EP4656973A1

EP4656973A1 - Air conditioner

Info

Publication number: EP4656973A1
Application number: EP24880957.6A
Authority: EP
Inventors: Yufeng Tan; Qi Chen; Gengui LV; Di Ma; Hongxia WU; Gang Yan
Original assignee: Xian Jiaotong University; Hisense Guangdong Air Conditioning Co Ltd
Current assignee: Xian Jiaotong University; Hisense Guangdong Air Conditioning Co Ltd
Priority date: 2023-10-27
Filing date: 2024-04-24
Publication date: 2025-12-03
Also published as: WO2025086578A1

Abstract

An air conditioner (1000), wherein a compressor (201), a heat exchanger, a throttling assembly and a flow division assembly (500) are connected to form a refrigerant loop. The flow division assembly (500) comprises a first pipeline (510), a plurality of second pipelines (520) and a flow division member (530). A first end of the first pipeline (510) is connected to the compressor (201), and a second end of the first pipeline is connected to a first end of the flow division member (530). First ends of the plurality of second pipelines (520) are connected to the heat exchanger, and second ends of the plurality of second pipelines are connected to a second end of the flow division member (530). The flow division member (530) comprises different numbers of flow division channels, the flow division channels being in communication with the first pipeline (510) and the plurality of second pipelines (520). The flow division member (530) is configured to switch between different numbers of flow division channels, on the basis of the flow direction of the refrigerant and at least one of the workloads of the heat exchanger.

Description

The present application claims priority to Chinese Patent Application No. 202322911190.X, filed on October 27, 2023 , Chinese Patent Application No. 202322911319.7, filed on October 27, 2023 , and Chinese Patent Application No. 202311416348.4, filed on October 27, 2023 . The entire disclosures of the above-identified applications are hereby incorporated herein by reference.

TECHNICAL FIELD

The present disclosure relates to the technical field of air conditioning, in particular to an air conditioner.

BACKGROUND

With the development of science and technology and the improvement of people's living standards, air conditioners have become one of the commonly used household appliances. A refrigeration cycle or heating cycle of the air conditioner is executed by means of a compressor, a condenser, a throttling assembly, and an evaporator.

SUMMARY

An air conditioner is provided. The air conditioner includes a compressor, a heat exchanger, a throttling assembly, and a flow dividing assembly. The compressor is configured to compress a refrigerant. The heat exchanger is configured to exchange heat with the refrigerant. The throttling assembly is configured to adjust a flow rate of the refrigerant. The compressor, the heat exchanger and the throttling assembly are connected to form a refrigerant loop. The flow dividing assembly includes a first pipeline, a plurality of second pipelines, and a flow dividing member. A first end of the first pipeline is connected to the compressor. First ends of the plurality of second pipelines are connected to the heat exchanger. A first end of the flow dividing member is connected to a second end of the first pipeline, and a second end of the flow dividing member is connected to second ends of the plurality of second pipelines. The flow dividing member includes different numbers of flow dividing passages, and the flow dividing passages communicate the first pipeline with the plurality of second pipelines. The flow dividing member is configured to switch among the different numbers of flow dividing passages on the basis of at least one of a flow direction of the refrigerant and a working load of the heat exchanger, so as to change the number of the flow dividing passages in communication with the heat exchanger.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a structural diagram of an air conditioner according to some embodiments;
FIG. 2 is a schematic diagram of a refrigerant flow direction between a flow dividing assembly and a heat exchanger according to some embodiments;
FIG. 3 is a schematic diagram of another refrigerant flow direction between the flow dividing assembly and the heat exchanger according to some embodiments;
FIG. 4 is a structural diagram of a flow dividing member according to some embodiments;
FIG. 5 is a sectional view of the flow dividing member according to some embodiments;
FIG. 6 is another structural diagram of the flow dividing member according to some embodiments;
FIG. 7 is a side view of the flow dividing member according to some embodiments;
FIG. 8 is a structural diagram of a baffle according to some embodiments;
FIG. 9 is a side view of the baffle according to some embodiments;
FIG. 10 is a structural diagram of a first unidirectional passage and a first opening and closing assembly according to some embodiments;
FIG. 11 is a structural diagram of a second unidirectional passage and a second opening and closing assembly according to some embodiments;
FIG. 12 is a structural diagram of another flow dividing member according to some embodiments;
FIG. 13 is a partial enlarged view at circle A in FIG. 12;
FIG. 14A is a schematic diagram of a refrigerant flow direction between another flow dividing assembly and the heat exchanger according to some embodiments;
FIG. 14B is a schematic diagram of another refrigerant flow direction between another flow dividing assembly and the heat exchanger according to some embodiments;
FIG. 14C is a schematic diagram of yet another refrigerant flow direction between another flow dividing assembly and the heat exchanger according to some embodiments;
FIG. 15 is a structural diagram of a first flow guide pipe according to some embodiments;
FIG. 16 is a sectional view of the first flow guide pipe according to some embodiments;
FIG. 17 is a front view of the first flow guide pipe according to some embodiments;
FIG. 18 is a structural diagram of a second flow guide pipe according to some embodiments;
FIG. 19 is a sectional view of the second flow guide pipe according to some embodiments;
FIG. 20 is a front view of the second flow guide pipe according to some embodiments; and
FIG. 21 is a structural diagram of a heat exchanger according to some embodiments.

Reference numerals:

air conditioner 1000;
indoor unit 100; first heat exchanger 101; first fan 102;
outdoor unit 200; compressor 201; four-way valve 202; second heat exchanger 203; expansion
valve 204; second fan 205;
controller 300;
heat exchanger 400; fin 410; heat exchange tube 420; connecting pipe 430; supercooling pipe 440; first supercooling sub-pipe 4401; second supercooling sub-pipe 4402; third supercooling sub-pipe 4403;
flow dividing assembly 500; first pipeline 510; second pipeline 520; flow dividing member 530; flow dividing body 536; first sub-body 531; second sub-body 532; transition portion 533; flow guide passage 534; flow guide portion 535;
first passage 501; second passage 502; first unidirectional passage 503; second unidirectional passage 504; first opening and closing assembly 505; second opening and closing assembly 506; rotating shaft 507; baffle 508; limiting portion 509; first sub-baffle 5081; second sub-baffle 5082; first hinge portion 5083; second hinge portion 5084;
first flow guide pipe 601; first body 6011; first flow guide hole 6012; first sub-flow guide hole 6013; second sub-flow guide hole 6014; second flow guide pipe 602; second body 6021; second flow guide hole 6022; blocking portion 6023; connecting portion 6024; driver 700; signal device 800.

DETAILED DESCRIPTION OF THE EMBODIMENTS

Some embodiments of the present disclosure will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are only a part of embodiments of the present disclosure, not all of them. Based on the embodiments provided by the present disclosure, all other embodiments obtained by those ordinarily skilled in the art fall within the scope of protection of the present disclosure.
Unless otherwise specified in the context, throughout the description and the claims, the term "comprise" and other forms thereof, such as the third-person singular form "comprises" and the present participle form "comprising" are construed in an open and inclusive meaning, that is, "comprising, but not limited to". In the description, the term such as "one embodiment", "some embodiments", "exemplary embodiments", "example", "specific example", or "some examples" are intended to indicate that specific features, structures, materials, or characteristics related to the embodiment or example are included in at least one embodiment or example of the present disclosure. The illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics may be included in any appropriate manner in any one or more embodiments or examples.
Hereinafter, the terms "first" and "second" are only for the purpose of describing, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of technical features indicated. Thus, the features defined as "first" and "second" may explicitly or implicitly include one or more such features. In the description of some embodiments of the present disclosure, unless otherwise specified, "a plurality of" means two or more.
When describing some embodiments, the term "connected" and its derivatives may be used. The term "connected" should be understood in a broad sense, for example, the term "connected" may refer to fixed connection, and may also refer to detachable connection or integrated connection; and the term may refer to direct connection, and may also refer to indirect connection by means of an intermediate medium. The embodiments disclosed herein are not necessarily limited to the content of this disclosure.
The expression "at least one of A, B, and C" has the same meaning as the expression "at least one of A, B, or C", and both include the following combinations of A, B, and C: only A, only B, only C, a combination of A and B, a combination of A and C, a combination of B and C, and a combination of A, B, and C.
The use of the expression "suitable to" or "configured to" herein means open and inclusive language, which does not exclude apparatuses suitable to or configured to perform additional tasks or steps.
As used herein, the term "about", "roughly", or "approximately" includes a stated value as well as an average value within an acceptable deviation range of a specified value, where the acceptable deviation range is, for example, determined by those of ordinary skill in the art in view of a measurement under discussion and errors related to the measurement of the specific value (that is, the limitation of a measurement system).
As used herein, the terms "parallel", "perpendicular" and or "equal" include stated conditions as well as conditions similar to the stated conditions, where the similar conditions are within an acceptable deviation range, and the acceptable deviation range is, for example, determined by those of ordinary skill in the art in view of the measurement under discussion and errors related to the measurement of the specific value (that is, the limitation of the measurement system).
A heat exchanger in an air conditioner is usually connected to a flow dividing assembly, and a flow dividing member of the flow dividing assembly may divide a refrigerant. However, the number of flow dividing passages inside the flow dividing member is unchanged. As the state and working load of the heat exchanger change, the number of the flow dividing passages required by the highest heat exchange performance of the heat exchanger also changes. Under such circumstances, the constant flow dividing structure cannot match different working modes of the air conditioner. In the different working modes, especially after switching between a refrigeration mode and a heating mode, the number of the flow dividing passages of the flow dividing member cannot meet the requirement, and the heat exchanger cannot reach the highest heat exchange performance (such as the energy efficiency ratio), thereby affecting the working efficiency of the air conditioner.
In some solutions, the air conditioner includes a plurality of flow dividing assemblies, and the plurality of flow dividing assemblies have different numbers of flow dividing passages, so that the air conditioner can use different numbers of flow dividing passages in the different working modes. However, the plurality of flow dividing assemblies increase the number of pipelines inside the air conditioner, so that the pipelines are complex, the miniaturization of the air conditioner is hindered, and the cost of the air conditioner is increased.
In order to solve the above problems, some embodiments of the present disclosure provide an air conditioner 1000. In the air conditioner 1000, a flow dividing member may switch different numbers of flow dividing passages in different working modes of the air conditioner 1000, thereby improving the heat exchange performance of a heat exchanger, and then improving the working efficiency of the air conditioner 1000.
As shown in FIG. 1, the air conditioner 1000 includes an indoor unit 100.
The indoor unit 100 includes a first heat exchanger 101 (an indoor heat exchanger). The first heat exchanger 101 is configured to perform heat exchange between the indoor air and a refrigerant transferred in the first heat exchanger 101. For example, the first heat exchanger 101 works as an evaporator in a refrigeration mode of the air conditioner 1000, and works as a condenser in a heating mode of the air conditioner 1000.
The indoor unit 100 further includes a first fan 102 (an indoor fan). The first fan 102 is arranged inside a housing of the indoor unit 100, and is configured to suck the indoor air into the indoor unit 100 through an indoor air inlet of the indoor unit 100, and send out the indoor air exchanging heat with the first heat exchanger 101 through an indoor air outlet of the indoor unit 100.
The air conditioner 1000 further includes an outdoor unit 200. The indoor unit 100 and the outdoor unit 200 are connected by means of a pipeline to transfer the refrigerant.
The outdoor unit 200 includes a compressor 201, and the compressor 201 is configured to compress the refrigerant such that a low-pressure refrigerant is compressed to form a high-pressure refrigerant.
The outdoor unit 200 further includes a four-way valve 202. The four-way valve 202 is arranged inside a refrigerant loop, and is configured to switch the flow direction of the refrigerant in the refrigerant loop to implement the refrigeration mode or the heating mode of the air conditioner 1000.
The outdoor unit 200 further includes a second heat exchanger 203 (an outdoor heat exchanger). The second heat exchanger 203 is configured to perform heat exchange between the outdoor air and a refrigerant transferred in the second heat exchanger 203. For example, the second heat exchanger 203 works as a condenser in the refrigeration mode of the air conditioner 1000, and works as an evaporator in the heating mode of the air conditioner 1000. To facilitate describing, the first heat exchanger 101 or the second heat exchanger 203 may also be referred to as a heat exchanger 400. In some embodiments, the heat exchanger 400 may be a finned tube heat exchanger.
The outdoor unit 200 further includes an expansion valve 204 (a throttling assembly), and the expansion valve 204 is connected between the first heat exchanger 101 and the second heat exchanger 203. The pressure of the refrigerant flowing through the first heat exchanger 101 and the second heat exchanger 203 is adjusted by means of the opening degree of the expansion valve 204, thereby adjusting the flow rate of the refrigerant flowing between the first heat exchanger 101 and the second heat exchanger 203. It should be noted that the compressor 201, the second heat exchanger 203, the expansion valve 204, and the first heat exchanger 101 are sequentially connected to form the refrigerant loop.
The outdoor unit 200 further includes a second fan 205 (an outdoor fan). The second fan 205 is configured to suck the outdoor air into the outdoor unit 200 through an outdoor air inlet of the outdoor unit 200, and send out the outdoor air exchanging heat with the second heat exchanger 203 through an outdoor air outlet of the outdoor unit 200.
In some embodiments, the air conditioner 1000 includes one or more indoor units 100. Thus, the various requirements of a user can be met.
In some embodiments, as shown in FIG. 1, the air conditioner 1000 further includes a controller 300, and the controller 300 is configured to control operation of components inside the air conditioner 1000. The controller 300 may be a central processing unit (CPU), a general-purpose processor, a network processor (NP), a digital signal processor (DSP), a microprocessor, a microcontroller, a programmable logic device (PLD), or any combination thereof. The controller 300 may also be other device having a processing function, for example, a circuit, a device, or a software module.
A flow dividing assembly in some embodiments of the present disclosure is introduced below.
In some embodiments, as shown in FIG. 2 and FIG. 3, the air conditioner 1000 further includes a flow dividing assembly 500 (a distributing unit). The flow dividing assembly 500 is connected to the heat exchanger 400 (for example, the first heat exchanger 101 or the second heat exchanger 203) and the compressor 201. The flow dividing assembly 500 is configured to divide or gather the refrigerant flowing in.
In some embodiments, as shown in FIG. 2 and FIG. 3, the flow dividing assembly 500 includes a first pipeline 510 (a main pipeline). A first end of the first pipeline 510 is connected to the compressor 201.
The flow dividing assembly 500 further includes a plurality of second pipelines 520 (flow dividing pipelines). First ends of the plurality of second pipelines 520 are connected to the heat exchanger 400.
The flow dividing assembly 500 further includes a flow dividing member 530 (a distributor). A first end of the flow dividing member 530 is connected to a second end of the first pipeline 510, and a second end of the flow dividing member 530 is connected to second ends of the plurality of second pipelines 520.
In some embodiments, as shown in FIG. 4, the flow dividing member 530 includes a flow dividing body 536. The flow dividing body 536 may include a plurality of sub-bodies. For example, as shown in FIG. 4 to FIG. 6, the flow dividing body 536 includes a first sub-body 531 (a main joint portion) and a second sub-body 532 (a sub-joint portion). The first sub-body 531 and the second sub-body 532 are cylindrical, respectively. The refrigerant may flow unidirectionally between the first sub-body 531 and the second sub-body 532, thereby reducing the flow resistance of the refrigerant, and reducing the influence on the flow rate of the refrigerant.
In some embodiments, as shown in FIG. 4, the flow dividing member 530 further includes a first passage 501 (a main passage). The first passage 501 is arranged inside the flow dividing body 536, and a second end of the first pipeline is in communication with the first passage 501. For example, the first passage 501 is arranged inside the first sub-body 531.
In some embodiments, as shown in FIG. 4, the flow dividing member 530 further includes a plurality of second passages 502 (sub-passages). The plurality of second passages 502 are arranged inside the flow dividing body 536, and second ends of the plurality of second pipelines 520 are in communication with the plurality of second passages 502 respectively. For example, the second passages 502 are arranged inside the second sub-body 532.
In some embodiments, the diameter of the second sub-body 532 is greater than the diameter of the first sub-body 531. For example, cross sections of the first sub-body 531 and the second sub-body 532 are respectively in shapes of circles with different diameters. Thus, the flow directions of the refrigerants between the first passage 501 and the second passages 502 may be matched, the plurality of second passages 502 can be arranged inside the second sub-body 532, and the construction of the integrated flow dividing member 530 is facilitated.
By simplifying the structure of the flow dividing member 530, the connection between the first sub-body 531 and the compressor 201 can be achieved through the first pipeline 510, and the connection between the second sub-body 532 and the heat exchanger 400 can be achieved through the plurality of second pipelines 520.
In some embodiments, as shown in FIG. 5, the flow dividing body 536 further includes a transition portion 533. The transition portion 533 is arranged on one side of the second sub-body 532 close to the first sub-body 531, and is connected to the second sub-body 532 and the first sub-body 531. The diameter of the transition portion 533 decreases in a direction close to the first sub-body 531.
Under such circumstances, the flow dividing body 536 further includes a flow guide passage 534, and the flow guide passage 534 is arranged inside the transition portion 533 and is in communication with the first passage 501 and the plurality of second passages 502.
As shown in FIG. 5, the flow dividing body 536 further includes a flow guide portion 535. The flow guide portion 535 is configured to guide the refrigerant flowing through, so as to reduce the resistance of the refrigerant when flowing between the first passage 501 and the second passages 502. The flow guide portion 535 is arranged at the center of the transition portion 533. The flow guide portion 535 is in a shape of a cone, and a vertex of the cone faces the first passage 501. The flow guide passage 534 surrounds the flow guide portion 535.
Thus, by arranging the transition portion 533, the flow guide passage 534, and the flow guide portion 535, the refrigerant can flow inside the flow guide passage 534 along the flow guide portion 535, thereby reducing the resistance of the refrigerant when flowing between the first passage 501 and the second passages 502.
In some embodiments, as shown in FIG. 7, under such circumstance that the flow dividing body 536 has a circular cross section, the plurality of second passages 502 are arranged at intervals in a circumferential direction of the flow dividing body 536. The plurality of second passages 502 may be circular holes with equal diameters, so that the flow rates of the refrigerant flowing into the different second passages 502 are the same, and the flow dividing uniformity of the refrigerant is improved.
The first passage 501 is located at a central axis of the flow dividing body 536. On a plane perpendicular to the central axis of the flow dividing body 536, orthographic projections of the plurality of second passages 502 surround an orthographic projection of the first passage 501. Thus, by arranging the plurality of second passages 502 at intervals in the circumferential direction of the flow dividing body 536, the refrigerant can flow in the circumferential direction of the flow dividing body 536, thereby forming an annular flow inside the flow dividing member 530, and then improving the flow dividing uniformity of the refrigerant.
In some embodiments, as shown in FIG. 4 and FIG. 6, the plurality of second passages 502 include first unidirectional passages 503. The first unidirectional passages 503 are configured to be opened when the refrigerant flows from the first pipeline 510 to the plurality of second pipelines 520 and be closed when the refrigerant flows from the plurality of second pipelines 520 to the first pipeline 510. Thus, under the circumstance that the heat exchanger 400 serves as the condenser, the refrigerant flows from the first passage 501 to the first unidirectional passages 503.
The plurality of second passages 502 further include second unidirectional passages 504. The second unidirectional passages 504 are configured to be closed when the refrigerant flows from the first pipeline 510 to the plurality of second pipelines 520 and be opened when the refrigerant flows from the plurality of second pipelines 520 to the first pipeline 510. Thus, under the circumstance that the heat exchanger 400 serves as the evaporator, the refrigerant flows from the second unidirectional passages 504 to the first passage 501.
Extension directions of the first unidirectional passages 503 and the second unidirectional passages 504 may be parallel to each other, and the flow direction of the refrigerant inside the first unidirectional passages 503 is opposite to the flow direction of the refrigerant inside the second unidirectional passages 504. For example, the first unidirectional passages 503 and the second unidirectional passages 504 extend in an axial direction of the flow dividing body 536 respectively.
In some embodiments, as shown in FIG. 4 and FIG. 6, the plurality of second passages 502 further include first opening and closing assemblies 505. The first opening and closing assemblies 505 are arranged inside the first unidirectional passages 503 and configured to be opened when the refrigerant flows from the first pipeline 510 to the plurality of second pipelines 520, so as to enable the refrigerant to enter the plurality of second pipelines 520 through the first unidirectional passages 503.
The plurality of second passages 502 further include second opening and closing assemblies 506. The second opening and closing assemblies 506 are arranged inside the second unidirectional passages 504 and configured to be opened when the refrigerant flows from the plurality of second pipelines 520 to the first pipeline 510, so as to enable the refrigerant to enter the first pipeline 510 through the second unidirectional passages 504.
In some embodiments, the number of the first unidirectional passages 503 is less than the number of the second unidirectional passages 504.
The number of the flow dividing passages corresponding to the flow rate of the refrigerant and the highest heat exchange performance of the heat exchanger 400 when the heat exchanger 400 serves as the condenser is different from that of the flow dividing passages corresponding to the flow rate of the refrigerant and the highest heat exchange performance of the heat exchanger 400 when the heat exchanger 400 serves as the evaporator. For example, a first number of the flow dividing passages connected to the heat exchanger 400 when the heat exchanger 400 serves as the condenser is less than a second number of the flow dividing passages connected to the heat exchanger 400 when the heat exchanger 400 serves as the evaporator. That is, the number of the first unidirectional passages 503 is less than the number of the second unidirectional passages 504.
Here, the first number may be understood as the number of the flow dividing passages required by the highest heat exchange performance of the heat exchanger 400 when the heat exchanger 400 serves as the condenser; and the second number may be understood as the number of the flow dividing passages required by the highest heat exchange performance of the heat exchanger 400 when the heat exchanger 400 serves as the evaporator.
For example, a ratio of the number of the first unidirectional passages 503 to the number of the second unidirectional passages 504 is 2 : 3. It can be understood that the ratio of the number of the first unidirectional passages 503 to the number of the second unidirectional passages 504 may also be 1 : 3, 1 : 2, 3 : 5, 3 : 4, or other ratios. The ratio of the number of the first unidirectional passages 503 to the number of the second unidirectional passages 504 being 2 : 3 is taken as an example, when the ratio of the number of the first unidirectional passages 503 to the number of the second unidirectional passages 504 is less than 2 : 3, the number of the first unidirectional passages 503 is too small, and the difference between the number of the first unidirectional passages 503 and the number of the second unidirectional passages 504 is too large, so that the heating effect when the heat exchanger 400 serves as the condenser is reduced, and the utilization rate of heat exchange tubes inside the heat exchanger 400 is reduced; and when the ratio of the number of the first unidirectional passages 503 to the number of the second unidirectional passages 504 is greater than 2 : 3, the number of the first unidirectional passages 503 is too large, and the number of the flow dividing passages required by the highest heat exchange performance when the heat exchanger 400 serves as the condenser is small, so that the energy efficiency ratio of the heat exchanger 400 is reduced.
Thus, by setting the ratio of the number of the first unidirectional passages 503 to the number of the second unidirectional passages 504 to be 2 : 3, the heat exchange efficiency of the heat exchanger 400 can be improved under the circumstance of increasing the energy efficiency ratio of the heat exchanger 400.
In some embodiments, as shown in FIG. 7, for example, the cross section of the flow dividing body 536 is divided into two semicircles through a center line L, in the semicircles of the cross section of the flow dividing body 536, the first unidirectional passages 503 and the second unidirectional passages 504 are alternately arranged in the circumferential direction of the flow dividing body 536 (for example, a circumferential direction of the second sub-body 532). The first unidirectional passages 503 in the first semicircle and the second semicircle of the cross section of the flow dividing body 536 are symmetric to each other, and the second unidirectional passages 504 in the semicircles are also symmetric to each other. That is, the first unidirectional passages 503 may be symmetric about the center line L, and the second unidirectional passages 504 may be symmetric about the center line L.
Besides, the number of the second unidirectional passages 504 is greater than the number of the first unidirectional passages 503, so that in the first semicircle of the cross section of the flow dividing body 536, in the circumferential direction of the flow dividing body 536, each first unidirectional passage 503 is located between two adjacent second unidirectional passages 504. For example, in the first semicircle of the cross section of the flow dividing body 536, three second unidirectional passages 504 and two first unidirectional passages 503 are arranged.
Similarly, in the second semicircle of the cross section of the flow dividing body 536, in the circumferential direction of the flow dividing body 536, each first unidirectional passage 503 is located between two adjacent second unidirectional passages 504. For example, in the second semicircle of the cross section of the flow dividing body 536, three second unidirectional passages 504 and two first unidirectional passages 503 are arranged.
Thus, by means of the symmetric first unidirectional passages 503 and the symmetric second unidirectional passages 504, the flow dividing uniformity of the refrigerant can be improved. Besides, the first unidirectional passages 503 and the second unidirectional passages 504 serve as a part of the flow dividing member 530, so that the refrigerant flow dividing structure of the flow dividing member 530 is compact, and the space occupied by the flow dividing member 530 can be reduced. The first opening and closing assemblies 505 and the second opening and closing assemblies 506 in some embodiments of the present disclosure are introduced below.
In some embodiments, the first opening and closing assemblies 505 and the second opening and closing assemblies 506 can be controlled to be opened and closed. In some examples, the first opening and closing assemblies 505 and the second opening and closing assemblies 506 are controlled to be opened and closed by means of driving components on the basis of operating parameters of the air conditioner 1000. For example, the first opening and closing assemblies 505 and the second opening and closing assemblies 506 may be solenoid valves, pneumatic control valves, electric valves, etc.
Here, the operating parameters of the air conditioner 1000 may include refrigerant flow directions, refrigerant pressure, refrigerant temperatures, indoor ambient temperatures, outdoor ambient temperatures, etc. Thus, the accuracy in selection of the number of the flow dividing passages can be improved, thereby improving the heat exchange effect of the air conditioner 1000.
Alternatively, the first opening and closing assemblies 505 and the second opening and closing assemblies 506 may be automatically opened and closed by means of the pressure of the refrigerant during the flow process of the refrigerant, thereby controlling the first unidirectional passages 503 and the second unidirectional passages 504 to be opened and closed. Under such circumstances, the first opening and closing assemblies 505 can open the first unidirectional passages 503 when the refrigerant flows from the first pipeline 510 to the plurality of second pipelines 520 and close the first unidirectional passages 503 when the refrigerant flows from the plurality of second pipelines 520 to the first pipeline 510. The second opening and closing assemblies 506 can open the second unidirectional passages 504 when the refrigerant flows from the plurality of second pipelines 520 to the first pipeline 510 and close the second unidirectional passages 504 when the refrigerant flows from the first pipeline 510 to the plurality of second pipelines 520. Thus, the first opening and closing assemblies 505 and the second opening and closing assemblies 506 can achieve the effects of unidirectional flowing and reverse cutting-off.
Thus, no additional driving component is needed, the structure of the flow dividing member 530 can be simplified, and the cost can be reduced.
Besides, by means of the first opening and closing assemblies 505 and the second opening and closing assemblies 506, flow paths with opposite flow directions can be formed inside the first unidirectional passages 503 and the second unidirectional passages 504. When the air conditioner 1000 is in the refrigeration mode or the heating mode, the plurality of heat exchangers 400 respectively serve as condensers and evaporators, the flow direction of the refrigerant in the flow dividing members 530 corresponding to the condensers is opposite to the flow direction of the refrigerant in the flow dividing members 530 corresponding to the evaporators, and the refrigerants flow unidirectionally inside the first unidirectional passages 503 and the second unidirectional passages 504.
Thus, the heat exchangers 400 in different states may have different numbers of flow dividing passages, thereby improving the heat exchange performance of the heat exchangers 400 when the air conditioner 1000 is in different modes.
It should be noted that the first opening and closing assemblies 505 and the second opening and closing assemblies 506 are of similar structures. To facilitate describing, the first opening and closing assemblies 505 are mainly introduced below.
In some embodiments, as shown in FIG. 8 and FIG. 9, each first opening and closing assembly 505 includes a rotating shaft 507. Two ends of the rotating shaft 507 are arranged on an inner wall surface of the first unidirectional passage 503, and the rotating shaft 507 extends in a radial direction of the first unidirectional passage 503. For example, a plurality of mounting grooves are formed in inner wall surfaces of the first unidirectional passages 503 and inner wall surfaces of the second unidirectional passages 504, respectively. The two ends of the rotating shaft 507 are respectively mounted inside the plurality of mounting grooves.
In each second opening and closing assembly 506, two ends of the rotating shaft 507 are arranged on the inner wall surface of the second unidirectional passage 504, and the rotating shaft 507 extends in a radial direction of the second unidirectional passage 504.
Each first opening and closing assembly 505 further includes a baffle 508. The baffle 508 is rotationally connected to the rotating shaft 507 and configured to open and close the first unidirectional passage 503.
The baffle 508 may be an integral part, so as to rotate as a whole relative to the rotating shaft 507. Thus, the number of assembly components can be reduced, the assembly efficiency can be improved, and the closing effect of the baffle 508 can be improved. Alternatively, the baffle 508 may also be split parts, so as to respectively rotate relative to the rotating shaft 507. Thus, production and mounting of the baffle 508 are facilitated.
The baffle 508 being split parts is mainly taken as an example below for explanation.
It can be understood that the shape of the baffle 508 inside the first unidirectional passage 503 is identical with the inner contour of the first unidirectional passage 503, and the shape of the baffle 508 inside the second unidirectional passage 504 is identical with the inner contour of the second unidirectional passage 504. Thus, the contact reliability of the baffle 508 with the first unidirectional passage 503 or the second unidirectional passage 504 can be improved, thereby reducing the probability of leakage of the refrigerant when the first opening and closing assembly 505 and the second opening and closing assembly 506 are closed.
As shown in FIG. 10 and FIG. 11, the first opening and closing assembly 505 further includes limiting portions 509 (limiting blocks). The limiting portions 509 are arranged on the inner wall surface of the first unidirectional passage 503 and protrude from the inner wall surface. The limiting portions 509 inside the first unidirectional passage 503 are located on one side of the baffle 508 close to the first passage 501 and abut against the baffle 508, so as to limit a rotating direction of the baffle 508 inside the first unidirectional passage 503.
The limiting portions 509 of the second opening and closing assembly 506 are arranged on the inner wall surface of the second unidirectional passage 504 and protrude from the inner wall surface. The limiting portions 509 inside the second unidirectional passage 504 are located on one side of the baffle 508 away from the first passage 501 and abut against the baffle 508, so as to limit a rotating direction of the baffle 508 inside the second unidirectional passage 504.
Thus, by arranging the limiting portions 509, the rotating directions of the baffles 508 inside the first opening and closing assembly 505 and the second opening and closing assembly 506 may be opposite, so that the baffle 508 inside the first unidirectional passage 503 rotates in a direction away from the first passage 501 so as to open the first unidirectional passage 503, and the baffle 508 inside the second unidirectional passage 504 rotates in a direction close to the first passage 501 so as to open the second unidirectional passage 504. Thus, the refrigerant may flow unidirectionally in different passages.
When the baffle 508 inside the first unidirectional passage 503 is blocked by the limiting portions 509, the baffle 508 rotates to the position perpendicular to the central axis of the first unidirectional passage 503, thereby closing the first unidirectional passage 503. When the baffle 508 inside the second unidirectional passage 504 is blocked by the limiting portions 509, the baffle 508 rotates to the position perpendicular to the central axis of the second unidirectional passage 504, thereby closing the second unidirectional passage 504. Thus, the refrigerant may be prevented from flowing reversely in the unidirectional passages.
When the refrigerant flows from the first pipeline 510 to the plurality of second pipelines 520, the refrigerant flows from the first passage 501 to the plurality of second passages 502. At this time, the refrigerant enters the first unidirectional passages 503 and the second unidirectional passages 504, respectively. In the first unidirectional passages 503, the refrigerant pushes the baffles 508 by means of the pressure of the refrigerant, so that the baffles 508 rotate in a direction away from the limiting portions 509 (for example, the direction away from the first passage 501), and the refrigerant can pass through the first unidirectional passages 503. In the second unidirectional passages 504, the sides of the baffles 508 away from the first pipeline 510 are blocked by the limiting portions 509, so that the baffles 508 cannot rotate, and the refrigerant is cut off inside the second unidirectional passages 504.
When the refrigerant flows from the plurality of second pipelines 520 to the first pipeline 510, the refrigerant flows from the plurality of second passages 502 to the first passage 501. At this time, the refrigerant enters the first unidirectional passages 503 and the second unidirectional passages 504, respectively. In the second unidirectional passages 504, the refrigerant pushes the baffles 508 by means of the pressure of the refrigerant, so that the baffles 508 rotate in a direction away from the limiting portions 509 (for example, the direction close to the first passage 501), and the refrigerant can pass through the second unidirectional passages 504. In the first unidirectional passages 503, the sides of the baffles 508 close to the first pipeline 510 are blocked by the limiting portions 509, so that the baffles 508 cannot rotate, and the refrigerant is cut off inside the first unidirectional passages 503.
In some embodiments, as shown in FIG. 8 and FIG. 9, the baffle 508 includes a first sub-baffle 5081. The first sub-baffle 5081 is located on one side of the rotating shaft 507 in a radial direction.
The baffle 508 further includes a second sub-baffle 5082. The second sub-baffle 5082 is located on the other side of the rotating shaft 507 in the radial direction, so that the second sub-baffle 5082 and the first sub-baffle 5081 are arranged opposite to each other.
The baffle 508 further includes a first hinge portion 5083. The first hinge portion 5083 is arranged at one end of the first sub-baffle 5081 close to the rotating shaft 507 and rotationally sleeved on an outer side of the rotating shaft 507.
The baffle 508 further includes a second hinge portion 5084. The second hinge portion 5084 is arranged at one end of the second sub-baffle 5082 close to the rotating shaft 507 and rotationally sleeved on an outer side of the rotating shaft 507.
Thus, by means of the first hinge portion 5083 and the second hinge portion 5084, the baffle 508 can stably rotate around the rotating shaft 507. For example, the first sub-baffle 5081 and the second sub-baffle 5082 are symmetrically mounted on two sides of the rotating shaft 507, the inner contour of the first unidirectional passage 503 is identical with the shapes of the first sub-baffle 5081 and the second sub-baffle 5082 therein, and the inner contour of the second unidirectional passage 504 is identical with the shapes of the first sub-baffle 5081 and the second sub-baffle 5082 therein. The first sub-baffle 5081 and the second sub-baffle 5082 rotate towards the same side of the baffle 508 in an axial direction of the second passage 502, so as to open the first unidirectional passage 503 and the second unidirectional passage 504 respectively.
It can be understood that the first sub-baffle 5081 or the second sub-baffle 5082 cannot rotate towards the side of the baffle 508 close to the limiting portion 509 due to the fact that it is blocked by the limiting portion 509.
In some embodiments, as shown in FIG. 8, the first hinge portions 5083 and the second hinge portions 5084 are arranged in the axial direction of the rotating shaft 507, and the baffle 508 may include a plurality of first hinge portions 5083 and a plurality of second hinge portions 5084.
It can be understood that during the rotation process of the first sub-baffle 5081 and the second sub-baffle 5082, an included angle between the first sub-baffle 5081 and the second sub-baffle may be any value in the range of 0-180°. For example, the included angle between the first sub-baffle 5081 and the second sub-baffle is 0°, 30°, 60°, 90°, 120°, 150°, or 180°.
When the first unidirectional passage 503 or the second unidirectional passage 504 is opened, the first sub-baffle 5081 rotates in a direction close to the second sub-baffle 5082, and the second sub-baffle 5082 rotates in a direction close to the first sub-baffle 5081, so that the first sub-baffle 5081 and the second sub-baffle 5082 can be attached to each other. At this time, the included angle between the first sub-baffle 5081 and the second sub-baffle 5082 is 0°. When the first sub-baffle 5081 and the second sub-baffle 5082 are opened, as the included angle between the first sub-baffle 5081 and the second sub-baffle 5082 decreases, the resistance of the first opening and closing assembly 505 and the second opening and closing assembly 506 on the refrigerant decreases, and the flow rate of the refrigerant increases.
When the first unidirectional passage 503 or the second unidirectional passage 504 is closed, the first sub-baffle 5081 rotates in a direction away from the second sub-baffle 5082 until it is blocked by the limiting portion 509, and the second sub-baffle 5082 rotates in a direction away from the first sub-baffle 5081 until it is blocked by the limiting portion 509. At this time, the included angle between the first sub-baffle 5081 and the second sub-baffle 5082 is 180°, and the first sub-baffle 5081 and the second sub-baffle 5082 are located on the same plane. Here, rotating in a direction away from the sub-baffle may be understood as rotating in a direction close to the limiting portion 509. It can be understood that when the first sub-baffle 5081 and the second sub-baffle 5082 are closed, as the included angle between the two sub-baffles decreases, the closing speeds of the first opening and closing assembly 505 and the second opening and closing assembly 506 increases.
Thus, when the refrigerant passes through the first unidirectional passage 503 or the second unidirectional passage 504, the refrigerant can push the first sub-baffle 5081 and the second sub-baffle 5082 to rotate, so that the refrigerant passes from two sides of the rotating shaft 507, the refrigerant is divided uniformly, and the heat exchange efficiency of the heat exchanger 400 can be improved.
In some embodiments, as shown in FIG. 7, the rotating shaft 507 extends in the radial direction of the flow dividing body 536 (for example, the radial direction of the second sub-body 532), the first opening and closing assembly 505 and the second opening and closing assembly 506 each include limiting portions 509 in pair, and the limiting portions in pair may be symmetrically located on two sides of the rotating shaft 507.
For example, the first sub-baffle 5081 is blocked by the limiting portion 509 on one side of the rotating shaft 507, and the second sub-baffle 5082 is blocked by the limiting portion 509 on the other side of the rotating shaft 507. The positions of the two limiting portions 509 respectively correspond to the positions of the first sub-baffle 5081 and the second sub-baffle 5082, and the two limiting portions 509 respectively abut against the middle of the first sub-baffle 5081 and the middle of the second sub-baffle 5082, thereby providing a stable and reliable supporting force for the baffle 508. Thus, when the limiting portions 509 block the first sub-baffle 5081 and the second sub-baffle 5082, the first unidirectional passage 503 and the second unidirectional passage 504 have good closing performance.
The heat exchanger 400 being the second heat exchanger 203 is mainly taken as an example below for description of flow paths of the refrigerant when the heat exchanger 400 serves as the condenser and the evaporator, respectively.
When the second heat exchanger 203 serves as the condenser, as shown in FIG. 2, the refrigerant pressure is high, the first pipeline 510 is connected to an exhaust pipe of the compressor 201, and the influence of the pressure drop on the heat exchange performance of the heat exchanger 400 is small. Under such circumstance, a small number of flow dividing passages (that is, the first unidirectional passages 503) may be used for flow of the refrigerant, thereby increasing the flow rate of the refrigerant inside the first unidirectional passages 503, and then increasing the heat transfer coefficient of the heat exchanger 400.
When the second heat exchanger 203 serves as the evaporator, as shown in FIG. 3, the refrigerant pressure is low, the first pipeline 510 is connected to a gas return pipe of the compressor 201, and the influence of the pressure drop on the heat exchange performance of the heat exchanger 400 is large. Under such circumstance, a large number of flow dividing passages (that is, the second unidirectional passages 504) need to be used for flow of the refrigerant, thereby reducing the pressure drop on the refrigerant side, and avoiding the influence on the heat exchange performance of the heat exchanger 400 caused by the excessively large evaporation temperature glide caused by the excessively large pressure drop. Here, the evaporation temperature glide may be understood as the difference between an inlet evaporation temperature and an outlet evaporation temperature of the evaporator.
It should be noted that dotted arrows in FIG. 2 and FIG. 3 represent flow directions of the refrigerant.
In the air conditioner 1000 provided in some embodiments of the present disclosure, the refrigerant can unidirectionally flow in the first unidirectional passages 503 through the first opening and closing assemblies 505, the refrigerant can unidirectionally flow in the second unidirectional passages 504 through the second opening and closing assemblies 506, and the flow directions of the refrigerant inside the first unidirectional passages 503 and the second unidirectional passages 504 are opposite. Thus, passages allowing the refrigerant to flow in different directions can be formed in the same flow dividing member 530, and the flow dividing member 530 can have different flow areas in the different flow directions of the refrigerant, thereby switching between the first unidirectional passages 503 and the second unidirectional passages 504 on the basis of the different states of the heat exchanger 400, and then selecting the corresponding number of flow dividing passages on the basis of the state of the heat exchanger 400.
Here, the state of the heat exchanger 400 may be understood as the corresponding working state when the heat exchanger 400 serves as the condenser or the evaporator. The flow area may be understood as the sectional area of the passage through which the refrigerant flows.
Of course, in some embodiments, the structure of the flow dividing member 530 switching different numbers of flow dividing passages may also be other structures.
As shown in FIG. 12 to FIG. 14A, the flow dividing member 530 includes a first flow guide pipe 601 (an inner-layer pipe). The first end of the first pipeline 510 is connected to the compressor 201, and the second end thereof is connected to the first flow guide pipe 601.
The flow dividing member 530 further includes a second flow guide pipe 602 (an outer-layer pipe). The first ends of the plurality of second pipelines 520 are connected to the heat exchanger 400, and the second ends thereof are connected to the second flow guide pipe 602. The second flow guide pipe 602 is sleeved on an outer side of the first flow guide pipe 601 and is in contact with the first flow guide pipe 601 so as to close a gap between the second flow guide pipe 602 and the first flow guide pipe 601.
In some embodiments, as shown in FIG. 15 to FIG. 17, the first flow guide pipe 601 includes a first body 6011. The cross section of the first body 6011 may be circular.
The first flow guide pipe 601 further includes a plurality of first flow guide holes 6012 (inner flow guide holes). The plurality of first flow guide holes 6012 are arranged at intervals in a circumferential direction of the first body 6011 and penetrate through a pipe wall of the first body 6011.
In some examples, as shown in FIG. 15 to FIG. 17, the plurality of first flow guide holes 6012 include a plurality of first sub-flow guide holes 6013 (a first group of flow guide holes). The number of the plurality of first sub-flow guide holes 6013 is equal to the number of second flow guide holes 6022.
The plurality of first flow guide holes 6012 further include a plurality of second sub-flow guide holes 6014 (a second group of flow guide holes). The number of the plurality of first sub-flow guide holes 6013 is greater than the number of the plurality of second sub-flow guide holes 6014.
In some embodiments, as shown in FIG. 18 to FIG. 20, the second flow guide pipe 602 includes a second body 6021. The cross section of the second body 6021 may be circular.
The second flow guide pipe 602 further includes a plurality of second flow guide holes 6022 (outer flow guide holes). The plurality of second flow guide holes 6022 are arranged at intervals in a circumferential direction of the second body 6021 and penetrate through a pipe wall of the second body 6021. The plurality of second flow guide holes 6022 are in communication with the plurality of second pipelines 520.
In some embodiments, at least one of the first flow guide pipe 601 and the second flow guide pipe 602 is rotatable, and the first flow guide pipe 601 and the second flow guide pipe 602 are configured to rotate relative to each other between a first relative position and a second relative position. For example, one of the first flow guide pipe 601 and the second flow guide pipe 602 is stationary, and the other one of the first flow guide pipe 601 and the second flow guide pipe 602 rotates. Of course, the first flow guide pipe 601 and the second flow guide pipe 602 may also rotate respectively, thereby reducing the rotation amplitude of the first flow guide pipe 601 and the second flow guide pipe 602, and preventing twining of the first pipeline 510 and the plurality of second pipelines 520. It should be noted that the first flow guide pipe 601 or the second flow guide pipe 602 may rotate clockwise or anti-clockwise. The first flow guide pipe 601 rotating and the second flow guide pipe 602 being stationary are mainly taken as an example below for explanation.
The positions of the plurality of first flow guide holes 6012 in the axial direction of the first body 6011 may correspond to the positions of the plurality of second flow guide holes 6022 in the axial direction of the first body 6011. When the first flow guide pipe 601 rotates to the first relative position or the second relative position, the plurality of second flow guide holes 6022 are in communication with the plurality of first sub-flow guide holes 6013 or the plurality of second sub-flow guide holes 6014.
At the first relative position, the plurality of first sub-flow guide holes 6013 are in communication with the plurality of second flow guide holes 6022, so as to form first flow guide passages. For example, when the plurality of first sub-flow guide holes 6013 are in communication with the plurality of second flow guide holes 6022, the refrigerant can sequentially pass through the first flow guide pipe 601 and the second flow guide pipe 602 to flow to the plurality of second pipelines 520, or sequentially pass through the second flow guide pipe 602 and the first flow guide pipe 601 to flow to the first pipeline 510. At this time, the number of the second pipelines 520 through which the refrigerant flows is equal to the number of the first flow guide holes 6012 in communication with the second flow guide holes 6022. Moreover, when the first flow guide holes 6012 are not in communication with the second flow guide holes 6022, the refrigerant cannot flow through the second pipelines 520 there.
At the second relative position, the plurality of second sub-flow guide holes 6014 are in communication with part of the second flow guide holes 6022, so as to form second flow guide passages.
The number of the plurality of first sub-flow guide holes 6013 and the number of the plurality of second sub-flow guide holes 6014 are different, so that the flow area of the first flow guide passages is different from the flow area of the second flow guide passages, and the plurality of first sub-flow guide holes 6013 and the plurality of second sub-flow guide holes 6014 are in communication with different numbers of second pipelines 520, respectively. When the refrigerant flows in one of the plurality of first sub-flow guide holes 6013 and the plurality of second sub-flow guide holes 6014, the other one is cut off to prevent the refrigerant from passing.
In some embodiments, the number of the flow dividing passages of the flow dividing member 530 can be selected on the basis of the working state and working load of the heat exchanger 400.
In some examples, when the heat exchanger 400 serves as the condenser and the working load is greater than or equal to the preset value, the first flow guide pipe 601 is controlled to rotate to the first relative position, so that the plurality of first sub-flow guide holes 6013 overlap the plurality of second flow guide holes 6022, which can increase the flow area of the first flow guide passages. Under such circumstances, the number of the flow dividing passages in communication with the heat exchanger 400 when the heat exchanger 400 serves as the condenser is greater than the number of the flow dividing passages in communication with the heat exchanger 400 when the heat exchanger 400 serves as the evaporator.
Here, the working load can be understood as the heat exchange capacity (or the heat exchange amount) of the heat exchanger 400. The heat exchange capacity may be related to parameters, such as the heat transfer coefficient, the refrigerant flow velocity, the refrigerant flow rate, the heat exchange area, the heat exchange temperature difference, etc., of the heat exchanger 400.
It can be understood that the preset value is a numerical value set in advance and is related to the ultimate heat exchange capacity of the heat exchanger 400. In some examples, the preset value is 50%, 60%, 70%, 80%, 90%, or 100% of the ultimate heat exchange capacity of the heat exchanger 400. As the preset value increases, the ultimate heat exchange capacity of the heat exchanger 400 increases, and the working load that can be borne by the heat exchanger 400 increases. Of course, the preset value can also be other numerical values. The ultimate heat exchange capacity of the heat exchanger 400 can be understood as the highest heat exchange capacity that can be borne by the heat exchanger 400. Besides, the working load of the heat exchanger 400 being greater than or equal to the preset value can be understood as the working load of the heat exchanger 400 being high.
As shown in FIG. 14A, when the heat exchanger 400 serves as the condenser and the working load is greater than or equal to the preset value, the refrigerant pressure is high, and the first pipeline 510 is connected to the exhaust pipe of the compressor 201. Under such circumstances, the working load of the heat exchanger 400 is high, and the number of the flow dividing passages (that is, the first flow guide passages corresponding to the plurality of first sub-flow guide holes 6013) needs to be increased for flowing of the refrigerant, so that the pressure drop on the refrigerant side can be reduced, and the heat exchange performance of the heat exchanger 400 can be improved.
In some examples, when the heat exchanger 400 serves as the condenser and the working load is less than the preset value, the first flow guide pipe 601 is controlled to rotate to the second relative position, so that the plurality of second sub-flow guide holes 6014 overlap part of the second flow guide holes 6022, so as to form the second flow guide passages with the small flow area. Under such circumstance, a few flow dividing passages are in communication with the heat exchanger 400. Here, the working load of the heat exchanger 400 being less than the preset value can be understood as the working load of the heat exchanger 400 being low.
As shown in FIG. 14B, when the heat exchanger 400 serves as the condenser and the working load is less than the preset value, the refrigerant is in a high-pressure region, the first pipeline 510 is connected to the exhaust pipe of the compressor 201, and the influence of the pressure drop on the heat exchange performance of the heat exchanger 400 is small. Under such circumstances, the number of the flow dividing passages (that is, the second flow guide passages corresponding to the plurality of second sub-flow guide holes 6014) can be reduced for flowing of the refrigerant, so that the flow velocity of the refrigerant inside the second flow guide passages can be increased, then the heat transfer coefficient of the heat exchanger 400 can be increased, and the heat exchange performance of the heat exchanger 400 can be improved.
For example, when the heat exchanger 400 serves as the condenser and the working load is less than the preset value, the number of the flow dividing passages at an inlet of the heat exchanger 400 is reduced by approximately half.
In some examples, when the heat exchanger 400 serves as the evaporator, the first flow guide pipe 601 is controlled to rotate to the first relative position, so that the plurality of first sub-flow guide holes 6013 overlap the plurality of second flow guide holes 6022, so as to form the first flow guide passages.
As shown in FIG. 14C, when the heat exchanger 400 serves as the evaporator, the flow dividing member 530 is located at an outlet of the heat exchanger 400, and the dryness of the refrigerant during an evaporation process increases. Besides, the refrigerant is in a low-pressure region, the first pipeline 510 is connected to the gas return pipe of the compressor 201, and the pressure drop may affect the heat exchange performance of the heat exchanger 400. Under such circumstances, the number of the flow dividing passages (that is, the first flow guide passages corresponding to the plurality of first sub-flow guide holes 6013) needs to be increased for flowing of the refrigerant, so that the pressure drop on the refrigerant side can be reduced, and the influence on the heat exchange performance of the heat exchanger 400 caused by the excessively large evaporation temperature glide caused by the excessively large pressure drop can be avoided.
Thus, the number of the corresponding flow dividing passages is adjusted on the basis of the working state and working load of the heat exchanger 400, so that the heat exchanger 400 can work at the highest heat exchange performance in various states, and the heat exchange performance of the heat exchanger 400 is improved. It should be noted that dotted arrows in FIG. 14A to FIG. 14C represent flow directions of the refrigerant.
In some embodiments, as shown in FIG. 18, one end of the second flow guide pipe 602 is closed to form a blocking portion 6023 (a closed end surface). The second flow guide holes 6022 are close to the blocking portion 6023. Under such circumstances, one end of the first flow guide pipe 601 abuts against the blocking portion 6023, so that the blocking portion 6023 can close the end of the first flow guide pipe 601. The first flow guide holes 6012 are close to the blocking portion 6023.
For example, the first flow guide holes 6012 are distributed at intervals on a peripheral side of the first body 6011 close to the blocking portion 6023, and the second flow guide holes 6022 correspond to the first flow guide holes 6012 in position. Here, corresponding in position can be understood as that at the first relative position or the second relative position, the central axes of the second flow guide holes 6022 approximately overlap the central axes of the corresponding first flow guide holes 6012, so that the first flow guide holes 6012 are in communication with the second flow guide holes 6022.
Thus, by arranging the first flow guide holes 6012 and the second flow guide holes 6022 to be close to the blocking portion 6023, the refrigerant can be blocked by the blocking portion 6023 when flowing inside the first flow guide pipe 601, the refrigerant can enter the first flow guide holes 6012 and the second flow guide holes 6022 conveniently, and the refrigerant can flow along predetermined paths conveniently.
It can be understood that when the refrigerant is driven by the compressor 201 to enter the first flow guide pipe 601 through the first pipeline 510, the end of the first flow guide pipe 601 is blocked by the blocking portion 6023, so that the refrigerant can flow into the flow dividing member 530 in the axial direction of the flow dividing member 530 and flow out of the flow dividing member 530 in the radial direction of the flow dividing member 530, thereby forming relatively uniform flow paths of the refrigerant, improving the flow dividing uniformity of the refrigerant, and improving the refrigeration or heating effect of the air conditioner 1000.
In some embodiments, as shown in FIG. 14A to FIG. 14C, the second flow guide pipe 602 further includes a plurality of connecting portions 6024 (liquid separation joint portions). The plurality of connecting portions 6024 are arranged in the circumferential direction of the second body 6021 and are in communication with the plurality of second flow guide holes 6022 respectively. The connecting portions 6024 extend in the radial direction of the second body 6021 and in a direction away from the second body 6021, and the plurality of second pipelines 520 are respectively connected to (for example, inserted into) the plurality of connecting portions 6024, so as to be in communication with the plurality of second flow guide holes 6022 through the plurality of connecting portions 6024. Besides, the connecting portions 6024 may be in hollow cylindrical shapes. Thus, the refrigerant can flow between the plurality of second pipelines 520 and the flow dividing member 530 through the connecting portions 6024.
The connecting portions 6024 extend outwards in the radial direction of the second body 6021, so that the connecting portions 6024 can be connected to the second pipelines 520, the connection reliability of the second pipelines 520 with the flow dividing member 530 can be improved, and the operation stability of the air conditioner 1000 can be improved. The structure is simple and reliable, and can be flexibly adjusted and replaced.
Besides, by arranging the plurality of connecting portions 6024 connected to the plurality of second pipelines 520, the refrigerant can be uniformly guided into the plurality of second pipelines 520, the flow resistance of the refrigerant can be reduced, and the flow rate of the refrigerant can be ensured. Besides, the connecting portions 6024 extend outwards, so that the refrigerant can flow into the corresponding second pipelines 520 after flowing outwards in the radial direction by a preset distance, the refrigerant can be prevented from quickly flowing into the second pipelines 520 after being sprayed from the second flow guide holes 6022, and the flow stability of the refrigerant is improved.
In some embodiments, as shown in FIG. 16 and FIG. 19, the plurality of first sub-flow guide holes 6013 are uniformly arranged in the circumferential direction of the first body 6011, and the plurality of second sub-flow guide holes 6014 are uniformly arranged in the circumferential direction of the first body 6011. The plurality of second flow guide holes 6022 are uniformly arranged in the circumferential direction of the second body 6021. Thus, the refrigerant can uniformly flow towards the different second pipelines 520, the pressure distribution inside the air conditioner 1000 can be balanced, and the flow rate or flow velocity of the refrigerant can be stabilized, thereby improving the stability and reliability of the air conditioner 1000.
In some embodiments, as shown in FIG. 17 and FIG. 20, the plurality of second flow guide holes 6022 and the plurality of first flow guide holes 6012 are respectively circular holes and have equal diameters. When the refrigerant passes through the plurality of second flow guide holes 6022 and the plurality of first flow guide holes 6012, the circular holes with the equal diameters can make the refrigerant have the approximately same flow velocity and flow rate inside the circular holes at different positions, so that the distribution uniformity of the refrigerant is improved, and the working stability and heat exchange effect of the air conditioner 1000 are improved.
Besides, the shapes of the circular holes match the shapes of cross sections of the connecting portions 6024 and the second pipelines 520. Thus, the refrigerant flows smoothly between the flow dividing member 530 and the second pipelines 520, thereby reducing the pressure loss of the air conditioner 1000. Besides, the structures in the same shape are good in sealing performance after being connected, so that the risk of leakage of the refrigerant is reduced, and the working reliability of the air conditioner 1000 is improved.
In some embodiments, as shown in FIG. 16, the number of the plurality of first sub-flow guide holes 6013 is twice that of the plurality of second sub-flow guide holes 6014, and each of the plurality of second sub-flow guide holes 6014 is located between two adjacent first sub-flow guide holes 6013 in the circumferential direction of the first body 6011. Besides, the two first sub-flow guide holes 6013 adjacent to the second sub-flow guide hole 6014 are arranged symmetric about a central axis K of the second sub-flow guide hole 6014.
In some examples, the plurality of first sub-flow guide holes 6013 are uniformly distributed at intervals of 180/N° in the circumferential direction of the first body 6011, and the number is 2N (that is, a multiple of 2). The plurality of second sub-flow guide holes 6014 are uniformly distributed at intervals of 360/N° in the circumferential direction of the first body 6011, and the number is N. The plurality of second flow guide holes 6022 are uniformly distributed at intervals of 180/N° in the circumferential direction of the second body 6021, and the number is 2N. For example, the plurality of first flow guide holes 6012 include six first sub-flow guide holes 6013 and three second sub-flow guide holes 6014.
The number of the plurality of first sub-flow guide holes 6013 is twice that of the plurality of second sub-flow guide holes 6014, so that the central axis K of any second sub-flow guide hole 6014 may be located on an axis of symmetry of the two adjacent first sub-flow guide holes 6013, thereby facilitating uniform distribution of the refrigerant.
In some embodiments, as shown in FIG. 14A to FIG. 14C, the air conditioner 1000 further includes a driver 700. The driver 700 is arranged on the periphery of the second flow guide pipe 602, and configured to drive the first flow guide pipe 601 and the second flow guide pipe 602 to rotate relative to each other between the first relative position and the second relative position.
In some examples, the driver 700 is annular, surrounds the second flow guide pipe 602, and is attached to the second flow guide pipe 602. The driver 700 can drive, by means of an electromagnetic effect, the first flow guide pipe 601 to rotate to a preset angle, so that the plurality of first sub-flow guide holes 6013 or the plurality of second sub-flow guide holes 6014 overlap the plurality of second flow guide holes 6022, thereby forming the first flow guide passages and the second flow guide passages with different flow rates, and changing the number of the flow dividing passages.
Under such circumstances, the air conditioner 1000 further includes a signal device 800, and the signal device 800 is located on the outer side of the flow dividing member 530 and connected to the driver 700. The signal device 800 includes a signal acquisition device and a signal generation device, and can determine the working state of the air conditioner 1000 on the basis of the parameters, such as the external air state, the exhaust state of the compressor 201, etc., and send a signal to the driver 700. For example, the signal device 800 may be a pressure sensor, a temperature sensor, a flow sensor, an angular displacement sensor, or a current sensor. It should be noted that the signal device 800 can also be integrated into the controller 300, or arranged independent of the controller 300.
In some embodiments, the driver 700 may include an electromagnetic driver, which adjusts the relative positions of the first flow guide pipe 601 and the second flow guide pipe 602 by means of an electromagnetic force. For example, the electromagnetic driver is similar to a coil structure inside the solenoid valve, and by means of the electromagnetic force generated after the coil structure is electrified, the first flow guide pipe 601 is driven to rotate. Thus, the first flow guide passages and the second flow guide passages are switched quickly, thereby changing the number of the flow dividing passages conveniently.
In the air conditioner 1000 provided by some embodiments of the present disclosure, by arranging the first flow guide pipe 601 and the second flow guide pipe 602, the refrigerant can sequentially pass through the first flow guide pipe 601 and the second flow guide pipe 602 to flow to the outer side of the flow dividing member 530 in the radial direction. Besides, the first flow guide pipe 601 and the second flow guide pipe 602 can rotate relative to each other, and by adjusting the position of the first flow guide pipe 601 to the first relative position and the second relative position, the first flow guide holes 6012 and the second flow guide holes 6022 can form the flow dividing passages with different flow areas, thereby forming the first flow guide passages and the second flow guide passages with different flow rates, and then controlling the flow rate of the refrigerant. Thus, when the air conditioner 1000 is in the refrigeration mode or the heating mode, the number of the flow dividing passages of the flow dividing member 530 may be adapted to the highest heat exchange performance of the heat exchanger 400.
Thus, for the different states of the heat exchanger 400, the relative rotation angle of the first flow guide pipe 601 and the second flow guide pipe 602 can be flexibly adjusted, and the number of the flow dividing passages can be changed without arranging check valves in different directions and with different flow areas, thereby improving the compactness of the structure of the flow dividing member 530, accurately distributing the flow rate of the refrigerant, and then improving the heat exchange performance of the heat exchanger 400.
Besides, the first flow guide holes 6012 and the second flow guide holes 6022 are respectively located on the pipe wall of the first body 6011 and the pipe body of the second body 6021, so that the refrigerant can flow from inside to outside or from outside to inside in the radial direction of the flow dividing member 530, the refrigerant can form an annular flow inside the flow dividing member 530, the refrigerant is uniformly distributed, and the flow dividing uniformity of the refrigerant is improved.
The structure of the heat exchanger 400 according to some embodiments of the present disclosure is introduced below.
In some embodiments, as shown in FIG. 21, the heat exchanger 400 includes a plurality of heat exchange tubes 420. The plurality of heat exchange tubes 420 are connected to the compressor 201, and the refrigerant from the compressor 201 flows through the plurality of heat exchange tubes 420 for heat exchange. First ends of the plurality of heat exchange tubes 420 are respectively connected to the plurality of second pipelines 520.
The heat exchanger 400 further includes a plurality of fins 410. The plurality of fins 410 are arranged at intervals in a thickness direction (for example, the MN direction in FIG. 21) of the corresponding fins. The plurality of heat exchange tubes 420 are inserted into the plurality of fins 410 and arranged at intervals in a length direction (for example, the UD direction in FIG. 21) of the plurality of fins 410.
The heat exchanger 400 further includes a connecting pipe 430 (a flute-shaped pipe). The connecting pipe 430 is connected to second ends of the plurality of heat exchange tubes 420.
The heat exchanger 400 may be of a single-row structure. For example, a row of heat exchange tubes 420 are arranged in the thickness direction of the plurality of fins 410, and the plurality of heat exchange tubes 420 are connected to the plurality of second pipelines 520 on the same side of the plurality of fins 410.
The flow dividing member 530 being of the structures as shown in FIG. 2 and FIG. 3 is mainly taken as an example below for explanation.
As shown in FIG. 2, when the heat exchanger 400 serves as the condenser, the first part of heat exchange tubes 420 in communication with the first unidirectional passages 503 have the same flow direction, and the refrigerant flows into the first part of heat exchange tubes 420 through the flow dividing assembly 500, so as to flow inside the first part of heat exchange tubes 420, thereby improving the heat exchange performance of the heat exchanger 400. Then the refrigerant flows into the connecting pipe 430 through the second ends of the first part of heat exchange tubes 420 and is gathered.
As shown in FIG. 3, when the heat exchanger 400 serves as the evaporator, the second part of heat exchange tubes 420 in communication with the second unidirectional passages 504 have the same flow direction, and the refrigerant flows into the second part of heat exchange tubes 420 through the connecting pipe 430, so as to flow inside the second part of heat exchange tubes 420, thereby improving the heat exchange performance of the heat exchanger 400. Then the refrigerant is gathered inside the flow dividing member 530.
The flow dividing member 530 being of the structures as shown in FIG. 14A to FIG. 14C is taken as an example for explanation.
As shown in FIG. 14A, when the heat exchanger 400 serves as the condenser and the working load is greater than or equal to the preset value, the third part of heat exchange tubes 420 in communication with the plurality of first sub-flow guide holes 6013 have the same flow direction, and the refrigerant is divided into the third part of heat exchange tubes 420 through the flow dividing assembly 500, so as to flow inside the third part of heat exchange tubes 420, thereby improving the heat exchange performance of the heat exchanger 400. Then the refrigerant flows into the connecting pipe 430 through the second ends of the third part of heat exchange tubes 420 and is gathered.
As shown in FIG. 14B, when the heat exchanger 400 serves as the condenser and the working load is less than the preset value, the fourth part of heat exchange tubes 420 in communication with the plurality of second sub-flow guide holes 6014 have the same flow direction, and the remaining working process is similar to the working process when the heat exchanger 400 serves as the condenser and the working load is greater than or equal to the preset value, which is not repeated here.
As shown in FIG. 14C, when the heat exchanger 400 serves as the evaporator, the third part of heat exchange tubes 420 in communication with the plurality of first sub-flow guide holes 6013 have the same flow direction, and the refrigerant flows into the third part of heat exchange tubes 420 through the connecting pipe 430, so as to flow inside the third part of heat exchange tubes 420, thereby improving the heat exchange performance of the heat exchanger 400. Then the refrigerant is gathered inside the flow dividing member 530.
In some embodiments, as shown in FIG. 21, the heat exchanger 400 further includes a supercooling pipe 440. The supercooling pipe 440 is inserted into the plurality of fins 410 and is located on one side (for example, the lower side) of the plurality of heat exchange tubes 420 in a height direction (for example, the UD direction). A first end of the supercooling pipe 440 is connected to the connecting pipe 430, and a second end thereof is connected to the throttling assembly (that is, the expansion valve 204). The supercooling pipe 440 can increase the refrigerant flow volume of the heat exchanger 400, thereby increasing the capacity of the heat exchanger 400 for accommodating the liquid refrigerant, and then improving the heat exchange effect of the heat exchanger 400.
In some examples, the supercooling pipe 440 includes a first supercooling sub-pipe 4401. A first end of the first supercooling sub-pipe 4401 is connected to the connecting pipe 430.
The supercooling pipe 440 further includes a second supercooling sub-pipe 4402. A second end of the first supercooling sub-pipe 4401 is connected to a first end of the second supercooling sub-pipe 4402.
The supercooling pipe 440 further includes a third supercooling sub-pipe 4403. A second end of the second supercooling sub-pipe 4402 is bent towards the third supercooling sub-pipe 4403, so as to be connected to a first end of the third supercooling sub-pipe 4403. A second end of the third supercooling sub-pipe 4403 is connected to the throttling assembly. The extension directions of the first supercooling sub-pipe 4401 and the third supercooling sub-pipe 4403 are parallel to each other.
It should be noted that the shapes of the heat exchange tubes 420 may be similar to the shape of the supercooling pipe 440.
In the description of the above implementation manners, the specific features, structures, materials or characteristics may be combined appropriately in any one or more embodiments or examples.
A person skilled in the art should understand that the disclosure scope of the present disclosure is not limited to the above specific embodiments, and some elements of the embodiments may be amended and replaced without departing from the spirit of the present disclosure. The scope of the present disclosure is limited by the appended claims.

Claims

An air conditioner, comprising:
a compressor configured to compress a refrigerant;

a heat exchanger configured to exchange heat with the refrigerant;

a throttling assembly configured to adjust a flow rate of the refrigerant, wherein the compressor, the heat exchanger and the throttling assembly are connected to form a refrigerant loop; and

a flow dividing assembly comprising:
a first pipeline, wherein a first end of the first pipeline is connected to the compressor;

a plurality of second pipelines, wherein first ends of the plurality of second pipelines are connected to the heat exchanger; and

a flow dividing member, wherein a first end of the flow dividing member is connected to a second end of the first pipeline, and a second end of the flow dividing member is connected to second ends of the plurality of second pipelines,wherein the flow dividing member comprises different numbers of flow dividing passages, and the flow dividing passages communicate the first pipeline with the plurality of second pipelines, and wherein the flow dividing member is configured to switch among the different numbers of flow dividing passages on the basis of at least one of a flow direction of the refrigerant and a working load of the heat exchanger, so as to change the number of the flow dividing passages in communication with the heat exchanger.
The air conditioner according to claim 1, wherein the flow dividing member comprises:
a flow dividing body;

a first passage arranged inside the flow dividing body, wherein the second end of the first pipeline is in communication with the first passage; and

a plurality of second passages arranged inside the flow dividing body, wherein the second ends of the plurality of second pipelines are in communication with the plurality of second passages respectively, and the first passage is in communication with the plurality of second passages; and wherein the plurality of second passages comprise:
first unidirectional passages configured to be opened when the refrigerant flows from the first pipeline to the plurality of second pipelines and be closed when the refrigerant flows from the plurality of second pipelines to the first pipeline; and

second unidirectional passages configured to be closed when the refrigerant flows from the first pipeline to the plurality of second pipelines and be opened when the refrigerant flows from the plurality of second pipelines to the first pipeline, wherein the number of the first unidirectional passages is less than the number of the second unidirectional passages.
The air conditioner according to claim 2, wherein the plurality of second passages further comprise:
first opening and closing assemblies arranged inside the first unidirectional passages and configured to be opened when the refrigerant flows from the first pipeline to the plurality of second pipelines, so as to enable the refrigerant to enter the plurality of second pipelines through the first unidirectional passages; and

second opening and closing assemblies arranged inside the second unidirectional passages and configured to be opened when the refrigerant flows from the plurality of second pipelines to the first pipeline, so as to enable the refrigerant to enter the first pipeline through the second unidirectional passages.
The air conditioner according to claim 3, wherein any one of the first opening and closing assemblies and the second opening and closing assemblies comprises:
a rotating shaft, wherein two ends of the rotating shaft are arranged on an inner wall surface of the first unidirectional passage or the second unidirectional passage, and the rotating shaft extends in a radial direction of the first unidirectional passage or the second unidirectional passage;

a baffle rotationally connected to the rotating shaft and configured to open and close the first unidirectional passage or the second unidirectional passage; and

limiting portions arranged on the inner wall surface of the first unidirectional passage or the second unidirectional passage and protruding from the corresponding inner wall surface,

wherein the limiting portions inside the first unidirectional passage are located on one side of the baffle close to the first passage and abut against the baffle, so as to limit a rotating direction of the baffle inside the first unidirectional passage; and

the limiting portions inside the second unidirectional passage are located on one side of the baffle away from the first passage and abut against the baffle, so as to limit a rotating direction of the baffle inside the second unidirectional passage.
The air conditioner according to claim 4, wherein the baffle comprises:
a first sub-baffle;

a second sub-baffle, wherein the first sub-baffle and the second sub-baffle are respectively located on two sides of the rotating shaft in a radial direction;

a first hinge portion arranged at one end of the first sub-baffle close to the rotating shaft and rotationally sleeved on the rotating shaft; and

a second hinge portion arranged at one end of the second sub-baffle close to the rotating shaft and rotationally sleeved on the rotating shaft.
The air conditioner according to claim 4 or 5, wherein the rotating shaft extends in a radial direction of the flow dividing body, each of the first opening and closing assemblies and the second opening and closing assemblies comprises the limiting portions in pair, and the limiting portions in pair are symmetrically located on two sides of the rotating shaft.
The air conditioner according to any one of claims 2 to 6, wherein the flow dividing body has a circular cross section, the plurality of second passages are arranged at intervals in a circumferential direction of the flow dividing body, the first passage is located at a central axis of the flow dividing body, and on a plane perpendicular to the central axis of the flow dividing body, orthographic projections of the plurality of second passages surround an orthographic projection of the first passage.
The air conditioner according to claim 7,
wherein in semicircles of the cross section of the flow dividing body, the first unidirectional passages and the second unidirectional passages are alternately arranged in the circumferential direction of the flow dividing body; and

wherein the first unidirectional passages in the first semicircle of the cross section of the flow dividing body are symmetric to the first unidirectional passages in the second semicircle of the cross section of the flow dividing body, and the second unidirectional passages in the first semicircle of the cross section of the flow dividing body are symmetric to the second unidirectional passages in the second semicircle of the cross section of the flow dividing body.
The air conditioner according to any one of claims 2 to 8, wherein the flow dividing body comprises:
a cylindrical first sub-body, wherein the first passage is arranged inside the first sub-body; and

a cylindrical second sub-body, wherein a diameter of the second sub-body is greater than a diameter of the first sub-body, and the plurality of second passages are arranged inside the second sub-body.
The air conditioner according to claim 9, wherein the flow dividing body further comprises:
a transition portion connecting the second sub-body to the first sub-body, wherein a diameter of the transition portion decreases in a direction close to the first sub-body;

a flow guide passage arranged inside the transition portion and connecting the first passage to the plurality of second passages; and

a flow guide portion arranged at the center of the transition portion, wherein the flow guide portion is in a shape of a cone, a vertex of the cone faces the first passage, and the flow guide passage surrounds the flow guide portion.
The air conditioner according to claim 1, wherein the flow dividing member comprises:
a first flow guide pipe connected to the second end of the first pipeline, wherein the first flow guide pipe comprises:
a first body; and

a plurality of first flow guide holes arranged at intervals in a circumferential direction of the first body and penetrating through a pipe wall of the first body, wherein the plurality of first flow guide holes comprise:
a plurality of first sub-flow guide holes; and

a plurality of second sub-flow guide holes, wherein the number of the plurality of first sub-flow guide holes is greater than the number of the plurality of second sub-flow guide holes; and

a second flow guide pipe connected to the second ends of the plurality of second pipelines, wherein the second flow guide pipe is sleeved on the first flow guide pipe, and at least one of the first flow guide pipe and the second flow guide pipe is rotatable; and the second flow guide pipe comprises:
a second body; and

a plurality of second flow guide holes arranged at intervals in a circumferential direction of the second body and penetrating through a pipe wall of the second body, wherein the plurality of second flow guide holes are in communication with the plurality of second pipelines;

wherein the first flow guide pipe and the second flow guide pipe are configured to rotate relative to each other between a first relative position and a second relative position; at the first relative position, the plurality of first sub-flow guide holes are in communication with the plurality of second flow guide holes, so as to form first flow guide passages; and at the second relative position, the plurality of second sub-flow guide holes are in communication with part of the second flow guide holes, so as to form second flow guide passages.
The air conditioner according to claim 11, wherein the first flow guide pipe and the second flow guide pipe are configured to:
rotate to the first relative position when the heat exchanger is a condenser and the working load is greater than or equal to a preset value;

rotate to the second relative position when the heat exchanger is the condenser and the working load is less than the preset value; and

rotate to the first relative position, when the heat exchanger is an evaporator.
The air conditioner according to claim 11 or 12, wherein one end of the second flow guide pipe is closed to form a blocking portion, the second flow guide holes and the first flow guide holes are close to the blocking portion, and one end of the first flow guide pipe abuts against the blocking portion.
The air conditioner according to any one of claims 11 to 13, wherein the second flow guide pipe further comprises a plurality of connecting portions, the plurality of connecting portions are arranged in the circumferential direction of the second body and are in communication with the plurality of second flow guide holes respectively, the plurality of connecting portions extend in a radial direction of the second body and in a direction away from the second body, and the plurality of second pipelines are respectively connected to the plurality of connecting portions.
The air conditioner according to any one of claims 11 to 14, wherein the plurality of first sub-flow guide holes are uniformly arranged in the circumferential direction of the first body, and the plurality of second sub-flow guide holes are uniformly arranged in the circumferential direction of the first body; the plurality of second flow guide holes are uniformly arranged in the circumferential direction of the second body; and the plurality of second flow guide holes and the plurality of first flow guide holes are respectively circular holes and have equal diameters.
The air conditioner according to any one of claims 11 to 15, wherein the number of the plurality of second flow guide holes is equal to the number of the plurality of first sub-flow guide holes.
The air conditioner according to any one of claims 11 to 16, wherein the number of the plurality of first sub-flow guide holes is twice that of the plurality of second sub-flow guide holes, and each of the plurality of second sub-flow guide holes is located between two adjacent first sub-flow guide holes in the circumferential direction of the first body.
The air conditioner according to claim 17, wherein the two first sub-flow guide holes adjacent to any one of the plurality of second sub-flow guide holes are symmetrically arranged about the second sub-flow guide hole.
The air conditioner according to any one of claims 1 to 18, wherein the heat exchanger comprises:
a plurality of fins arranged at intervals in a thickness direction of the plurality of fins;

a plurality of heat exchange tubes inserted into the plurality of fins and arranged at intervals in a length direction of the plurality of fins, wherein first ends of the plurality of heat exchange tubes are respectively connected to the plurality of second pipelines; and

a connecting pipe connected to second ends of the plurality of heat exchange tubes.
The air conditioner according to claim 19, wherein the heat exchanger further comprises a supercooling pipe, the supercooling pipe is inserted into the plurality of fins and is located on one side of the plurality of heat exchange tubes in a height direction, a first end of the supercooling pipe is connected to the connecting pipe, and a second end of the supercooling pipe is connected to the throttling assembly.