CN216814680U

CN216814680U - Heat exchanger and air conditioner

Info

Publication number: CN216814680U
Application number: CN202122679660.5U
Authority: CN
Inventors: 丁爽; 王飞; 张鹏; 蒋骏; 李伟伟
Original assignee: Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Current assignee: 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: 2021-11-03
Publication date: 2022-06-24
Anticipated expiration: 2031-11-03
Also published as: CN216745036U; CN114165946A; CN216716627U; CN217817557U; CN216977244U; CN216694079U; CN216694107U; CN116045486A; CN217357662U; CN216694086U; CN216716629U; CN217357660U; CN216744999U; CN216694084U; CN216694081U; CN217357659U; CN216694077U; CN216716628U; CN216694088U; CN216694076U

Abstract

The utility model relates to an air conditioner technical field discloses a heat exchanger, including first main line, second main line, first heat transfer route, second heat transfer route, third heat transfer route, fourth heat transfer route, first bypass pipeline, second bypass pipeline and third bypass pipeline, wherein be equipped with first check valve on the first bypass pipeline, be equipped with the second check valve on the second bypass pipeline, the third bypass pipeline is equipped with the third check valve. When the refrigerant enters the heat exchanger from the first main pipeline for circulation, the circulation path of the refrigerant in the heat exchanger can be effectively shortened, and the rapid circulation of the refrigerant is facilitated; when the refrigerant enters the heat exchanger from the second main pipeline for circulation, the circulation path and the circulation time of the refrigerant in the heat exchanger can be prolonged, and the pressure drop in the heat exchanger is reduced. The third shunting element is communicated with the first shunting element through two bypass pipelines respectively provided with the one-way valves, so that abnormal sound generated when the refrigerant with larger flow impacts the one-way valves can be relieved. The application also discloses an air conditioner.

Description

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. 202122281454.9, is hereby incorporated by reference in its entirety.

Technical Field

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

Background

At present, an air conditioner generally comprises a refrigerant circulation loop consisting of a compressor, an outdoor heat exchanger, a throttling device, a four-way valve and an indoor heat exchanger, and the flow direction of a refrigerant in the refrigerant circulation loop is changed by the four-way valve, so that the refrigeration function and the heating function of the air conditioner are respectively realized.

The heat exchanger is downward in heating flow, a refrigerant in a heat exchange tube is positioned in a high-temperature and high-pressure area and is insensitive to pressure drop, and the heat transfer performance is mainly influenced by a heat transfer coefficient, so that the heat exchange tube is suitable for adopting fewer branches to accelerate circulation and increase the heat transfer coefficient; the heat exchanger has downward refrigerating flow, the refrigerant in the heat exchange tube is in a low-temperature and low-pressure area, and the heat transfer performance is mainly constrained by the heat transfer coefficient and the pressure drop, so that the heat exchange tube is suitable for adopting more branches, the heat transfer coefficient is ensured, and the pressure drop is greatly reduced to improve the system pressure.

The prior art discloses a heat exchanger, and this heat exchanger adopts shunt tubes or shunt to carry out the reposition of redundant personnel design to make the heat exchanger more branches of refrigerant flow through downwards at the refrigeration flow, prolonged the circulation route of refrigerant, reduced the pressure drop, promoted the heat exchanger and made the downward performance of refrigeration flow.

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 heat exchanger is downward in heating flow, the flow direction of the refrigerant circulation loop is changed, at the moment, the refrigerant needs to reversely flow along a downward flow path of the refrigerant flow of the heat exchanger, at the moment, the flow path is long, the refrigerant is not favorable for quick circulation, and the integral heat exchange efficiency of the air conditioner is reduced.

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 are used for solving the problem of how to enable the heat exchanger to extend a refrigerant flow path downwards in a refrigeration flow direction and shorten the refrigerant flow path downwards in a heating flow direction.

In some embodiments, the heat exchanger comprises:

a first main pipeline;

a second main pipeline;

a first heat exchange passage, a first end of which is communicated with the first flow dividing element, and a second end of which is communicated with the second flow dividing element; and the first shunt element is communicated with the first main pipeline;

a second heat exchange path having a first end connected to the first flow dividing element and a second end connected to the second flow dividing element;

a third heat exchange passage having a first end connected to the third flow dividing element and a second end connected to the second flow dividing element;

a fourth heat exchange path, a first end of which is communicated with the third flow dividing element and a second end of which is communicated with the fourth flow dividing element; and the fourth shunt element is communicated with the second main pipeline;

a first bypass line, a first end of which is communicated with the first flow dividing element, and a second end of which is communicated with the third flow dividing element;

a first end of the second bypass pipeline is communicated with the first flow dividing element, and a second end of the second bypass pipeline is communicated with the third flow dividing element;

a third bypass line, a first end of which is communicated with the second shunt element and a second end of which is communicated with the fourth shunt element;

a first check valve provided in the first bypass line, and a direction of conduction of the first check valve being defined to flow from the third branching element to the first branching element;

a second check valve provided in the second bypass line, a conduction direction of the second check valve being defined to flow from the third shunt element to the first shunt element;

and a third check valve disposed in the third bypass line, and a direction of conduction of the third check valve is defined to flow from the fourth shunt element to the second shunt element.

Optionally, the fourth shunt element comprises:

the shell is internally provided with a liquid dividing cavity which is provided with a first liquid dividing port and a second liquid dividing port;

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 (c) and (d),

a second liquid dividing branch pipe communicated with the liquid dividing cavity through the second liquid dividing port,

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.

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.

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

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

Optionally, the second pipe section is disposed to be biased to the second branch pipe side.

Optionally, the first dividing element, the second dividing element, the third dividing element and the fourth dividing element are respectively a refrigerant distributor.

Optionally, heat exchange tubes respectively included in the first heat exchange passage, the second heat exchange passage, the third heat exchange passage, and the fourth heat exchange passage are all copper tubes.

Optionally, the heat exchanger further comprises:

a casing having a tube plate therein; and heat exchange tubes respectively contained in the first heat exchange passage, the second heat exchange passage, the third heat exchange passage and the fourth heat exchange passage are fixed in the shell through the tube plates.

Optionally, the first and third dividing elements are disposed on one side of the casing, and the second and fourth dividing elements are disposed on the other side of the casing.

Optionally, the height of the first dividing element is greater than the height of the third dividing element.

Optionally, the height of the second flow dividing element is greater than the height of the fourth flow dividing element.

Optionally, the height of the second flow dividing element is equal to the height of the third flow dividing element.

The air conditioner comprises a refrigerant circulating 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 is/are the heat exchanger described in any of the above embodiments.

Optionally, the outdoor heat exchanger is the heat exchanger;

in a cooling mode, the first main pipeline of the outdoor heat exchanger is communicated with the exhaust port of the compressor, and the second main pipeline of the outdoor heat exchanger is communicated with the indoor heat exchanger;

in the heating mode, the second main pipeline of the outdoor heat exchanger is communicated with the indoor heat exchanger, and the first main pipeline of the outdoor heat exchanger is communicated with the air suction port of the compressor.

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

when the refrigerant enters the first flow dividing element from the first main pipeline, the refrigerant in the heat exchanger flows in a heating flow direction, the flowing path of the refrigerant comprises a first heat exchange path, a second heat exchange path, a third heat exchange path and a fourth heat exchange path, the first heat exchange path and the second heat exchange path form a fourth parallel path, and the fourth parallel path, the third heat exchange path and the fourth heat exchange path form a series path. Therefore, the circulation path of the refrigerant in the heat exchanger is effectively shortened, the rapid circulation of the refrigerant is facilitated, and the performance of the heat exchanger is improved.

When the refrigerant enters the second flow dividing element from the second main pipeline, the refrigerant in the heat exchanger circulates in a refrigerating flow direction, the circulation path of the refrigerant comprises a first heat exchange path, a second heat exchange path, a third heat exchange path, a fourth heat exchange path, a first bypass pipeline, a second bypass pipeline and a third bypass pipeline, the first heat exchange path, the second heat exchange path and the third heat exchange path form a first parallel path, the first parallel path and the fourth heat exchange path form a second parallel path, and the first bypass pipeline and the second bypass pipeline form a third parallel path. Therefore, the circulation path and the circulation time of the refrigerant in the heat exchanger are effectively prolonged, the pressure drop in the heat exchanger is reduced, and the performance of the heat exchanger is improved. In addition, the third shunting element adopts two bypass pipelines, and compared with the mode that one bypass pipeline is communicated with the first shunting element, the third shunting element can effectively shunt, so that abnormal sound generated by impact of a valve core of the one-way valve and other structures due to the fact that a refrigerant with a larger flow impacts the valve core of the one-way valve is relieved.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

fig. 1 is a schematic diagram of a refrigerant circulation circuit according to an embodiment of the disclosure;

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

fig. 3 is a schematic view of a refrigerant flow path of a heat exchanger provided in an embodiment of the present disclosure and flowing downward in a heating flow direction;

fig. 4 is a schematic diagram of a refrigerant flow path of the heat exchanger provided in the embodiment of the present disclosure in which a refrigerant flows downward;

fig. 5 is a schematic diagram illustrating a refrigerant flow path formed by a plurality of heat pipes of the heat exchanger according to the embodiment of the present disclosure;

FIG. 6 is a schematic structural diagram of a fourth shunt element provided by an embodiment of the present disclosure;

fig. 7 is a schematic structural diagram of a fourth shunt element at another angle provided by an embodiment of the present disclosure.

Reference numerals:

100: a first main pipeline; 110: a second main pipeline;

200: a first heat exchange path; 210: a second heat exchange path; 220: a third heat exchange path; 230: a fourth heat exchange path; 240: a first bypass line; 250: a second bypass line; 260: a third bypass line;

300: a first shunt element; 310: a second shunt element; 320: a third flow dividing element; 330: a fourth shunt element;

400: a first check valve; 410: a second one-way valve; 420: a third check valve;

500: a compressor; 510: an outdoor heat exchanger; 520: an indoor heat exchanger; 530: a throttling device; 540: a housing;

600: a collector pipe; 601: a first tube section; 602: a second tube section; 610: a liquid separation cavity; 611: a first branch chamber; 612: a second branch chamber; 620: a first branch liquid-separating pipe; 621: a second branch liquid 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 examples and are not intended to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used 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. For example, a and/or B, represents: a or B, or A and B.

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

A refrigerant circulation circuit of an air conditioner is generally composed of a compressor 500, an outdoor heat exchanger 510, a throttle device 530, an indoor heat exchanger 520, and a four-way valve for changing a flow direction of a refrigerant in the refrigerant circulation circuit. When the air conditioner operates in a cooling mode, a refrigerant discharged from the compressor 500 passes through the outdoor heat exchanger 510, the throttling device 530, and the indoor heat exchanger 520 in sequence by the four-way valve, and finally returns to the compressor 500 to be compressed again. When the air conditioner operates in a heating mode, a refrigerant discharged from the compressor 500 passes through the indoor heat exchanger 520, the throttling device 530, and the outdoor heat exchanger 510 in sequence through the four-way valve, and finally returns to the compressor 500 to be compressed again.

As shown in fig. 1 to 7, an embodiment of the present disclosure provides a heat exchanger, which includes a first main pipe 100, a second main pipe 110, a first heat exchange path 200, a second heat exchange path 210, a third heat exchange path 220, a fourth heat exchange path 230, a first bypass path 240, a second bypass path 250, a third bypass path 260, a first check valve 400, a second check valve 410, and a third check valve 420. Wherein, the first end of the first heat exchange channel 200 is communicated with the first flow dividing element 300, and the second end thereof is communicated with the second flow dividing element 310; moreover, the first shunt element 300 is in communication with the first main line 100; the first end of the second heat exchange path 210 is communicated with the first flow dividing element 300, and the second end is communicated with the second flow dividing element 310; the first end of the third heat exchange path 220 is communicated with the third flow dividing element 320, and the second end thereof is communicated with the second flow dividing element 310; the first end of the fourth heat exchange path 230 is communicated with the third flow dividing element 320, and the second end thereof is communicated with the fourth flow dividing element 330; and, fourth shunt element 330 is in communication with second main line 110; the first bypass line 240 has a first end connected to the first flow dividing element 300 and a second end connected to the third flow dividing element 320; the first end of the second bypass line 250 is connected to the first flow dividing element 300, and the second end thereof is connected to the third flow dividing element 320; the first end of the third bypass line 260 is connected to the second flow dividing element 310, and the second end thereof is connected to the fourth flow dividing element 330; the first check valve 400 is disposed in the first bypass line 240, and a direction of conduction of the first check valve 400 is defined to flow from the third shunting element 320 to the first shunting element 300; the second check valve 410 is disposed in the second bypass line 250, and a direction of conduction of the second check valve 410 is defined to flow from the third shunting element 320 to the first shunting element 300; the third check valve 420 is disposed in the third bypass line 260, and a direction of conduction of the third check valve 420 is defined to flow from the fourth dividing element 330 to the second dividing element 310.

With the heat exchanger provided in the embodiment of the present disclosure, when the refrigerant enters the first flow dividing element 300 from the first main pipeline 100, the refrigerant in the heat exchanger flows in a heating flow direction, as shown in fig. 3. Firstly, under the unidirectional conduction action of the first check valve 400 and the second check valve 410, the refrigerant in the first flow dividing element 300 can only enter the second flow dividing element 310 through the first heat exchange passage 200 and the second heat exchange passage 210, respectively. Then, under the unidirectional conduction action of the third check valve 420, the refrigerant in the second flow dividing element 310 can only enter the third flow dividing element 320 through the third heat exchange path 220. As the refrigerant circulates, the pressure in the third flow dividing element 320 is lower than the pressure in the first flow dividing element 300, and the refrigerant in the third flow dividing element 320 can only enter the fourth flow dividing element 330 through the fourth heat exchanging channel 230. Finally, the refrigerant in the fourth flow dividing element 330 flows out through the second main pipe 110.

When the refrigerant enters the fourth flow dividing element 330 from the second main pipeline 110, the refrigerant in the heat exchanger flows in a cooling flow direction, as shown in fig. 4. First, the refrigerant in the fourth flow dividing element 330 is divided into two paths, one path enters the third flow dividing element 320 through the fourth heat exchanging path 230, and the other path enters the second flow dividing element 310 through the third bypass line 260. Then, the refrigerant in the second flow dividing element 310 is divided into three paths, one path enters the third flow dividing element 320 through the third heat exchanging path 220, the other path enters the first flow dividing element 300 through the first heat exchanging path 200, and the other path enters the first flow dividing element 300 through the second heat exchanging path 210. Then, the refrigerant in the third flow dividing element 320 is divided into two paths, one path enters the first flow dividing element 300 through the first bypass line 240, and the other path enters the first flow dividing element 300 through the second bypass line 250. Finally, the refrigerant in the first flow dividing element 300 flows out through the first main pipeline 100. Since the flow rate in the third flow dividing element 320 is the sum of the flow rates of the third heat exchange passage 220 and the fourth heat exchange passage 230, the flow rate in the third flow dividing element 320 is much about twice the flow rate of the first heat exchange passage 200 or the second heat exchange passage 210. Here, two bypass lines, that is, the first bypass line 240 provided with the first check valve 400 and the second bypass line 250 provided with the second check valve 410 are adopted, compared with the case where the two bypass lines are communicated with the first flow dividing element 300 through one bypass line, the two bypass lines can effectively divide the flow, so that abnormal noise generated when the valve core collides with other structures due to the impact of a refrigerant with a large flow rate on the valve core of the check valve is relieved.

The heat exchanger flows downwards in the refrigeration process, the circulation path of the refrigerant comprises a first heat exchange path 200, a second heat exchange path 210, a third heat exchange path 220, a fourth heat exchange path 230, a first bypass path 240, a second bypass path 250 and a third bypass path 260, the first heat exchange path 200, the second heat exchange path 210 and the third heat exchange path 220 form a first parallel path, the first parallel path and the fourth heat exchange path 230 form a second parallel path, and the first bypass path 240 and the second bypass path 250 form a third parallel path. Therefore, the circulation path and the circulation time of the refrigerant in the heat exchanger are effectively prolonged, the pressure drop in the heat exchanger is reduced, and the performance of the heat exchanger is improved. The heat exchanger flows downwards in the heating direction, the circulation path of the refrigerant comprises a first heat exchange path 200, a second heat exchange path 210, a third heat exchange path 220 and a fourth heat exchange path 230, the first heat exchange path 200 and the second heat exchange path 210 form a fourth parallel path, and the fourth parallel path, the third heat exchange path 220 and the fourth heat exchange path 230 form a series path. Therefore, the circulation path of the refrigerant in the heat exchanger is effectively shortened, and the rapid circulation of the refrigerant is facilitated, and the performance of the heat exchanger is improved.

In some embodiments, fourth branching element 330 comprises a housing, a manifold 600, a first branch manifold 620, and a second branch manifold 621. The inside branch liquid chamber 610 of having seted up of casing, first branch liquid mouth and second branch liquid mouth have been seted up to the casing, collecting pipe 600 with divide liquid chamber 610 intercommunication, first branch liquid pipe 620 divides liquid mouth and divide liquid chamber 610 intercommunication through first branch liquid mouth, second branch liquid pipe 621 divides liquid mouth and divide liquid chamber 610 intercommunication through the second.

Optionally, the liquid separating cavity 610 comprises a confluence cavity, a first branch cavity 611 and a second branch cavity 612, the first branch liquid pipe 620 is communicated with the first branch cavity 611 through a first liquid separating port, and the second branch liquid pipe 621 is communicated with the second branch cavity 612 through a second liquid separating port.

Optionally, the collecting pipe 600 comprises a first pipe section 601 and a second pipe section 602 which are communicated in a bending way, and the first pipe section 601 is directly communicated with the liquid dividing cavity 610.

The plane in which the axes of the first and

second tube sections

601, 602 lie is the first plane. The plane in which the axes of the first branch fluid diverting pipe 620 and the second branch fluid diverting pipe 621 are located is the second plane. Optionally, the first plane is non-perpendicular to the second plane.

The manifold 600 comprises a first pipe segment 601 and a second pipe segment 602, the plane of the axes of the first pipe segment 601 and the second pipe segment 602 is a first plane, and the included angle between the first plane and the second plane is e. As shown in fig. 6. The first plane is non-perpendicular to the second plane, it being understood that the angle e between the first plane and the second plane is less than 90 °. Optionally, the angle between the first plane and the second plane is measured as the acute angle formed by the two planes. The first plane is non-perpendicular to the second plane such that the amount of refrigerant entering the first branch 620 and the second branch 621 through the first pipe segment 601 is different. For example, when the angle between the first plane and the second plane is on the side of the first branch liquid-separating pipe 620, the flow rate of the refrigerant flowing to the second branch liquid-separating pipe 621 is greater than the flow rate flowing to the first branch liquid-separating pipe 620 under the action of gravity. Similarly, when the included angle between the first plane and the second plane is on the side of the second branch liquid dividing pipe 621, the flow rate of the refrigerant flowing to the first branch liquid dividing pipe 620 is greater than the flow rate of the refrigerant flowing to the second branch liquid dividing pipe 621 under the action of gravity.

It is difficult to achieve refrigerant distribution with a flow ratio of 3:1 between the first branch liquid-dividing pipe 620 and the second branch liquid-dividing pipe 621 only by limiting the difference in the inner diameters of the first branch liquid-dividing pipe 620 and the second branch liquid-dividing pipe 621. 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 in which the flow ratio of the first branch liquid-dividing pipe 620 to the second branch liquid-dividing pipe 621 is 3:1 within a range not exceeding the allowable pipe diameter of the heat exchange pipe in the heat exchanger, only by limiting the difference in the inner diameters of the first branch liquid-dividing pipe 620 and the second branch liquid-dividing pipe 621.

According to the technical scheme, the included angle is formed between the first plane where the axes of the first pipe section 601 and the second pipe section 602 of the collecting pipe 600 are located and the second plane where the axes of the two liquid separating branch pipes are located, and the inner diameter difference between the two liquid separating branch pipes is further matched, so that the refrigerant flow ratio of the two liquid separating branch pipes is 3:1 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 pipe 621 does not need to be designed to be too small, and the flow rate of the refrigerant in the first branch liquid pipe 620 is much larger than that of the refrigerant in the second branch liquid pipe 621. Therefore, the refrigerant distribution scheme of the fourth shunting element 330 provided by the embodiment of the disclosure avoids the problem of excessive total pressure drop of the liquid dividing branch pipes of the fourth shunting element 330 and the heat exchanger when the refrigerant distribution ratio of the two liquid dividing branch pipes is relatively large.

Optionally, an included angle between a first plane where the axes of the first pipe section 601 and the second pipe section 602 of the collecting pipe 600 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 fluid distribution pipe 620 and the second branch fluid distribution pipe 621 is increased. Optionally, the inner diameter of first branch liquid-separating tube 620 is greater than or equal to 5.1mm and less than or equal to 6.1 mm; the inner diameter of the second branch liquid-dividing pipe 621 is 3.1mm or more and 3.7mm or less. Optionally, the second pipe section 602 of the collecting pipe 600 is inclined towards the second branch pipe 621 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 diphasic attitude along with the temperature rise, the temperature keeps unchanged at evaporating temperature this time, and the phase transition of liquid to gaseous state that only takes place constantly, and liquid refrigerant is less and less, and gaseous refrigerant is more and more, just all becomes gaseous 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 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 shunting of experience in heating comprises the following steps: the temperature difference of the outlets of the branches is within 2 ℃, the superheat degree of the outlets is about 1 ℃, and the shunting is better under the condition.

TABLE 1

TABLE 2

Optionally, when the air conditioner operates in a heating condition, the heat exchanger is used as an evaporator, and the first heat exchange path 200, the second heat exchange path 210, and the third heat exchange path 220 connected in parallel are communicated with the first liquid-dividing branch pipe 620, and the fourth heat exchange path 230 is communicated with the second liquid-dividing branch pipe 621, the refrigerant temperatures at the outlets of the heat exchange branch pipes are as shown in tables 1 and 2. In table 1, when the included angle between the first plane and the second plane is 90 degrees, the maximum temperature difference between the fourth heat exchange path 230 and the first three branches and the heating capacity of the air conditioner are different under the inner diameters of the first branch liquid distribution pipe 620 and the second branch liquid distribution pipe 621. As can be seen from the data in table 1, when the inner diameter of the first branch liquid-dividing pipe 620 is 5.6mm, and the inner diameter of the second branch liquid-dividing pipe 621 is 3.36mm, the maximum temperature difference between the fourth heat exchange path 230 of the heat exchanger and the first three branches is 3.4 ℃, and the heating capacity of the air conditioner is 4855.2W at the maximum inner diameter. Table 2 shows that when the inner diameter of the first branch liquid-separating pipe 620 is 5.6mm and the inner diameter of the second branch liquid-separating pipe 621 is 3.36mm, the included angle between the first plane and the second plane is different, the maximum temperature difference between the fourth heat exchanging channel 230 and the first three branches and the heating capacity of the air conditioner are different. As can be seen from table 2, when the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth heat exchanging path 230 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 620, is 3, the number of the heat exchange branches in the heat exchanger, which are communicated with the second branch liquid pipe 621, is 1, the inner diameter of the first branch liquid pipe 620 is 5.6mm, the inner diameter of the second branch liquid pipe 621 is 3.36mm, and the included angle between the first plane and the second plane is 60 degrees, the maximum temperature difference between the fourth heat exchange path 230 and the first three branches is the smallest, the uniformity of the heat exchange capacity of the refrigerant in each heat exchange branch is the best, and the heating capacity of the air conditioner is the largest. That is, the ratio of the amount of refrigerant in the first branch liquid-dividing pipe 620 to the amount of refrigerant in the second branch liquid-dividing pipe 621 is 3: 1.

In some embodiments, the first flow dividing element 300, the second flow dividing element 310, the third flow dividing element 320, and the fourth flow dividing element 330 are each a refrigerant distributor.

In some embodiments, the heat exchange tubes contained in the first heat exchange path 200, the second heat exchange path 210, the third heat exchange path 220 and the fourth heat exchange path 230 are all copper tubes. The copper pipe has excellent heat-conducting property, so that the refrigerant can better exchange heat with the external environment when circulating inside the heat exchange pipe.

In some embodiments, the first heat exchange path 200 comprises heat exchange tubes provided with heat exchange fins; and/or the heat exchange tube contained in the third heat exchange path 220 is provided with heat exchange fins; and/or the heat exchange tubes included in the fourth heat exchange path 230 are provided with heat exchange fins. Therefore, the heat exchange area of the heat exchange tube can be increased and the heat exchange efficiency of the refrigerant can be improved by arranging the heat exchange fins.

In some embodiments, the heat exchanger further includes a casing 540, a tube plate is disposed in the casing 540, and the heat exchange tubes included in the first heat exchange path 200, the second heat exchange path 210, the third heat exchange path 220, and the fourth heat exchange path 230 are all fixed in the casing 540 through the tube plate.

Optionally, the first heat exchanging path 200, the second heat exchanging path 210, the third heat exchanging path 220, and the fourth heat exchanging path 230 are disposed in the cabinet 540 from top to bottom.

In some embodiments, the height of the first one-way valve 400 and the height of the second one-way valve 410 are the same.

Alternatively, the first check valve 400 and the second check valve 410 are disposed at the left side of the cabinet 540, and the third check valve 420 is disposed at the right side of the cabinet 540.

In some embodiments, the first and third

flow dividing elements

300 and 320 are disposed on one side of the housing 540 and the second and fourth

flow dividing elements

310 and 330 are disposed on the other side of the housing 540.

Alternatively, the first and

third shunt elements

300 and 320 are disposed on the left side of the housing 540, and the second and

fourth shunt elements

310 and 330 are disposed on the right side of the housing 540.

In some embodiments, the height of the first shunt element 300 is greater than the height of the third shunt element 320. In this way, the refrigerant in the heat exchanger flows downwards in the heating direction, and besides the reason that the pressure in the third flow dividing element 320 is lower than the pressure of the first flow dividing element 300, the height of the first flow dividing element 300 is greater than that of the third flow dividing element 320, so the refrigerant in the third flow dividing element 320 cannot flow to the first flow dividing element 300 through the first check valve 400 and the second check valve 410 under the action of gravity.

In some embodiments, the height of the second shunt element 310 is greater than the height of the fourth shunt element 330. In this way, the refrigerant in the heat exchanger flows downward in the heating direction, and besides the reason that the pressure in the fourth flow dividing element 330 is lower than the pressure in the second flow dividing element 310, the height of the second flow dividing element 310 is greater than that of the fourth flow dividing element 330, so that the refrigerant in the fourth flow dividing element 330 cannot flow to the second flow dividing element 310 through the third check valve 420 under the action of gravity.

In some embodiments, the height of the second shunt element 310 and the height of the third shunt element 320 are the same.

In some embodiments, the height of first main pipeline 100 is greater than the height of second main pipeline 110.

Optionally, the first main pipeline 100 is disposed at the left side of the cabinet 540, and the second main pipeline 110 is disposed at the right side of the cabinet 540.

In some embodiments, the first heat exchange path 200 comprises a plurality of heat exchange tubes, and the plurality of heat exchange tubes form a U-shaped refrigerant flow path with an upward opening or a downward opening.

Exemplarily, as shown in fig. 5, the first heat exchange path 200 is a U-shaped refrigerant flow path with an opening facing downward, which is composed of 6 heat exchange tubes, wherein the number of the heat exchange tubes on the left side of the first heat exchange path 200 is 3, and the adjacent heat exchange tubes are communicated through hairpin tubes; the number of the heat exchange tubes on the right side of the first heat exchange passage 200 is 3, and the adjacent heat exchange tubes are communicated through the hairpin tube. The first heat exchange tube at the upper left part of the first heat exchange passage 200 is communicated with the first heat exchange tube at the upper right part of the first heat exchange passage through a hairpin tube, the first heat exchange tube at the lower left part of the first heat exchange passage 200 is communicated with the first flow dividing element 300, and the first heat exchange tube at the lower right part of the first heat exchange passage 200 is communicated with the second flow dividing element 310, so that a U-shaped refrigerant flow path with a downward opening is formed. It should be noted that, the communication mode of the heat exchange tubes on the same side is taken as an example, the front end of the first heat exchange tube on the upper portion of the left side is communicated with the front end of the first heat exchange tube on the upper portion of the right side through the hairpin tube, the rear end of the first heat exchange tube on the upper portion of the left side is communicated with the rear end of the second heat exchange tube on the upper portion of the left side through the hairpin tube, the front end of the second heat exchange tube on the upper portion of the left side is communicated with the front end of the third heat exchange tube on the upper portion of the left side through the hairpin tube, and the heat exchange tubes on the same side form a serpentine structure by analogy in sequence. The heat exchange tubes described below are connected in a similar manner.

In some embodiments, the second heat exchange path 210 includes a plurality of heat exchange tubes, and the plurality of heat exchange tubes form a U-shaped refrigerant flow path with an upward opening or a downward opening.

Exemplarily, as shown in fig. 5, the second heat exchange path 210 is a U-shaped refrigerant flow path with an upward opening formed by 8 heat exchange tubes, wherein the number of the heat exchange tubes on the left side of the second heat exchange path 210 is 4, and the adjacent heat exchange tubes are communicated through hairpin tubes; the number of the heat exchange tubes on the right side of the second heat exchange path 210 is 4, and the adjacent heat exchange tubes are communicated through the hairpin tube. The first heat exchange tube at the lower part of the left side of the second heat exchange path 210 is communicated with the first heat exchange tube at the lower part of the right side of the second heat exchange path 210 through a hairpin tube, the first heat exchange tube at the upper part of the left side of the second heat exchange path 210 is communicated with the first flow dividing element 300, and the first heat exchange tube at the upper part of the right side of the second heat exchange path 210 is communicated with the second flow dividing element 310, thereby forming a U-shaped refrigerant flow path with an upward opening.

In some embodiments, the third heat exchange path 220 comprises a plurality of heat exchange tubes forming a U-shaped refrigerant flow path with an upward opening or a downward opening.

Exemplarily, as shown in fig. 5, the third heat exchange path 220 is a U-shaped refrigerant flow path with an opening facing downward, and 9 heat exchange tubes form the third heat exchange path, where the number of the heat exchange tubes on the left side of the third heat exchange path 220 is 5, and adjacent heat exchange tubes are communicated through hairpin tubes; the number of the heat exchange tubes on the right side of the third heat exchange passage 220 is 4, and the adjacent heat exchange tubes are communicated through the hairpin tube. The first heat exchange tube at the upper left part of the third heat exchange path 220 is communicated with the first heat exchange tube at the upper right part of the third heat exchange path 220 through a hairpin tube, the first heat exchange tube at the lower left part of the third heat exchange path 220 is communicated with the third flow dividing element 320, and the first heat exchange tube at the lower right part of the third heat exchange path 220 is communicated with the second flow dividing element 310, so that a U-shaped refrigerant flow path with an opening facing downwards is formed.

In some embodiments, the fourth heat exchange path 230 includes a plurality of heat exchange tubes, and the plurality of heat exchange tubes form a U-shaped refrigerant flow path with an upward opening or a downward opening.

Exemplarily, as shown in fig. 5, the fourth heat exchange path 230 is a U-shaped refrigerant flow path with an opening facing downward, and the number of the heat exchange tubes on the left side of the fourth heat exchange path 230 is 4, and the adjacent heat exchange tubes are communicated through hairpin tubes; the number of the heat exchange tubes on the right side of the fourth heat exchange path 230 is 5, and the adjacent heat exchange tubes are communicated through the hairpin tube. The first heat exchange tube at the upper left part of the fourth heat exchange path 230 is communicated with the first heat exchange tube at the upper right part of the fourth heat exchange path 230 through a hairpin tube, the first heat exchange tube at the lower left part of the fourth heat exchange path 230 is communicated with the third shunting element 320, and the first heat exchange tube at the lower right part of the fourth heat exchange path 230 is communicated with the fourth shunting element 330, so that a U-shaped refrigerant flow path with a downward opening is formed.

The embodiment of the present disclosure further provides an air conditioner, and the indoor heat exchanger 520 and/or the outdoor heat exchanger 510 are/is the heat exchanger described in any of the above embodiments.

Optionally, the outdoor heat exchanger 510 is the heat exchanger described in any of the above embodiments.

In the cooling mode of the air conditioner, the outdoor heat exchanger 510 serves as a condenser, the first main line 100 of the outdoor heat exchanger 510 is connected to the discharge port of the compressor 500 by a four-way valve, and the second main line 110 of the outdoor heat exchanger 510 is connected to the indoor heat exchanger 520. The refrigerant discharged from the compressor 500 through the discharge port enters the first flow dividing element 300 from the first main line 100, and at this time, the refrigerant in the outdoor heat exchanger 510 flows in the heating flow direction. The first heat exchange path 200 and the second heat exchange path 210 form a fourth parallel path, under the unidirectional conduction action of the first check valve 400, the second check valve 410 and the third check valve 420, the refrigerant in the first flow dividing element 300 can only rapidly enter the fourth flow dividing element 330 through the fourth parallel path, the third heat exchange path 220 and the fourth heat exchange path 230 in sequence, and finally the refrigerant in the fourth flow dividing element 330 enters the indoor heat exchanger 520 through the second main pipe 110. Therefore, the circulation path of the refrigerant in the air conditioner is shortened, and the rapid circulation of the refrigerant is facilitated.

In the heating mode of the air conditioner, the outdoor heat exchanger 510 serves as an evaporator, and the indoor heat exchanger 520 is connected to an exhaust port of the compressor 500 through a four-way valve. At this time, the second main pipe 110 of the outdoor heat exchanger 510 communicates with the indoor heat exchanger 520, and the first main pipe 100 of the outdoor heat exchanger 510 communicates with the suction port of the compressor 500. The refrigerant discharged from the compressor 500 through the discharge port passes through the indoor heat exchanger 520 and enters the second main pipe 110 of the outdoor heat exchanger 510, and the refrigerant enters the fourth diverging element 330 through the second main pipe 110, at this time, the refrigerant in the outdoor heat exchanger 510 circulates in a cooling flow direction. First, the refrigerant in the fourth flow-dividing element 330 is divided into two paths, one path enters the third flow-dividing element 320 through the fourth heat exchange path 230, and the other path enters the second flow-dividing element 310 through the second bypass line 250. Then, the refrigerant in the second flow dividing element 310 is divided into three paths, one path enters the third flow dividing element 320 through the third heat exchanging path 220, the other path enters the first flow dividing element 300 through the first heat exchanging path 200, and the other path enters the first flow dividing element 300 through the second heat exchanging path 210. Then, the refrigerant in the third flow dividing element 320 is divided into two paths, one path enters the first flow dividing element 300 through the first bypass line 240, and the other path enters the first flow dividing element 300 through the second bypass line 250. Finally, the refrigerant in the first flow dividing element 300 enters the suction port of the compressor 500 through the first main pipeline 100. Therefore, the circulation path and the circulation time of the refrigerant in the air conditioner are prolonged, the pressure drop in the air conditioner is reduced, and the performance in the air conditioner is improved. Meanwhile, the third shunting element 320 adopts two bypass lines, namely the first bypass line 240 provided with the first check valve 400 and the second bypass line 250 provided with the second check valve 410, and can effectively shunt the refrigerant compared with the case that the refrigerant is communicated with the first shunting element 300 through one bypass line, so that abnormal sound generated by impact of the valve core of the check valve and other structures caused by impact of the valve core of the refrigerant with larger flow is relieved.

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

1. A heat exchanger, comprising:

a first main pipeline;

a second main pipeline;

a first heat exchange passage, a first end of which is communicated with the first flow dividing element and a second end of which is communicated with the second flow dividing element; and the first shunt element is communicated with the first main pipeline;

a third bypass line, a first end of which is communicated with the second flow dividing element, and a second end of which is communicated with the fourth flow dividing element;

2. The heat exchanger of claim 1, wherein the fourth dividing element comprises:

3. The heat exchanger of claim 2, wherein the first plane is at an angle greater than or equal to 50 degrees and less than or equal to 70 degrees to the second plane.

4. The heat exchanger of claim 3,

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

5. The heat exchanger according to any one of claims 2 to 4, wherein the second tube section is provided offset to the second branch liquid pipe side.

6. The heat exchanger according to any one of claims 1 to 4, wherein the first flow dividing element, the second flow dividing element, the third flow dividing element and the fourth flow dividing element are each a refrigerant distributor.

7. The heat exchanger according to any one of claims 1 to 4, wherein the first heat exchange passage, the second heat exchange passage, the third heat exchange passage and the fourth heat exchange passage respectively comprise heat exchange tubes which are all copper tubes.

8. The heat exchanger of any one of claims 1 to 4, further comprising:

9. An air conditioner comprising a refrigerant circulation circuit constructed by at least 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 is the heat exchanger as recited in any one of claims 1 to 8.

10. The air conditioner according to claim 9, wherein the outdoor heat exchanger is the heat exchanger;