Air pipe structure, variable shunting heat exchanger and air conditioner

Abstract

The utility model relates to the technical field of household appliances, and discloses a gas pipe structure of a variable shunting heat exchanger, which comprises a gas collecting pipe, a gas inlet pipe, a gas pipe valve component and a first gas pipe branch pipe, the air inlet pipe is communicated with the air collecting pipe, the air pipe valve component is arranged on the air collecting pipe and comprises an air valve conduction inflow end and an air valve conduction outflow end, one side of the air valve conduction outflow end of the air collecting pipe is communicated with the air inlet pipe, and the first air pipe branch pipe is communicated with one side of the air valve conduction outflow end of the air collecting pipe. Wherein the first gas pipe branch pipe is arranged at the first height of the gas collecting pipe, the gas inlet pipe is arranged at the second height of the gas collecting pipe, and the first height is larger than or equal to the second height. Therefore, the integral shunting uniformity of the variable shunting heat exchanger is improved. The utility model further provides the variable flow dividing heat exchanger and the air conditioner.

Description

Technical Field

[0001] The present application relates to the field of household appliance technology, for example, to an air pipe structure, a variable split heat exchanger and an air conditioner. Background Art

[0002] When the air conditioner is running in cooling mode and heating mode, the optimal refrigerant flow path of the heat exchanger required is different. Taking the outdoor heat exchanger as an example, when the air conditioner is running in cooling mode, the optimal connection state of multiple heat exchange flow paths in the outdoor heat exchanger is series connection, and when the air conditioner is running in heating mode, the optimal connection state of multiple heat exchange flow paths in the outdoor heat exchanger is parallel connection.

[0003] The existing variable split heat exchanger can be used as an outdoor heat exchanger. In order to make the heat exchanger perform at its best when operating in different modes, valve components such as a one-way valve and a liquid separation valve are used so that the heat exchange flow path of the outdoor heat exchanger can be changed according to the operating mode of the air conditioner. When the air conditioner operates in the cooling mode, the multiple heat exchange flow paths of the variable split heat exchanger are connected in series, and when the air conditioner operates in the heating mode, the multiple heat exchange flow paths of the variable split heat exchanger are connected in parallel.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

[0005] The air pipe structure of the heat exchanger causes a large difference in refrigerant flow between different heat exchange flow paths of the heat exchanger, thereby reducing the heat exchange efficiency of the heat exchanger.

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Utility Model Content

[0007] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The disclosed embodiments provide an air pipe structure, a variable split heat exchanger and an air conditioner to solve the problem that when the air conditioner is operating in a heating mode, the refrigerant flow rate between different heat exchange paths of the heat exchanger is greatly different, thereby reducing the heat exchange efficiency of the variable split heat exchanger.

[0009] In some embodiments, the air pipe structure includes an air collecting pipe, an air inlet pipe, an air pipe valve component, and a first air pipe branch pipe. The air inlet pipe is connected to the air collecting pipe; the air pipe valve component is arranged on the air collecting pipe, including an air valve conduction inflow end and an air valve conduction outflow end, and one side of the air valve conduction outflow end of the air collecting pipe is connected to the air inlet pipe, and the first air pipe branch pipe is connected to one side of the air valve conduction outflow end of the air collecting pipe. The first air pipe branch pipe is arranged at a first height of the air collecting pipe, the air inlet pipe is arranged at a second height of the air collecting pipe, and the first height is greater than or equal to the second height.

[0010] In some embodiments, the variable split heat exchanger includes the air pipe structure as described above.

[0011] In some embodiments, an air conditioner includes a variable split heat exchanger as described above.

[0012] The air pipe structure, variable split heat exchanger and air conditioner provided by the embodiments of the present disclosure can achieve the following technical effects:

[0013] When the variable split flow heat exchanger is in heating mode, the refrigerant flowing out of the second and third air pipe branches needs to flow through the air pipe valve component, then flow in the air collecting pipe, and flow out through the air inlet pipe. Especially when the air pipe valve component is a one-way valve, the refrigerant needs to overcome a large valve resistance. In this way, the refrigerant flowing out of the second and third air pipe branches needs to have a longer flow path, and the setting of the air pipe valve component increases the flow resistance of the refrigerant, which increases the difference in refrigerant flow between different heat exchange flow paths of the variable split flow heat exchanger.

[0014] In the air pipe structure of the variable flow split heat exchanger provided in the embodiment of the present disclosure, the first air pipe branch is arranged at a first height of the air collecting pipe, and the air inlet pipe is arranged at a second height of the air collecting pipe, wherein the first height is greater than or equal to the second height. In this way, the first air pipe branch is flush with the air inlet pipe, or the air inlet pipe is arranged at the lower part of the first air pipe branch, thus reducing the upward flow height of the refrigerant flowing out of the second air pipe branch and the third air pipe branch, that is, reducing the length of the flow path of the refrigerant flowing out of the second air pipe branch and the third air pipe branch, reducing the difference in the amount of refrigerant between the first heat exchange flow path, the second heat exchange flow path and the third heat exchange flow path, and improving the overall heat exchange efficiency of the variable flow split heat exchanger.

[0015] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

[0017] Figure 1 is a schematic diagram of a liquid pipe structure provided by an embodiment of the present disclosure;

[0018] Figure 2 yes Figure 1 A front view of the liquid pipe structure shown;

[0019] Figure 3 is a structural schematic diagram of another liquid pipe structure provided by an embodiment of the present disclosure;

[0020] Figure 4 is a structural schematic diagram of another liquid pipe structure provided by an embodiment of the present disclosure;

[0021] Figure 5 is a structural schematic diagram of another liquid pipe structure provided by an embodiment of the present disclosure;

[0022] Figure 6 yes Figure 1 A bottom view of a liquid pipe structure is shown;

[0023] Figure 7 is a refrigerant flow distribution diagram of each branch when the angle a is 45 degrees provided in an embodiment of the present disclosure;

[0024] Figure 8 is a refrigerant flow distribution diagram of each branch when the angle a is 160 degrees provided in an embodiment of the present disclosure;

[0025] Fig. 9 The first branch provided in the embodiment of the present disclosure is located at a position 70 mm from the liquid inlet pipe connecting the manifold and the refrigerant flow distribution diagram of each branch;

[0026] Fig.10 It is a refrigerant flow distribution diagram of each branch provided by the embodiment of the present disclosure, where the first branch pipe is located at a distance of 80 mm from the liquid inlet pipe connecting the manifold;

[0027] Fig.11 It is a refrigerant flow distribution diagram of each branch provided by the embodiment of the present disclosure, in which the first branch pipe is located at a distance of 85 mm from the liquid inlet pipe connecting the manifold;

[0028] Fig.12 It is a refrigerant flow distribution diagram of each branch provided by the embodiment of the present disclosure, in which the first branch pipe is located at 90 mm from the liquid inlet pipe connecting the manifold;

[0029] Fig.13 The first branch pipe provided in the embodiment of the present disclosure is located at a distance of 100 mm from the liquid inlet pipe connecting the manifold and the refrigerant flow distribution diagram of each branch;

[0030] Fig.14 is a schematic structural diagram of a variable split flow heat exchanger provided by an embodiment of the present disclosure;

[0031] Fig.15 This is a schematic diagram of the gas pipe structure of a heat exchanger of a comparative example;

[0032] Fig.16 is a schematic diagram of the air pipe structure of a heat exchanger provided in an embodiment of the present disclosure;

[0033] Fig.17 is a flow diagram of the refrigerant when the variable split flow heat exchanger provided by the embodiment of the present disclosure is used as an evaporator;

[0034] Fig.18 It is a flow diagram of the refrigerant when the variable split heat exchanger provided in the embodiment of the present disclosure is used as a condenser.

[0035] Reference numerals:

[0036] 100, collecting pipe; 101, closing structure; 110, liquid inlet pipe; 120, first branch pipe; 130, liquid pipe valve component; 140, second branch pipe; 141, first connecting pipe; 142, third connecting pipe; 150, third branch pipe; 151, second connecting pipe; 152, fourth connecting pipe; 153, fifth connecting pipe; 200, gas collecting pipe; 201, first gas collecting pipe section; 202, second gas collecting pipe section; 210, gas inlet pipe; 220, gas pipe valve component; 230, first gas pipe branch pipe; 240, second gas pipe branch pipe; 250, third gas pipe branch pipe; 300, heat exchange pipe; 301, heat exchange fin; 310, first heat exchange flow path; 320, second heat exchange flow path; 330, third heat exchange flow path. DETAILED DESCRIPTION

[0037] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0038] The terms "first", "second", etc. in the specification and claims of the embodiments of the present disclosure and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate, so that the embodiments of the embodiments of the present disclosure described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0039] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0040] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to the specific circumstances.

[0041] Unless otherwise stated, the term "plurality" means two or more.

[0042] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B indicates: A or B.

[0043] The term "and / or" is a description of the association relationship between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or, A and B.

[0044] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0045] The disclosed embodiment provides a liquid pipe structure, including a manifold 100, a second branch pipe 140, and a third branch pipe 150. The second branch pipe 140 is used to communicate with the second heat exchange path 320 of the heat exchanger; the third branch pipe 150 is used to communicate with the third heat exchange path 330 of the heat exchanger, and the connection point between the second branch pipe 140 and the manifold 100 is higher than the connection point between the third branch pipe 150 and the manifold 100, wherein the number of resistance components through which the refrigerant flows after flowing out of the second branch pipe 140 is greater than the number of resistance components through which the refrigerant flows after flowing out of the third branch pipe 150, or the refrigerant flows through at least one valve component after flowing out of the second branch pipe 140. Figures 1 to 6 shown.

[0046] Optionally, the number of resistance components through which the refrigerant flows after flowing out of the second branch pipe 140 is greater than the number of resistance components through which the refrigerant flows after flowing out of the third branch pipe 150. It can be understood as follows: the resistance components may include the heat exchange tube 300 of the heat exchanger, a valve component, etc., and the valve component may be a one-way valve, a solenoid valve, a three-way valve, etc.

[0047] When the types of resistance components are the same but the resistance generated by each resistance component is different, the resistance generated by the resistance components shall be uniformly converted and then the number shall be counted. For example, the resistance component through which the refrigerant flows out of the second branch pipe 140 includes a plurality of longer heat exchange tubes, and the resistance component through which the refrigerant flows out of the third branch pipe 150 includes a plurality of shorter heat exchange tubes. Then, the plurality of longer heat exchange tubes may be folded into shorter heat exchange tubes, and then the number of the resistance components flowing through shall be counted respectively. Alternatively, when the resistance component through which the refrigerant flows out of the second branch pipe 140 includes a first valve component, and the resistance component through which the refrigerant flows out of the third branch pipe 150 includes a second valve component, and the resistance of the first valve component is greater than the resistance of the second valve component, then the resistance generated by the first valve component shall be converted into the resistance of the second valve component and then the number shall be counted. For example, if the resistance generated by the first valve component is 1.5 times that of the second valve component, then the first valve component is equivalent to 1.5 second valve components.

[0048] Similarly, when the types of resistance components are different, they can also be converted before counting. For example, the refrigerant flowing out of the second branch pipe 140 flows through 3 heat exchange tubes and 1 one-way valve, and the refrigerant flowing out of the third branch pipe 150 flows through 4 heat exchange tubes, wherein the resistance generated by 1 one-way valve is about 3 times that of 1 heat exchange tube, so 1 one-way valve is converted into 3 heat exchange tubes, and then the number of resistance components is counted separately.

[0049] Optionally, the refrigerant flows through at least one valve component after flowing out of the second branch pipe 140, which can be understood as the refrigerant at the outlet of the third branch pipe 150 does not flow through the valve component, or the number of valve components through which the refrigerant flows out of the second branch pipe 140 is greater than the number of valve components through which the refrigerant flows out of the third branch pipe 150. Other statistical methods are the same as above and will not be repeated here.

[0050] It can be understood that the number of resistance components through which the refrigerant flows after flowing out of the second branch 140 is greater than the number of resistance components through which the refrigerant flows after flowing out of the third branch 150, or the refrigerant flows through at least one valve component after flowing out of the second branch 140, so that the pressure drop or pressure loss of the refrigerant after flowing out of the second branch 140 is greater than the pressure drop or pressure loss of the refrigerant after flowing out of the third branch 150.

[0051] Optionally, the path of the refrigerant after flowing out of the second branch pipe 140 can be understood as the path from flowing out of the second branch pipe 140 to converging with the refrigerant after flowing out of the third branch pipe 150. Similarly, the path of the refrigerant after flowing out of the third branch pipe 150 can be understood as the path from the third branch pipe 150 to converging with the refrigerant after flowing out of the second branch pipe 140. Optionally, the confluence of the two can be the air inlet pipe 210 of the air pipe structure.

[0052] The liquid pipe structure of the variable flow split heat exchanger is provided with a liquid pipe valve component 130. When the air conditioner is in heating mode, the refrigerant enters the liquid pipe structure and needs to be split in the liquid pipe structure after passing through the liquid pipe valve component 130, and flows to the second branch pipe 140 and the third branch pipe 150 respectively. However, due to the influence of the refrigerant flow pressure, the refrigerant will show an upward flow trend after passing through the liquid pipe valve component 130, so that the liquid distribution amount of the upper branch pipe tends to be greater than the liquid distribution amount of the lower branch pipe. The liquid pipe structure provided in the embodiment of the present disclosure utilizes the upward flow trend of the refrigerant in the liquid pipe structure. The connection point between the second branch pipe 140 and the collecting pipe 100 is higher than the connection point between the third branch pipe 150 and the collecting pipe 100. In this way, under the upward flow trend of the refrigerant, the amount of refrigerant diverted by the second branch pipe 140 is greater than the amount of refrigerant diverted by the third branch pipe 150, so that the refrigerant flowing into the second branch pipe 140 can overcome the larger pressure drop or pressure loss, thereby balancing the diversion uniformity of the entire heat exchanger.

[0053] Optionally, the second branch pipe 140 includes a first connecting pipe 141 directly connected to the header 100, and the third branch pipe 150 includes a second connecting pipe 151 directly connected to the header 100, wherein the angle between the first connecting pipe 141 and the header 100 is smaller than the angle between the second connecting pipe 151 and the header 100. In this way, the refrigerant is further allowed to flow into the second branch pipe 140 preferentially during the flow process, thereby improving the uniformity of the refrigerant diversion of the variable diversion heat exchanger as a whole. Optionally, the angle between the first connecting pipe 141 and the header 100 can be greater than or equal to 0° and less than or equal to 45°, and the angle between the second connecting pipe 151 and the header 100 can be greater than 45° and less than or equal to 90°.

[0054] Optionally, the first connecting pipe 141 is connected in parallel with the port of the header 100; and / or the second connecting pipe 151 is vertically connected to the side wall of the header 100. Figure 3 In this way, the refrigerant in the manifold 100 can directly rush into the second branch pipe 140 after passing through the liquid pipe one-way valve 130, further increasing the flow rate entering the second branch pipe 140, better balancing the flow distribution effect, reducing the flow unevenness problem caused by the large pressure loss in the heat exchange flow path connected to the second branch pipe 140, and improving the overall flow distribution uniformity effect.

[0055] Optionally, the second branch pipe 140 further includes a third connecting pipe 142 for being directly connected to the second heat exchange flow path 320, and the third branch pipe 150 further includes a fourth connecting pipe 152 for being directly connected to the third heat exchange flow path 330, wherein the height of the third connecting pipe 142 is lower than the height of the fourth connecting pipe 152. In this way, the refrigerant of the second branch pipe 140 can flow into the second heat exchange flow path 320 at the lower part through the third connecting pipe 142, and the refrigerant of the third branch pipe 150 can flow into the third heat exchange flow path 330 at the upper part through the fourth connecting pipe 152.

[0056] Optionally, the third connecting pipe 142 and the fourth connecting pipe 152 are both arranged horizontally. The third branch pipe 150 further includes a fifth connecting pipe 153 connected between the second connecting pipe 151 and the fourth connecting pipe 152, wherein the fifth connecting pipe 153 is parallel to the first connecting pipe 141, and the length of the fifth connecting pipe 153 is greater than the length of the first connecting pipe 141. In this way, the second branch pipe 140 is in a right angle shape, and the third branch pipe 150 is in a U-shape with two right angles. Figure 4 shown.

[0057] Optionally, the liquid pipe structure also includes a first branch pipe 120 and a liquid pipe valve component, the first branch pipe is used to be connected to the first heat exchange flow path 300 of the heat exchanger, and the liquid pipe valve component 130 is arranged on the collecting pipe 100, including a liquid valve conduction inlet end and a liquid valve conduction outflow end, wherein the first branch pipe 120 is arranged on the liquid valve conduction inlet end side of the collecting pipe 100, and the second branch pipe 140 and the third branch pipe 150 are arranged on the liquid valve conduction outflow end side of the collecting pipe 100.

[0058] The liquid pipe valve component has a liquid valve conduction inlet end and a liquid valve conduction outflow end, and the manifold is divided by the liquid pipe valve component. The manifold includes a first manifold part on the side of the liquid valve conduction inlet end and a second manifold part on the side of the liquid valve conduction outflow end. Among them, the first branch pipe 120 is arranged on the first manifold part on the side of the liquid valve conduction inlet end of the manifold 100, and the second branch pipe 140 and the third branch pipe 150 are arranged on the second manifold part on the side of the liquid valve conduction outflow end of the manifold 100.

[0059] Optionally, an angle between projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is greater than or equal to 90 degrees.

[0060] By adopting the liquid pipe structure of the heat exchanger provided in the embodiment of the present invention, by directly connecting the first branch pipe 120 to the side wall of the collecting pipe 100, there is no need to use a tee for connection, which can effectively reduce the number of interfaces and simplify the process, avoid the influence of the error of the Y-shaped tee in the production process on the connection between it and the pipeline, and keep the connection structure between the branch pipe and the collecting pipe 100 consistent, thereby improving the consistency of the product. At the same time, due to the arc structure of the liquid inlet pipe 110, centrifugal force will be generated during the process of passing the refrigerant, resulting in gas-liquid separation of the refrigerant under the action of centrifugal force, and then the part close to the outer arc of the liquid inlet pipe 110 is liquid phase refrigerant, and the part close to the inner arc is gas phase refrigerant, and the gas-liquid separation state will still continue to a certain extent after entering the collecting pipe 100. At this time, since the gas and liquid phases of the refrigerant are distributed very unevenly, it is easy to cause the liquid entering the first The refrigerant gas flow rate in one branch pipe 120 is relatively high, which in turn affects its heat exchange efficiency. By setting the first branch pipe 120 so that the angle between the projection along the axial direction of the collecting pipe 100 and the projection of the liquid inlet pipe 110 is greater than or equal to 90 degrees, under the action of the centrifugal force of the liquid inlet pipe 110, the liquid-phase refrigerant will be distributed in large quantities on the side of the collecting pipe 100 away from the liquid inlet pipe 110 after entering the collecting pipe 100. Therefore, the first branch pipe 120 is set to have an angle of more than 90 degrees relative to the liquid inlet pipe 110. The first branch pipe 120 can be connected to the side of the collecting pipe 100 away from the liquid inlet pipe 110, that is, the side where the liquid-phase refrigerant is more distributed, so that the liquid-phase refrigerant can fully flow into it, ensuring its heat exchange effect and improving the uniformity of the diversion of the liquid-phase refrigerant. The overall structure and process can be simplified and the uniformity of the diversion of the liquid-phase refrigerant can be ensured.

[0061] Among them, the liquid inlet pipe 110 includes at least one bent portion. It can be understood that since this solution is to solve the problem of uneven distribution of refrigerant gas and liquid caused by the centrifugal force of the liquid inlet, the liquid inlet pipe 110 adapted to this solution needs to have a part of the bent section so that it can change the flow direction of the internal refrigerant and produce a certain centrifugal effect on the refrigerant inside.

[0062] It is understandable that the specific shape of the liquid inlet pipe 110 is not limited, and it can be a U-shaped, L-shaped, multi-stage wavy shape (see Figure 2-5 ) and other shapes.

[0063] like Figure 6 As shown, the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 refers to the angle between the projections of the central axis of the liquid inlet pipe 110 and the central axis of the first branch pipe 120 along the axial direction of the manifold 100 is set to angle a.

[0064] Optionally, the angle between the projection of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is greater than or equal to 145 degrees and less than or equal to 180 degrees. In this way, by setting the angle between the projection of the first branch pipe 120 along the axial direction of the manifold 100 and the projection of the liquid inlet pipe 110 to be between 145 degrees and 180 degrees, the contact point between the first branch pipe 120 and the manifold 100 can be closer to the side of the manifold 100 away from the liquid inlet pipe 110. Since the refrigerant enters the manifold 100 under the action of centrifugal force, more liquid-phase refrigerant is distributed on the side away from the liquid inlet pipe 110, thereby allowing more liquid-phase refrigerant to enter the first branch pipe 120, reducing the proportion of gas-phase refrigerant entering the first branch pipe 120, and making the diversion of the liquid-phase refrigerant more uniform.

[0065] Preferably, the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is equal to 160 degrees. In this way, by setting the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 to 160 degrees, the liquid phase refrigerant and the gas phase refrigerant entering the first branch pipe 120 can be balanced, the proportion of the liquid phase refrigerant and the gas phase refrigerant in each branch is kept balanced, and the uniformity of the refrigerant diversion is further improved.

[0066] Combination Figure 7-8 As shown, the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is set to 45 degrees ( Figure 7 ), and the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is set to 160 degrees ( Figure 8 ), according to the distribution ratio of gas-phase refrigerant and liquid-phase refrigerant in each branch, it can be seen that when the angle between the projection of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the collecting pipe 100 is set to 160 degrees, the distribution of gas-phase refrigerant and liquid-phase refrigerant in the first branch pipe 120 is more uniform, which can avoid excessive gas-phase refrigerant entering the first branch pipe 120 and affecting the heat exchange effect of the first branch pipe 120.

[0067] Optionally, the distance from the connection point of the first branch pipe 120 and the manifold 100 to the end of the manifold 100 connected to the liquid inlet pipe 110 is greater than or equal to 40 mm and less than or equal to 100 mm. In this way, the setting position of the first branch pipe 120 is controlled within 40 mm to 100 mm from the point where the liquid inlet pipe 110 connects to the manifold 100. After the refrigerant of this part enters the manifold 100 from the liquid inlet pipe 110, the gas phase refrigerant and the liquid phase refrigerant are properly mixed, and the uniformity of the refrigerant mixing is high. Therefore, setting the first branch pipe 120 within this position range can improve the uniformity of the gas phase refrigerant and the liquid phase refrigerant entering therein.

[0068] Optionally, the distance from the connection point of the first branch pipe 120 and the manifold 100 to the end of the manifold 100 connected to the liquid inlet pipe 110 is greater than or equal to 70 mm and less than or equal to 90 mm. In this way, the first branch pipe 120 is further set to be within 60 mm to 80 mm from the point where the liquid inlet pipe 110 connects to the manifold 100, so that the liquid-phase refrigerant and the gas-phase refrigerant can be mixed more evenly, the influence caused by the separation of the gas-phase refrigerant and the liquid-phase refrigerant caused by the centrifugal force can be better eliminated, and the uniformity of the refrigerant diversion can be improved.

[0069] Optionally, the distance between the connection point of the first branch pipe 120 and the manifold 100 and the end of the manifold 100 connected to the liquid inlet pipe 110 is 80 mm. In this way, the first branch pipe 120 is set at a distance of 80 mm from the point where the liquid inlet pipe 110 connects to the manifold 100, so that the gas phase and liquid phase of the refrigerant are mixed in the best state, the uniformity of the refrigerant mixing is improved, and the refrigerant diversion effect is improved.

[0070] Combination Figure 9-13 As shown, the first branch pipe 120 is located at a distance of 70 mm (eg, Fig. 9 ), 80 mm (such as Fig.10 ), 85 mm (such as Fig.11 ), 90 mm (such as Fig.12 ) and 100 mm (such as Fig.13 ). Compare the flow distribution of the gas-phase refrigerant and the liquid-phase refrigerant in the first branch pipe 120, the second branch pipe 140 and the third branch pipe 150. It can be seen that when the first branch pipe 120 is set at 80 mm from the liquid inlet pipe 110 connecting the manifold 100, the distribution of the gas-phase refrigerant and the liquid-phase refrigerant in each branch pipe is relatively more uniform.

[0071] Optionally, the distance from the connection point between the first branch pipe 120 and the manifold 100 to the end where the manifold 100 is connected to the liquid inlet pipe 110 is L, and the diameter of the arc-shaped portion of the liquid inlet pipe 110 is R, wherein L is greater than or equal to 2R and less than or equal to 4R. Preferably, L=2.6R. In this way, the diameter of the liquid inlet pipe 110 affects the centrifugal force during the liquid inlet process. By setting the distance between the connection point between the first branch pipe 120 and the manifold 100 and the connection point between the liquid inlet pipe 110 and the manifold 100 to between 2 and 4 times the diameter of the liquid inlet pipe 110, the influence of the refrigerant gas-liquid separation caused by the centrifugal force generated by the liquid inlet pipe 110 can be better eliminated, the refrigerant can be kept uniform and stable, and the diversion effect can be improved.

[0072] It can be understood that when the collecting pipe 100 is arranged vertically, the conduction direction of the liquid pipe valve component 130 is from bottom to top, and the first branch pipe 120 is arranged on the lower side of the liquid pipe valve component 130, and the second branch pipe 140 and the third branch pipe 150 are arranged on the upper side of the liquid pipe valve component 130.

[0073] When the heat exchanger is used as an evaporator, the refrigerant can be diverted from the first branch pipe 120, the second branch pipe 140 and the third branch pipe 150 in parallel. When the heat exchanger is used as a condenser, the refrigerant enters the collecting pipe 100 through the third branch pipe 150, and enters the second branch pipe 140 under the obstruction of the liquid pipe valve component 130, and flows through the first branch pipe 120 and returns to the collecting pipe 100, so that the first branch pipe 120, the second branch pipe 140 and the third branch pipe 150 are connected in series to form a flow path, thereby improving the efficiency of heating and cooling.

[0074] Optionally, the projections of the second branch pipe 140 and the third branch pipe 150 along the axial direction of the header pipe 100 overlap with the projections of the first branch pipe 120 along the axial direction of the header pipe 100. In this way, on the one hand, the first branch pipe 120, the second branch pipe 140 and the third branch pipe 150 can be kept on the same vertical plane, which is convenient for connecting the heat exchange flow path, and at the same time, the influence of gas-liquid separation caused by centrifugal force on the uniformity of the refrigerant entering the second branch pipe 140 and the third branch pipe 150 can be reduced, thereby improving the uniformity of the overall refrigerant diversion.

[0075] The original scheme (as shown in Table 1) and the improved scheme (as shown in Table 2) are used as a comparison to test the temperature of each branch outlet under the two working conditions of rated heating and intermediate heating when the heat exchanger is used as an evaporator. The original scheme is that the connection point between the second branch 140 and the manifold 100 is lower than the connection point between the third branch 150 and the manifold 100; the height of the other end of the second branch 140 is lower than the height of the other end of the third branch 150. The improved scheme is that the connection point between the second branch 140 and the manifold 100 is higher than the connection point between the third branch 150 and the manifold 100; the height of the other end of the second branch 140 is lower than the height of the other end of the third branch 150. By comparison, it can be seen that in the improved scheme, after the connection position of the second branch 140 and the third branch 150 relative to the manifold 100 is adjusted, the outlet temperatures of each branch are closer, indicating that the overall refrigerant diversion is more uniform.

[0076] Branch pipe Rated heating Intermediate heating The third branch outlet temperature (℃) -1.4 2.1 Second branch outlet temperature (℃) 4.8 3.7 First branch outlet temperature (℃) 4.7 6.4

[0077] Table 1

[0078] Branch Road Rated heating Intermediate heating The third branch outlet temperature (℃) -1.3 4.3 Second branch outlet temperature (℃) -1.7 5.1 First branch outlet temperature (℃) -1.9 3.6

[0079] Table 2

[0080] Optionally, the liquid pipe structure of the heat exchanger further includes: a fourth branch pipe, which is arranged on the side wall of the manifold 100 between the third branch pipe 150 and the liquid pipe valve component 130 .

[0081] The fourth branch pipe may be one or more. Thus, one or more fourth branch pipes may be selected according to different requirements for the number of diversions of the variable diversion, so that the refrigerant can be better divided into multiple paths under heating conditions, thereby improving the heat exchange effect of the overall heat exchanger.

[0082] Optionally, a connection hole is provided on the manifold 100, and the end of the first branch pipe 120 is butted against the connection hole and connected by welding. In this way, by directly welding the end of the first branch pipe 120 to the side wall of the manifold 100, the connection stability of the interface is maintained, and the structure is simplified to improve the consistency of the product.

[0083] Optionally, the connection between the third branch pipe 150 and the fourth branch pipe and the header 100 is the same as the connection between the first branch pipe 120 and the header 100. In this way, the branch pipes can be directly connected to the header 100 without using a tee, simplifying the structure and better improving product consistency.

[0084] Optionally, the diameter of the liquid inlet pipe 110 is smaller than that of the manifold 100, and one end of the liquid inlet pipe 110 is inserted into one end of the manifold 100. In this way, the diameter of the manifold 100 is set to be larger than that of the liquid inlet pipe 110. When the refrigerant is separated due to centrifugal force in the liquid inlet pipe 110, it can be fully mixed again in the manifold 100 with a larger volume, thereby improving the efficiency of the diversion when the manifold 100 is diverted to the first branch pipe 120, the second branch pipe 140, and the third branch pipe 150.

[0085] Optionally, the first branch pipe 120, the second branch pipe 140, the third branch pipe 150 and the fourth branch pipe have the same diameter. In this way, the uniformity of the refrigerant flow distribution can be further improved by using the first branch pipe 120, the second branch pipe 140, the third branch pipe 150 and the fourth branch pipe with the same diameter, and the uneven flow distribution caused by the difference in pipe diameter can be avoided.

[0086] Optionally, a closing structure 101 is provided at one end of the manifold 100, and one end of the liquid inlet pipe 110 is inserted into the closing structure 101 and welded to the closing structure 101. In this way, by using the closing structure 101 at one end of the manifold 100 to insert part of the liquid inlet pipe 110 into the inside thereof and welding, the stability of the connection between the two can be improved, and the risk of refrigerant leakage can be reduced.

[0087] Optionally, the other end of the header 100 is also provided with a closing structure, and one end of the second branch pipe 140 is inserted into the closing structure and welded to the closing structure. In this way, the stability of the connection between the header 100 and the second branch pipe 140 can also be improved.

[0088] Optionally, the manifold 100 and the closing structure 101 are integrally formed, so as to effectively simplify the structure, reduce interfaces, improve overall consistency, and reduce overall refrigerant leakage risk.

[0089] It can be understood that the closing structure 101 is a structure in which the diameter of the mouth of the manifold 100 is gradually reduced, and it can be directly formed by the manifold 100 through processes such as stamping or spinning.

[0090] Combination Fig.14 As shown, an embodiment of the present disclosure provides a variable split heat exchanger including the liquid pipe structure of the heat exchanger described above.

[0091] The variable split flow heat exchanger provided in this embodiment adopts the liquid pipe structure of the heat exchanger described above, and its effects are the same as those described above for the liquid pipe structure of the heat exchanger, which will not be described in detail here.

[0092] The disclosed embodiment also provides an air pipe structure that can be used for the aforementioned variable split flow heat exchanger.

[0093] Optionally, the air pipe structure includes an air collecting pipe 200, an air intake pipe 210, an air pipe valve component 220, and a first air pipe branch pipe 230. The air intake pipe 210 is connected to the air collecting pipe 200; the air pipe valve component 220 is arranged on the air collecting pipe 200, including an air valve conduction inlet end and an air valve conduction outflow end, and one side of the air valve conduction outflow end of the air collecting pipe 200 is connected to the air intake pipe 210, and the first air pipe branch pipe 230 is connected to one side of the air valve conduction outflow end of the air collecting pipe 200. Among them, the first air pipe branch pipe 230 is arranged at a first height of the air collecting pipe 200, and the air intake pipe 210 is arranged at a second height of the air collecting pipe 200, and the first height is greater than or equal to the second height.

[0094] In the air pipe structure provided by the embodiment of the present disclosure, the first air pipe branch 230 is arranged at a first height of the air collecting pipe 200, the air intake pipe 210 is arranged at a second height of the air collecting pipe 200, and the first height is greater than or equal to the second height, so that the height at which the air intake pipe 210 is arranged on the air collecting pipe 200 is flush with the first air pipe branch 230, or the height at which the air intake pipe 210 is arranged on the air collecting pipe 200 is lower than the first air pipe branch 230. In this way, when the variable split heat exchanger operates in the heating mode, the length of the flow path of the refrigerant flowing out of the second air pipe branch 240 and the third air pipe branch 250 is reduced, the difference in the refrigerant flow rate between the multiple heat exchange flow paths of the variable split heat exchanger is reduced, and the heat exchange efficiency of the variable split heat exchanger is improved.

[0095] It can be understood that when the variable split heat exchanger is in use, the collecting pipe 200 is vertically arranged, and the first height can be understood as the vertical distance from the bottom of the collecting pipe 200 to the setting position of the first air pipe branch 230 in the collecting pipe 200, and the second height can be understood as the vertical distance from the bottom of the collecting pipe 200 to the setting position of the air intake pipe 210 in the collecting pipe 200.

[0096] Optionally, the trachea valve component 220 divides the air collecting pipe 200 into a first air collecting pipe section 201 and a second air collecting pipe section 202, and the first air collecting pipe section 201 is a conducting section located in the conducting direction of the trachea valve component 220, located above the trachea valve component 220, and the second air collecting pipe section 202 is located below the trachea valve component 220. The second trachea branch pipe 240 and the third trachea branch pipe 250 are both arranged in the second trachea branch pipe 202. When the air conditioner is running in the heating mode, the refrigerant flowing out through the second trachea branch pipe 240 and the third trachea branch pipe 250 needs to flush the trachea valve component 220 and then flow upwards and flow out through the air inlet pipe 210.

[0097] Optionally, a first position and a second position are symmetrically arranged at a first height of the air collecting pipe 200 , wherein the first air pipe branch 230 is arranged at the first position, and the air intake pipe 210 is arranged at the second position.

[0098] When the first air pipe branch 230 is flush with the intake pipe 210, the first air pipe branch 230 and the intake pipe 210 are symmetrically arranged at the first height of the collecting pipe 200. This symmetrical arrangement can be understood as a symmetrical first position and a second position obtained by dividing the diameter of the collecting pipe 200 at the first height.

[0099] Optionally, a first position and a second position are symmetrically arranged at a first height of the air collecting pipe 200, wherein the first air pipe branch 230 is arranged at the first position, and the air intake pipe 210 is arranged below the second position.

[0100] When the air inlet pipe 210 is disposed at the lower part of the first air pipe branch 230, the air inlet pipe 210 can be disposed directly below the second position, thereby further reducing the length of the flow path of the refrigerant flowing out of the second air pipe branch 240 and the third air pipe branch 250. Optionally, the second air pipe branch 240 and the third air pipe branch 250 are disposed directly below the first position. In this way, the first air pipe branch 230, the second air pipe branch 240 and the third air pipe branch 250 are arranged in the same vertical direction, thereby improving the uniformity of the flow direction of the refrigerant flowing out of different air pipe branches.

[0101] Optionally, the difference between the first height of the first air pipe branch 230 and the second height of the air intake pipe 210 is less than or equal to a first preset difference. When the air intake pipe 210 is arranged below the first air pipe branch 230, the difference between the first air pipe branch 230 and the air intake pipe 210 in the vertical direction should not be too large, so that the refrigerant flowing out of the first air pipe branch 230 is conducive to flowing out through the air intake pipe 210. Optionally, the first preset difference is less than or equal to 20 mm.

[0102] Optionally, the manifold 200 includes a top of a capping structure, wherein the distance from the inlet pipe 210 to the top of the manifold 200 is greater than or equal to a first preset distance. Optionally, the first preset distance is greater than or equal to 20 mm, thus further improving the uniformity of the refrigerant amount between the multiple heat exchange paths.

[0103]

[0104] Table 3

[0105] Table 3 shows the mass flow ratios of the refrigerant in the first heat exchange path 310, the second heat exchange path 320 and the third heat exchange path 330 when different air pipe structures are used, where air pipe structure 1 is Fig.15 The trachea structure shown in the figure, in which the air inlet pipe 210 is located at the upper part of the first trachea branch pipe 230, the trachea structure 1 can be used as a comparative structure. The trachea structure 2 is the trachea structure provided in the embodiment of the present disclosure, which can be seen in Fig.16 . It can be seen from Table 3 that in the air pipe structure 1, the difference in refrigerant mass flow rate between the first heat exchange flow path 310 and the second heat exchange flow path 320 is about 21%, and in the air pipe structure 2 provided in the embodiment of the present disclosure, the difference in refrigerant mass flow rate between the first heat exchange flow path 310 and the second heat exchange flow path 320 is about 13%. It can be seen that the air pipe structure provided in the embodiment of the present disclosure has a significant technical effect of improving the uniformity of the refrigerant flow between different heat exchange flow paths. Optionally, the liquid pipe structure used in the variable split flow heat exchanger in the embodiment of the present disclosure is as follows: Figure 3 shown.

[0106] The variable split flow heat exchanger provided in the embodiment of the present disclosure also includes a plurality of heat exchange paths, including a first heat exchange path 310, a second heat exchange path 320, and a third heat exchange path 330. In this way, a complete variable split flow heat exchange structure can be formed, so that the variable split flow heat exchanger can have different flow paths under cooling and heating conditions, better balance the different requirements for refrigerant flow paths under cooling and heating conditions, and improve the heat exchange efficiency of the heat exchanger under cooling and heating conditions.

[0107] When the first air branch 230, the second air branch 240 and the third air branch 250 converge into the collecting pipe 200 at the same time, the air pipe valve component 220 can be turned on to directly discharge the refrigerant through the intake pipe 210, which is conducive to the side-by-side circulation of multiple heat exchange flow paths. On the contrary, when the refrigerant flows into the collecting pipe 200 from the intake pipe 210, the air pipe valve component 220 can be closed, so that the refrigerant first passes through the first air branch 230, then through the second air branch 240, and finally through the third air branch 250, forming a series of heat exchange flow paths, thereby having different numbers of heat exchange flow paths under cooling and heating conditions, better meeting the different requirements of cooling conditions and cooling conditions for the number of heat exchange flow paths, and improving the overall performance of the variable split heat exchanger.

[0108] In order to further improve the consistency of the product, the first tracheal branch pipe 230, the second tracheal branch pipe 240 and the third tracheal branch pipe 250 are directly connected to the side wall of the gas collecting pipe 200. The use of tees can be further reduced, thereby reducing the setting of interfaces, simplifying the overall structure, and making the overall consistency higher.

[0109] It can be understood that the connection mode between the first air pipe branch 230, the second air pipe branch 240 and the third air pipe branch 250 and the air collecting pipe 200 is the same as the connection mode between the first branch pipe 120 and the collecting pipe 100. Using the same connection mode can simplify the process requirements.

[0110] The first heat exchange flow path 310 is connected between the first branch pipe 120 and the third air pipe branch pipe 250, the second heat exchange flow path 320 is connected between the second branch pipe 140 and the second air pipe branch pipe 240, and the third heat exchange flow path 330 is connected between the third branch pipe 150 and the first air pipe branch pipe 230. In this way, by providing a plurality of heat exchange flow paths respectively correspondingly arranged between the branch pipes and the air pipe branches, different flow paths can be generated under cooling conditions and heating conditions, thereby improving the overall performance of the variable split heat exchanger.

[0111] Optionally, the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330 are all formed by a plurality of heat exchange tubes 300 connected in series, and the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330 are all provided in the same set of heat exchange fins 301. The overall consistency of the variable split heat exchanger can be maintained, and the same set of heat exchange fins 301 can be connected to further improve the heat exchange efficiency of the variable split heat exchanger.

[0112] Optionally, the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330 are arranged in sequence from bottom to top in the vertical direction. In this way, the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330 are vertically distributed, and the influence of gravity on the refrigerant can be used to further reduce the amount of refrigerant entering the third heat exchange flow path 330 under heating conditions, balance the influence of pressure loss caused by the need to pass through the trachea valve component 220 in the second heat exchange flow path 320 and the first heat exchange flow path 310, and improve the uniformity of the diversion.

[0113] Combination Fig.17 As shown, in the case where the variable split heat exchanger is used as an evaporator, the liquid refrigerant enters the collecting pipe 100 through the liquid inlet pipe 110, and the liquid pipe valve component 130 is turned on under the action of pressure. At this time, the refrigerant enters the first branch pipe 120, the second branch pipe 140 and the third branch pipe 150 at the same time, and passes through the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330 side by side, and then enters the collecting pipe 200 through the first air pipe branch pipe 230, the second air pipe branch pipe 240 and the third air pipe branch pipe 250 respectively. At this time, the air pipe valve component 220 in the collecting pipe 200 is also in a turned-on state. The refrigerant refluxes in the collecting pipe 200 and is discharged through the air inlet pipe 210, so that three parallel flow paths can be formed for heat exchange, which greatly reduces the pressure drop while ensuring the heat transfer coefficient, thereby increasing the system pressure and thus increasing the low-temperature heating capacity.

[0114] Combination Fig.18 As shown, in the case where the variable split heat exchanger is used as a condenser, the gas phase refrigerant enters the collecting pipe 200 through the inlet pipe 210. At this time, under the pressure of the refrigerant, the air pipe valve component 220 is in a non-conducting state. After the refrigerant enters the collecting pipe 200 and is in the upper half of the air pipe valve component 220, it flows into the third heat exchange flow path 330 through the first air pipe branch pipe 230 for heat exchange, and then flows into the collecting pipe 100 through the third branch pipe 150. At this time, the liquid pipe valve component 130 in the collecting pipe 100 is also in a non-conducting state under the action of pressure. The refrigerant continues to enter the second branch pipe 140 and flows into the second heat exchange flow path After heat exchange at 320, the heat exchanger flows into the lower half of the collecting pipe 200 at the lower side of the air pipe valve component 220 through the second air pipe branch 240, and continues to flow into the third air pipe branch 250 from this part, and after heat exchange at the first heat exchange flow path 310, it flows into the part of the collecting pipe 100 at the lower side of the liquid pipe valve component 130 through the first branch pipe 120, and finally flows out from the liquid inlet pipe 110, thereby forming a whole heat exchange flow path connecting the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330 in series, thereby accelerating the circulation and increasing the heat transfer coefficient, thereby improving the high-temperature cooling capacity.

[0115] In some embodiments, an air conditioner includes the variable split heat exchanger described above.

[0116] The effects of the air conditioner provided by the embodiment of the present disclosure are the same as those described above for the liquid pipe structure of the heat exchanger, and are not described in detail here.

[0117] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A trachea structure, characterized in that: include: Gas collecting pipe (200); An air intake pipe (210) is connected to the air collecting pipe (200); The air pipe valve component (220) is arranged on the air collecting pipe (200), and comprises an air valve conduction inlet end and an air valve conduction outlet end, and one side of the air valve conduction outlet end of the air collecting pipe (200) is connected to the air inlet pipe (210). The first air pipe branch (230) is connected to one side of the air valve conduction outflow end of the air collecting pipe (200). The first air pipe branch (230) is arranged at a first height of the air collecting pipe (200), the air intake pipe (210) is arranged at a second height of the air collecting pipe (200), and the first height is greater than or equal to the second height.

2. The tracheal structure according to claim 1, characterized in that: A first position and a second position are symmetrically arranged at a first height of the gas collecting pipe (200). The first tracheal branch pipe (230) is arranged at a first position, and the air intake pipe (210) is arranged at a second position.

3. The tracheal structure according to claim 1, characterized in that: A first position and a second position are symmetrically arranged at a first height of the gas collecting pipe (200). The first air pipe branch (230) is arranged at a first position, and the air intake pipe (210) is arranged below a second position.

4. The tracheal structure according to claim 3, characterized in that: The difference between the first height of the first tracheal branch pipe (230) and the second height of the air intake pipe (210) is less than or equal to a first preset difference.

5. The tracheal structure according to claim 3, characterized in that: Also includes: A second air pipe branch (240) is connected to one side of the air valve inflow end of the air collecting pipe (200); and The third air pipe branch (250) is connected to one side of the air valve conduction inflow end of the air collecting pipe (200).

6. The tracheal structure according to claim 5, characterized in that: The second tracheal branch tube (240) and the third tracheal branch tube (250) are arranged below the first position.

7. The tracheal structure according to any one of claims 1 to 6, characterized in that: The distance from the air intake pipe (210) to the top end of the air collecting pipe (200) is greater than or equal to a first preset distance.

8. A variable split flow heat exchanger, characterized in that: include: The trachea structure according to any one of claims 1 to 7; and, A plurality of heat exchange flow paths, each heat exchange flow path is connected to the gas collecting pipe (200) of the gas pipe structure through the gas pipe branch pipe.

9. The variable split heat exchanger according to claim 8, characterized in that: Also included is a liquid pipe structure, wherein the liquid pipe structure includes: A header (100); A second branch pipe (140) is used to communicate with a second heat exchange flow path (320) of the heat exchanger; The third branch pipe (150) is used to communicate with the third heat exchange flow path (330) of the heat exchanger, and the connection point between the second branch pipe (140) and the header (100) is higher than the connection point between the third branch pipe (150) and the header (100), wherein: The number of resistance components through which the refrigerant flows after flowing out of the second branch pipe (140) is greater than the number of resistance components through which the refrigerant flows after flowing out of the third branch pipe (150), or the refrigerant flows through at least one valve component after flowing out of the second branch pipe (140).

10. The variable split heat exchanger according to claim 9, characterized in that: Also includes: A first branch pipe (120) for communicating with a first heat exchange flow path (310) of the heat exchanger; and, The liquid pipe valve component (130) is arranged on the manifold (100), and comprises a liquid valve conduction inflow end and a liquid valve conduction outflow end. The first branch pipe (120) is arranged on the side of the liquid valve conduction inflow end of the manifold (100), and the second branch pipe (140) and the third branch pipe (150) are arranged on the side of the liquid valve conduction outflow end of the manifold (100).

11. The variable split heat exchanger according to claim 10, characterized in that: The angle between the projections of the liquid inlet pipe (110) and the first branch pipe (120) of the liquid pipe structure along the axial direction of the manifold (100) is greater than or equal to 90 degrees; and / or, The angle between the projections of the liquid inlet pipe (110) and the first branch pipe (120) along the axial direction of the manifold (100) is greater than or equal to 145 degrees and less than or equal to 180 degrees; and / or, The angle between the projections of the liquid inlet pipe (110) and the first branch pipe (120) along the axial direction of the manifold (100) is equal to 160 degrees; and / or, The liquid inlet pipe (110) is U-shaped.

12. The variable split heat exchanger according to claim 10, characterized in that: The distance from the connection point between the first branch pipe (120) and the manifold (100) to the end of the manifold (100) connected to the liquid inlet pipe (110) is greater than or equal to 30 mm and less than or equal to 100 mm.

13. The variable split heat exchanger according to claim 10, characterized in that: The plurality of heat exchange flow paths include a first heat exchange flow path (310), a second heat exchange flow path (320) and a third heat exchange flow path (330), The first heat exchange flow path (310) is connected between the first branch pipe (120) and the third airway branch pipe (250), the second heat exchange flow path (320) is connected between the second branch pipe (140) and the second airway branch pipe (240), and the third heat exchange flow path (330) is connected between the third branch pipe (150) and the first airway branch pipe (230).

14. An air conditioner, characterized in that: It comprises the variable split heat exchanger as claimed in any one of claims 8 to 13.

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