and the liquid outlet end of the third heat exchange part, wherein the first bypass pipeline is provided with a first electromagnetic valve, and the second bypass pipeline is provided with a second electromagnetic valve.

In some embodiments, when a compressor of an air conditioner operates in a low frequency state, the first solenoid valve is controlled to be closed, and the second solenoid valve is controlled to be opened, so that the refrigerant in the heat exchanger flows through only the first heat exchange portion.

In some embodiments, when the air conditioner operates in the defrosting mode, the first solenoid valve and the second solenoid valve are controlled to be conducted, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are communicated in parallel.

In some embodiments, further comprising: the first liquid separator is arranged at a port of the second bypass pipeline, which is connected with the first end of the second heat exchange part; and the second liquid separator is arranged at a port of the second bypass pipeline connected with the liquid outlet end of the third heat exchange part.

In some embodiments, the second liquid separator comprises: the liquid separation device comprises a shell, a liquid separation device and a liquid separation device, wherein a liquid separation cavity is formed in the shell, and a first liquid separation port and a second liquid separation port are formed in the shell; the collecting pipe comprises a first pipe section and a second pipe section which are connected in a bent mode, and the first pipe section is directly connected with the liquid separating cavity; the first liquid dividing branch pipe is communicated with the liquid dividing cavity through the first liquid dividing port and communicated with the second bypass pipeline; and the second branch liquid distribution pipe is communicated with the liquid distribution cavity through the second liquid distribution port and communicated with the third heat exchange part, wherein the plane where the axes of the first pipe section and the second pipe section are located is a first plane, the plane where the axes of the first branch liquid distribution pipe and the second branch liquid distribution pipe are located is a second plane, and the first plane and the second plane are not vertical.

In some embodiments, the first plane and the second plane form an angle greater than or equal to 50 degrees and less than or equal to 70 degrees; or the included angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees.

In some embodiments, the first branch knock-out tube has an inner diameter greater than or equal to 5.1mm and less than or equal to 6.1mm; the inner diameter of the second branch liquid-dividing pipe is more than or equal to 3.1mm and less than or equal to 3.7mm.

In some embodiments, the first heat exchange portion is disposed at an upper portion of the second heat exchange portion, and the second heat exchange portion is disposed at an upper portion of the third heat exchange portion.

In some embodiments, the first heat exchange portion comprises a first heat exchange branch and a second heat exchange branch which are communicated in parallel; the second heat exchange part comprises a third heat exchange branch; and, the third heat exchanging part includes a fourth heat exchanging branch.

In some embodiments, the air conditioner comprises a heat exchanger as described above.

The heat exchanger and the air conditioner provided by the embodiment of the disclosure can realize the following technical effects:

the heat exchanger provided by the embodiment of the disclosure comprises a first heat exchange part, a second heat exchange part and a third heat exchange part which are sequentially connected in series, wherein a first solenoid valve is arranged on a first bypass pipeline, and a second solenoid valve is arranged on a second bypass pipeline. Therefore, when refrigeration is carried out, the first electromagnetic valve and the second electromagnetic valve are in a closed state, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are sequentially connected in series, the length of a flow path of a high-temperature refrigerant in the heat exchanger is prolonged, and the refrigerant can be fully subjected to heat exchange to realize supercooling; when heating is carried out, the first electromagnetic valve and the second electromagnetic valve are in a conducting state, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are connected in parallel, and the problem of pressure loss caused by too long flow paths is solved; when defrosting is carried out, the first electromagnetic valve and the second electromagnetic valve are in a conducting state, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are connected in parallel, the temperature of pipelines of the heat exchange parts is kept at a high temperature, and the defrosting uniformity of the heat exchanger can be effectively improved.

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 in the accompanying drawings, which correspond to the accompanying drawings and not in a limiting sense, in which elements having the same reference numeral designations represent like elements, and in which:

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

FIG. 2 is a schematic structural diagram of another heat exchanger provided by the disclosed embodiment;

fig. 3 is a schematic diagram of a refrigerant flow path of the heat exchanger provided by the embodiment of the disclosure as an outdoor heat exchanger in a cooling operation;

fig. 4 is a schematic diagram of a refrigerant flow path of the heat exchanger provided by the embodiment of the disclosure as an outdoor heat exchanger in heating operation;

fig. 5 is a schematic diagram of a refrigerant flow path of the heat exchanger provided by the embodiment of the disclosure as an outdoor heat exchanger in a defrosting operation;

fig. 6 is a schematic diagram of a refrigerant flow path of the heat exchanger provided in the embodiment of the disclosure as an outdoor heat exchanger during a cooling operation when the compressor operates at a low frequency;

fig. 7 is a schematic diagram of a refrigerant flow path of the heat exchanger provided in the embodiment of the disclosure as an outdoor heat exchanger during a heating operation when the compressor operates at a low frequency;

FIG. 8 is a schematic structural view of a second liquid separator according to an embodiment of the disclosure;

fig. 9 is a schematic structural diagram of another second liquid separator provided in the embodiments of the present disclosure.

Reference numerals:

100: a first header port; 200: a second header port; 311: a first heat exchange branch; 312: a second heat exchange branch; 320: a third heat exchange branch; 330: a fourth heat exchange branch; 340: a first bypass line; 341: a first solenoid valve; 350: a second bypass line; 351: a second solenoid valve; 400: a first liquid separator; 500: a second 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.

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 disclosed embodiments 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 in a matching way; 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; and 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.

In the heat exchanger and the air conditioner related to the embodiment of the disclosure, the bypass pipeline and the electromagnetic valve are arranged, so that the heat exchanger can respectively convey refrigerants through different flow paths in different air conditioning modes, and the performance requirements of the heat exchanger in different working modes can be simultaneously ensured. Meanwhile, the defrosting uniformity of the heat exchanger is improved by controlling the conduction or the closing of the electromagnetic valve. Most of the embodiments provided by the application are the embodiments when the heat exchanger is used as an outdoor heat exchanger.

As shown in fig. 1 to 9, when the air conditioner operates in a cooling condition and the heat exchanger is used as an outdoor heat exchanger, an embodiment of the present disclosure provides a heat exchanger, the heat exchanger includes a first heat exchanging portion, a second heat exchanging portion and a third heat exchanging portion, which are sequentially connected in series, the second heat exchanging portion includes a first end communicated with the first heat exchanging portion and a second end communicated with the third heat exchanging portion, and the heat exchanger further includes: a first bypass line 340 communicating the second end of the second heat exchange portion with the inlet end of the first heat exchange portion; and a second bypass line 350 communicating the first end of the second heat exchanging portion with the liquid outlet end of the third heat exchanging portion, wherein the first bypass line 340 is provided with a first electromagnetic valve 341, and the second bypass line 350 is provided with a second electromagnetic valve 351.

The heat exchanger provided by the embodiment of the present disclosure includes a first heat exchange portion, a second heat exchange portion and a third heat exchange portion which are sequentially connected in series, wherein a first solenoid valve 341 is disposed on a first bypass pipeline 340, and a second solenoid valve 351 is disposed on a second bypass pipeline 350. In this way, when refrigeration is performed, the first electromagnetic valve 341 and the second electromagnetic valve 351 are in a closed state, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are sequentially connected in series, the length of a flow path of a high-temperature refrigerant in the heat exchanger is prolonged, and the refrigerant can be fully subjected to heat exchange to realize 'supercooling'; when heating is performed, the first solenoid valve 341 and the second solenoid valve 351 are in a conducting state, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are connected in parallel, and the problem of pressure loss caused by too long flow paths is solved; when defrosting is performed, the first solenoid valve 341 and the second solenoid valve 351 are in a conducting state, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are connected in parallel, the temperature of pipelines of the heat exchange parts is kept at a high temperature, and the defrosting uniformity of the heat exchanger can be effectively improved.

Alternatively, when the compressor of the air conditioner operates in a low frequency state, the first solenoid valve 341 is controlled to be closed, and the second solenoid valve 351 is controlled to be opened, so that the refrigerant in the heat exchanger flows through only the first heat exchange portion.

The amount of refrigerant required by the compressor during low-frequency operation is less than that required during rated operation. The existing air conditioner cannot change the amount of the refrigerant in the refrigerating system when the compressor operates at low frequency, so that the amount of the refrigerant transported in the refrigerating system when the compressor operates at low frequency is larger than the actually required amount of the refrigerant, and further the energy efficiency of the compressor when the compressor operates at low frequency is low. Based on this, when the compressor of the air conditioner operates in a low frequency state, the heat exchanger provided in the embodiment of the present disclosure controls the first electromagnetic valve 341 to be closed, the second electromagnetic valve 351 to be turned on, the refrigerant only flows through the first heat exchanging portion, and most of the refrigerant in the second heat exchanging portion and the third heat exchanging portion is stored in the pipeline in a liquid state through condensation of the condenser, and does not participate in operation of the system. Therefore, the amount of the refrigerant circulating in the system when the compressor operates at the low frequency is reduced, and the energy efficiency of the air conditioner when the compressor operates at the low frequency is effectively improved.

Alternatively, when the air conditioner operates in the defrosting mode, the first solenoid valve 341 and the second solenoid valve 351 are controlled to be conducted so that the first heat exchange part, the second heat exchange part, and the third heat exchange part are communicated in parallel.

When defrosting is performed, the first electromagnetic valve 341 and the second electromagnetic valve 351 are controlled to be conducted, so that the first heat exchange part, the second heat exchange part and the third heat exchange part are communicated in parallel, the pipeline temperature of each heat exchange part is kept at a high temperature, and the defrosting uniformity of the heat exchanger can be effectively improved.

Optionally, the heat exchanger further comprises a first liquid separator 400 and a second liquid separator 500, which are disposed at the ports of the second bypass line 350 connected to the first end of the second heat exchange portion; the second liquid separator 500 is disposed at a port of the second bypass pipeline 350 connected to the liquid outlet end of the third heat exchange portion.

Therefore, the liquid separating function of the liquid separator can form a plurality of flow channels in a split flow mode in the process that the refrigerant flows along the heat exchange branch, so that the circulation of the refrigerant is more reasonable, and high heat exchange efficiency can be kept under the condition that the heat exchanger is used as an evaporator or a condenser.

Optionally, the second liquid separator 500 includes a housing, the housing has a liquid separating cavity therein, and the housing is opened with a first liquid separating port and a second liquid separating port; the collecting pipe 520 comprises a first pipe section 521 and a second pipe section 522 which are communicated in a bending mode, and the first pipe section 521 is directly communicated with the liquid separating cavity; a first branch liquid-dividing pipe 530 communicated with the liquid-dividing chamber through the first liquid-dividing port, and the first branch liquid-dividing pipe 530 is communicated with the second bypass line 350; and the second branch liquid distribution pipe 540 is communicated with the liquid distribution cavity through the second liquid distribution port, and the second branch liquid distribution pipe 540 is communicated with the third heat exchange part, wherein the plane where the axes of the first pipe section 521 and the second pipe section 522 are located is a first plane, the plane where the axes of the first branch liquid distribution pipe 530 and the second branch liquid distribution pipe 540 are located is a second plane, and the first plane and the second plane are not vertical.

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. 9. 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 non-perpendicular to the second plane, such that the amount of refrigerant entering the first branch 530 and the second branch 540 via 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.

Optionally, the first heat exchange portion is disposed at an upper portion of the second heat exchange portion, and the second heat exchange portion is disposed at an upper portion of the third heat exchange portion.

Optionally, the first heat exchange portion comprises a first heat exchange branch 311 and a second heat exchange branch 312 which are communicated in parallel; the second heat exchanging part comprises a third heat exchanging branch 320; and, the third heat exchanging part includes a fourth heat exchanging branch 330.

In this embodiment, the structures of the single heat exchange tubes in the first heat exchange branch 311, the second heat exchange branch 312, the third heat exchange branch 320 and the fourth heat exchange branch 330 adopt the same structural design, for example, the diameters of the single heat exchange tubes in the first heat exchange branch 311, the second heat exchange branch 312, the third heat exchange branch 320 and the fourth heat exchange branch 330 are the same, the thicknesses of the tubes are uniform, the curvatures and the lengths of the bent tubes are the same, and the like, so that the refrigerant can uniformly flow in the heat exchanger, and unstable changes in pressure and flow rate of the refrigerant caused by the change in the tube diameters are avoided, so that the refrigerant can stably realize heat exchange with the surrounding environment when flowing through the heat exchanger.

The heat exchange tube definition mainly aims at division of the refrigerant by pipelines of each part downward in refrigeration flow, but does not limit structural design of the heat exchanger, heat exchange effect of heating flow direction and the like.

As shown in the heat exchanger of fig. 4, when the heat exchanger is used as an evaporator, the refrigerant is divided by the second liquid separator 500 and then flows into four heat exchange branches connected in parallel, that is, a first heat exchange branch 311, a second heat exchange branch 312, a third heat exchange branch 320, and a fourth heat exchange branch 330. In the direction shown in fig. 4, the refrigerant flows through the liquid separating branch pipe on the left side of the second liquid separator 500 and then flows into only the fourth heat exchange branch 330, and the refrigerant flows through the liquid separating branch pipe on the right side of the second liquid separator 500 and then flows into three heat exchange branches, namely, the first heat exchange branch 311, the second heat exchange branch 312 and the third heat exchange branch 320. It can be seen that after the refrigerant passes through the second liquid separator 500, the refrigerant amount required by the two liquid separating branch pipes of the second liquid separator 500 is different. In the heat exchanger shown in fig. 4, the refrigerant quantity required for the right branch liquid dividing pipe is approximately 3 times the refrigerant quantity of the left branch liquid dividing 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 the first pipe section 521 of the manifold 520 is larger than the inner diameter of the first branch liquid pipe 530.

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.

By only limiting the difference in the inner diameters of the first branch liquid-dividing pipe 530 and the second branch liquid-dividing pipe 540, it is difficult to achieve refrigerant distribution with a refrigerant flow rate difference of 3. 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 diameter of the liquid separating branch pipe, in order to realize refrigerant distribution with a flow ratio of 3. Therefore, it is difficult to achieve refrigerant distribution with a flow rate ratio of the first branch liquid-separating pipe 530 to the second branch liquid-separating pipe 540 of 3.

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

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

Alternatively, the inner diameter of first branch liquid-dividing line 530 is greater than or equal to 5.1mm, and less than or equal to 6.1mm; the second branch liquid-dividing pipe 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, the heat in the ambient air is continuously absorbed from the low-temperature liquid state, and reaches a gas-liquid two-phase state along with the temperature rise, the temperature is kept constant at the evaporating temperature at this time, only the phase change from the liquid state to the gas state is continuously generated, the liquid state refrigerants are less and less, the gas state refrigerants are more and more, the refrigerant is just completely changed into the gas state when reaching the outlet of the whole heat exchange branch, and the temperature is 1-2 ℃ higher than the evaporating temperature. 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 that the heat exchange effect of the whole heat exchanger is poor under the same refrigerant flow, and the capacity of the air conditioner is very low. Therefore, the method for judging good split of experience during heating is as follows: the temperature difference of the outlets of the branches is within 2 ℃, the superheat degree of the outlets is about 1 ℃, and the shunting is better under the condition.

TABLE 1

TABLE 2

Alternatively, when the air conditioner operates in a heating working condition and the heat exchanger serves as an evaporator, and the first heat exchange branch 311, the second heat exchange branch 312, and the third heat exchange branch 320 connected in parallel are communicated with the first liquid-dividing branch pipe 530, and the fourth heat exchange branch 330 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 shown in table 1 and table 2. Table 1 shows the maximum temperature difference between the fourth heat exchange branch 330 and the first three branches and the heating capacity of the air conditioner under different inner diameters of the first liquid-dividing branch 530 and the second liquid-dividing branch 540 when the included angle between the first plane and the second plane is 90 degrees. As can be seen from the data in table 1, when the inner diameter of the first branch liquid dividing pipe 530 is 5.6mm, and the inner diameter of the second branch liquid dividing pipe 540 is 3.36mm, the maximum temperature difference between the fourth heat exchanging branch 330 and the first three branches of the heat exchanger is 3.4 ℃, and the heating capacity of the air conditioner is 4855.2W at the inner diameter. Table 2 shows that when the inner diameter of the first branch liquid-dividing pipe 530 is 5.6mm, and the inner diameter of the second branch liquid-dividing pipe 540 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the fourth heat exchange branch 330 and the first three branches is equal to the heating capacity of the air conditioner. As can be seen from table 2, when the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth heat exchange branch 330 and the first three branches is the smallest, which is 1.2 ℃, and the heating capacity of the air conditioner is the largest at this angle, which is 5016.1W.

As can be seen from the data in tables 1 and 2, when the number of the heat exchange branches in the heat exchanger, which are communicated with the first branch liquid pipe 530, is 3, and the number of the heat exchange branches in the heat exchanger, which are communicated with the second branch liquid pipe 540, is 1, for example, as shown in the heat exchanger shown in fig. 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-separation pipe 530 to the amount of refrigerant in the second branch liquid-separation pipe 540 is 3.

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-separating 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-separating 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 branch liquid-separating pipe 530 to the refrigerant amount in the second branch liquid-separating pipe 540 can be better realized to be 3. The temperature difference realized by other inner diameters and included angles and the heating capacity of the air conditioner in the embodiment are similar to the data in tables 1 and 2, and are not repeated here.

According to the heat exchanger provided by the embodiment of the disclosure, due to the arrangement of the first electromagnetic valve 341 and the second electromagnetic valve 351, performance requirements of the heat exchanger under different working modes can be ensured simultaneously by controlling the conduction or the closure of the first electromagnetic valve 341 and the second electromagnetic valve 351.

As shown in fig. 3, the refrigerant flows downward, the first solenoid valve 341 and the second solenoid valve 351 are closed, and the flow path of the refrigerant in the heat exchanger is: the refrigerant enters through the first header 100 and is divided into two paths, the first path flows through the first heat exchange branch 311, the second path flows through the second heat exchange branch 312, the two paths converge at the first liquid separator 400, flow through the third heat exchange branch 320, flow through the fourth heat exchange branch 330, flow through the second liquid separator 500, and then flow out of the heat exchanger through the second header 200. It can be seen that, when the refrigerant flows downwards, due to the arrangement of the first solenoid valve 341 and the second solenoid valve 351, the length of the refrigerant path flowing downwards in the refrigeration flow direction is increased, the heat exchange time of the refrigerant in the heat exchanger is prolonged, the refrigerant can fully exchange heat with the surrounding environment, in addition, the branch paths through which the refrigerant flows are less, the flow rate is higher, the heat exchange effect of the heat exchanger is improved, and further, the refrigeration efficiency of the air conditioner is improved.

As shown in fig. 4, the heating flow is downward, the first solenoid valve 341 and the second solenoid valve 351 are turned on, and the flow path of the refrigerant in the heat exchanger is: the refrigerant enters through the second header 200 and is divided into four paths, the first path passes through the second liquid separator 500, then flows through the fourth heat exchange branch 330, passes through the first electromagnetic valve 341, and then flows out of the first header 100; the second branch passes through a second liquid separator 500, a second electromagnetic valve 351 and a first liquid separator 400, then flows through a third heat exchange branch 320, passes through a first electromagnetic valve 341 and then flows out of the first main port 100; the third branch passes through the second heat exchange branch 312 after passing through the second liquid separator 500, the second solenoid valve 351 and the first liquid separator 400, and then flows out of the first main port 100; the fourth branch passes through the second liquid separator 500, the second solenoid valve 351 and the first liquid separator 400, then flows through the first heat exchange branch 311, and then flows out of the first main port 100. It can be seen that, in the heating direction, due to the arrangement of the first solenoid valve 341 and the second solenoid valve 351, the first heat exchange branch 311, the second heat exchange branch 312, the third heat exchange branch 320 and the fourth heat exchange branch 330 are connected in parallel and communicated, at this time, the number of branches through which the refrigerant flows is large, the problem of pressure loss caused by too long flow paths is avoided, the heat exchange efficiency of the heat exchanger is improved, and further the heating efficiency of the air conditioner is improved.

As shown in fig. 5, the defrost flow is downward, the first solenoid valve 341 and the second solenoid valve 351 are turned on, and the flow path of the refrigerant in the heat exchanger is: the refrigerant enters through the first header 100 and is divided into four paths, and the refrigerant flows through the first heat exchange branch 311, the first liquid separator 400, the second solenoid valve 351 and the second liquid separator 500 and then flows out of the second header 200; the second branch flows through the second heat exchange branch 312, the first liquid separator 400, the second solenoid valve 351 and the second liquid separator 500 and then flows out of the second header 200; the third branch flows through the first solenoid valve 341, the third heat exchange branch 320, the first liquid separator 400, the second solenoid valve 351 and the second liquid separator 500 and then flows out of the second header 200; the fourth branch flows through the first solenoid valve 341, the fourth heat exchange branch 330 and the second liquid separator 500 and then flows out of the second header 200; it can be seen that, when the defrosting flow is downward, due to the arrangement of the first solenoid valve 341 and the second solenoid valve 351, the first heat exchange branch 311, the second heat exchange branch 312, the third heat exchange branch 320, and the fourth heat exchange branch 330 are connected in parallel and communicated, at this time, the number of branches through which the refrigerant flows is large, and then the temperature of the pipelines of each heat exchange portion is kept at a high temperature, so that the defrosting uniformity of the heat exchanger can be effectively improved.

As shown in fig. 6, when the compressor is operated at a low frequency, the first solenoid valve 341 is closed and the second solenoid valve 351 is opened, and the flow path of the refrigerant in the heat exchanger is: the refrigerant enters through the first header 100 and is split into two paths, the first path is a path passing through the first heat exchange branch 311, the second path passes through the second heat exchange branch 312, the two paths converge at the first liquid separator 400, and the refrigerant flows out of the second header 200 after passing through the second solenoid valve 351 and the second liquid separator 500.

As shown in fig. 7, when the compressor is operated at a low frequency, the first solenoid valve 341 is closed and the second solenoid valve 351 is opened when the heating flow is downward, and the flow path of the refrigerant in the heat exchanger is: the refrigerant enters through the second header 200, flows through the second liquid separator 500 and the second solenoid valve 351, is divided into two paths through the first liquid separator 400, and flows out of the first header 100 after flowing through the first heat exchange branch 311 and the second heat exchange branch 312 respectively. It can be seen that, in the heat exchanger provided in the embodiment of the present disclosure, due to the arrangement of the first electromagnetic valve 341 and the second electromagnetic valve 351, the amount of refrigerant circulating in the system when the compressor operates at a low frequency is reduced, and thus the energy efficiency of the air conditioner when the compressor operates at a low frequency is effectively improved.

Optionally, an air conditioner, comprising a heat exchanger as described above.

The air conditioner provided by the embodiment of the disclosure comprises a refrigerant circulation loop at least composed of an indoor heat exchanger, an outdoor heat exchanger, a compressor and a four-way valve, wherein the indoor heat exchanger and/or the outdoor heat exchanger are/is the heat exchanger.

Optionally, in the refrigeration mode and when the heat exchanger is used as an outdoor heat exchanger, the first header port 100 is used as a port through which a refrigerant flows in, and the second header port 200 is used as a port through which the refrigerant flows out; in the heating mode, when the heat exchanger is used as an outdoor heat exchanger, the first header 100 serves as a refrigerant outflow port, and the second header 200 serves as a refrigerant inflow port.

Optionally, in the cooling mode and when the heat exchanger is used as an indoor heat exchanger, the first header port 100 is a port through which a refrigerant flows out, and the second header port 200 is a port through which a refrigerant flows in; in the heating mode, when the heat exchanger is used as an indoor heat exchanger, the first header port 100 is a port through which a refrigerant flows in, and the second header port 200 is a port through which the refrigerant flows out.

The air conditioner adopting the heat exchanger shown in the embodiment can respectively convey the refrigerant in different flow directions when the air conditioner operates in a refrigeration mode, a heating mode, a defrosting mode and a compressor operates at a low frequency, not only can make the refrigerant fully exchange heat downwards to realize supercooling in the refrigeration flow direction, can avoid the problem of pressure loss caused by overlong flow path downwards in the heating flow direction, can improve the defrosting uniformity downwards in the defrosting flow direction, and effectively improve the energy efficiency of the air conditioner when the compressor operates at the low frequency, thereby simultaneously ensuring the performance requirements of the heat exchanger in different working modes.

The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims (8)

1. A heat exchanger, wherein when an air conditioner operates in a cooling condition and the heat exchanger is used as an outdoor heat exchanger, the heat exchanger comprises a first heat exchanging portion, a second heat exchanging portion and a third heat exchanging portion which are sequentially connected in series, the second heat exchanging portion comprises a first end communicated with the first heat exchanging portion and a second end communicated with the third heat exchanging portion, and the heat exchanger further comprises:

the first bypass pipeline is communicated with the second end of the second heat exchange part and the liquid inlet end of the first heat exchange part; and (c) and (d),

a second bypass pipeline which is communicated with the first end of the second heat exchange part and the liquid outlet end of the third heat exchange part,

the first bypass pipeline is provided with a first electromagnetic valve, and the second bypass pipeline is provided with a second electromagnetic valve.

2. The heat exchanger of claim 1, further comprising:

the first liquid separator is arranged at a port of the second bypass pipeline, which is connected with the first end of the second heat exchange part; and the combination of (a) and (b),

and the second liquid separator is arranged at a port of the second bypass pipeline connected with the liquid outlet end of the third heat exchange part.

3. The heat exchanger of claim 2, wherein the second liquid separator comprises:

the liquid separation device comprises a shell, a liquid separation device and a liquid separation device, wherein a liquid separation cavity is formed in the shell, and a first liquid separation port and a second liquid separation port are formed in the shell;

the collecting pipe comprises a first pipe section and a second pipe section which are connected in a bent mode, and the first pipe section is directly connected with the liquid separating cavity;

the first liquid separation branch pipe is communicated with the liquid separation cavity through the first liquid separation port and communicated with the second bypass pipeline; and the combination of (a) and (b),

a second branch liquid dividing pipe communicated with the liquid dividing cavity through the second liquid dividing port and communicated with the third heat exchange part,

the plane of the axes of the first pipe section and the second pipe section is a first plane, the plane of the axes of the first branch liquid distribution pipe and the second branch liquid distribution pipe is a second plane, and the first plane is not perpendicular to the second plane.

4. The heat exchanger of claim 3,

the included angle between the first plane and the second plane is greater than or equal to 50 degrees and less than or equal to 70 degrees; alternatively, the first and second electrodes may be,

the included angle between the first plane and the second plane is greater than or equal to 30 degrees and less than or equal to 60 degrees.

5. The heat exchanger of claim 4,

the inner diameter of the first liquid separation branch pipe is greater than or equal to 5.1mm and less than or equal to 6.1mm;

the inner diameter of the second branch liquid-dividing pipe is more than or equal to 3.1mm and less than or equal to 3.7mm.

6. The heat exchanger according to any one of claims 3 to 5,

the first heat exchanging part is disposed at an upper portion of the second heat exchanging part, and the second heat exchanging part is disposed at an upper portion of the third heat exchanging part.

7. The heat exchanger of claim 1,

the first heat exchange part comprises a first heat exchange branch and a second heat exchange branch which are communicated in parallel;

the second heat exchange part comprises a third heat exchange branch; and the number of the first and second electrodes,

the third heat exchanging part comprises a fourth heat exchanging branch.

8. An air conditioner characterized by comprising the heat exchanger according to any one of claims 1 to 7.

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