Header component, variable shunting heat exchanger and air conditioner

Abstract

The utility model relates to the technical field of household appliances, and discloses a header component of a heat exchanger. The liquid separation branch pipes communicate with the collecting pipe and comprise the first liquid separation pipe and the second liquid separation pipe, and the first liquid separation pipe is used for communicating with a third heat exchange flow path of the heat exchanger; the second liquid distribution pipe is used for being communicated with a second heat exchange flow path of the heat exchanger, and the second liquid distribution pipe is located below the first liquid distribution pipe. And the number of the resistance parts through which the refrigerant flowing out of the second liquid distribution pipe flows is larger than that of the resistance parts through which the refrigerant flowing out of the first liquid distribution pipe flows, or the refrigerant flowing out of the second liquid distribution pipe flows through at least one valve part. In this way, more refrigerants can flow to the second heat exchange flow path of the heat exchanger under the action of gravity. 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 electrical appliance technology, for example, to a header component, a variable split-flow heat exchanger and an air conditioner. Background Art

[0002] The heat exchanger of the air conditioner is usually provided with a header component to collect or divide the refrigerant in each heat exchange flow path of the heat exchanger. Usually, the header component of the heat exchanger includes an air pipe structure and a liquid pipe structure to collect or divide the refrigerant at both ends of each heat exchange flow path.

[0003] Taking the existing variable split heat exchanger as an example, the 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, the variable split heat exchanger uses valve pipe components such as a one-way valve, a solenoid valve or a liquid separation valve, so that the heat exchange flow path of the outdoor heat exchanger can change 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] When the air conditioner operates in heating mode, the refrigerant enters the header of the heat exchanger. However, the existing header distributes the refrigerant unevenly, 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 embodiments of the present disclosure provide a header component of a heat exchanger, a variable split heat exchanger and an air conditioner to solve the problem that the refrigerant distribution of the header component is uneven, which affects the heat exchange efficiency of the heat exchanger.

[0009] In some embodiments, the manifold component of the heat exchanger includes: a manifold; a branch pipe connected to the manifold, including a first branch pipe and a second branch pipe, the first branch pipe is used to communicate with the third heat exchange flow path of the heat exchanger; the second branch pipe is used to communicate with the second heat exchange flow path of the heat exchanger, wherein the second branch pipe is located below the first branch pipe, wherein the number of resistance components through which the refrigerant flows after flowing out of the second branch pipe is greater than the number of resistance components through which the refrigerant flows after flowing out of the first branch pipe, or the refrigerant flows through at least one valve component after flowing out of the second branch pipe.

[0010] In some embodiments, the variable split heat exchanger includes a header member of the heat exchanger as described above.

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

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

[0013] The manifold assembly includes a manifold and a liquid branch pipe, the liquid branch pipe is connected to the manifold, and includes a first liquid branch pipe and a second liquid branch pipe. The first liquid branch pipe is used to be connected to the third heat exchange flow path of the heat exchanger, and the second liquid branch pipe is used to be connected to the second heat exchange flow path of the heat exchanger. Moreover, the second liquid branch pipe is located below the first liquid branch pipe, wherein the number of resistance components through which the refrigerant flows after flowing out of the second liquid branch pipe is greater than the number of resistance components through which the refrigerant flows after flowing out of the first liquid branch pipe, or the refrigerant flows through at least one valve component after flowing out of the second liquid branch pipe.

[0014] The number of resistance components that the refrigerant flows through after flowing out of the second liquid dispensing tube is greater than the number of resistance components that the refrigerant flows through after flowing out of the first liquid dispensing tube, or the refrigerant flows through at least one valve component after flowing out of the second liquid dispensing tube. In this way, the pressure drop of the refrigerant after flowing out of the second liquid dispensing tube is relatively large when entering the second heat exchange flow path for heat exchange and then flowing out. Based on this, the amount of refrigerant required for the second heat exchange flow path is greater than the amount of refrigerant in the third heat exchange flow path, so that the heat exchange capacity of the second heat exchange flow path can be balanced with that of the third heat exchange flow path. In the scheme provided by the embodiment of the present disclosure, the second liquid dispensing tube is located below the first liquid dispensing tube, and more refrigerant in the collecting pipe can be diverted to the second liquid dispensing tube under the action of gravity. In this way, the refrigerant in the second heat exchange flow path corresponding to the second liquid dispensing tube is relatively more, which balances the liquid dispensing uniformity of the liquid dispensing branch pipe.

[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 structural schematic diagram of a manifold component provided by an embodiment of the present disclosure;

[0018] Figure 2 yes Figure 1 A magnified view of a selected portion;

[0019] Figure 3 yes Figure 1 another enlarged view of a selected portion;

[0020] Figure 4 yes Figure 1 another enlarged view of a selected portion;

[0021] Figure 5 yes Figure 1 another enlarged view of a selected portion;

[0022] Figure 6 yes Figure 1 another enlarged view of a selected portion;

[0023] Figure 7 yes Figure 1 another enlarged view of a selected portion;

[0024] Figure 8 is a structural schematic diagram of another manifold component provided by an embodiment of the present disclosure;

[0025] Fig. 9 yes Figure 8 A magnified view of a selected portion;

[0026] Fig.10 yes Figure 8 another enlarged view of a selected portion;

[0027] Fig.11 is a schematic diagram of the structure of a filter provided by an embodiment of the present disclosure;

[0028] Fig.12 is a schematic diagram of the structure of a discrete element provided by an embodiment of the present disclosure;

[0029] Fig.13 is a bottom view of a header component provided by an embodiment of the present disclosure;

[0030] Fig.14 is a refrigerant flow distribution diagram of each branch when the angle a is 45 degrees provided in an embodiment of the present disclosure;

[0031] Fig.15 is a refrigerant flow distribution diagram of each branch when the angle a is 160 degrees provided in an embodiment of the present disclosure;

[0032] Fig.16 is a schematic structural diagram of a variable split flow heat exchanger provided by an embodiment of the present disclosure;

[0033] Fig.17 is a schematic diagram of a trachea structure provided by an embodiment of the present disclosure;

[0034] Fig.18 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;

[0035] Fig.19 is a flow diagram of a refrigerant when the variable split flow heat exchanger provided in an embodiment of the present disclosure is used as a condenser;

[0036] Fig. 20 It is a schematic diagram of the structure of a variable split heat exchanger provided in an embodiment of the present disclosure.

[0037] Reference numerals:

[0038] 100, manifold; 101, first liquid inlet end; 102, first manifold section; 103, upper sealing end; 110, liquid inlet pipe; 111, separation pipe section; 112, first connection point; 113, outflow pipe section; 120, first branch pipe; 121, second connection point; 130, liquid pipe valve component; 140, main pipe section; 141, first main pipe connection end; 142, second main pipe connection end; 151, first liquid distribution pipe; 1511, first liquid distribution end; 1512, first connecting end; 1513, first arc-shaped curved pipe section; 1514, first straight pipe section; 152, second liquid distribution pipe; 1 521, second liquid separation end; 1522, second connecting end; 1523, second arc-shaped bend pipe section; 1524, second straight pipe section; 160, discrete element; 161, first mesh portion; 162, second mesh portion; 200, gas collecting pipe; 201, first gas collecting pipe section; 202, second gas collecting pipe section; 210, air inlet pipe; 220, air pipe valve component; 230, first air pipe branch; 240, second air pipe branch; 250, third air pipe branch; 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

[0039] 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.

[0040] 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.

[0041] 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.

[0042] 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 specific circumstances.

[0043] Unless otherwise stated, the term "plurality" means two or more.

[0044] 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.

[0045] 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.

[0046] 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.

[0047] The embodiment of the present disclosure provides a header component of a heat exchanger. Optionally, the header component of the heat exchanger provided by the embodiment of the present disclosure can be used as a liquid pipe structure of the heat exchanger.

[0048] The manifold assembly provided in the embodiment of the present disclosure includes a manifold 100 and a liquid branch pipe. The liquid branch pipe is connected to the manifold 100, and includes a first liquid branch pipe 151 and a second liquid branch pipe 152. The first liquid branch pipe 151 is used to communicate with the third heat exchange flow path 330 of the heat exchanger; the second liquid branch pipe 152 is used to communicate with the second heat exchange flow path 320 of the heat exchanger. Moreover, the second liquid branch pipe 152 is located below the first liquid branch pipe 151, wherein the number of resistance components through which the refrigerant flows after flowing out of the second liquid branch pipe 152 is greater than the number of resistance components through which the refrigerant flows after flowing out of the first liquid branch pipe 151, or the refrigerant flows through at least one valve component after flowing out of the second liquid branch pipe 152.

[0049] Optionally, the resistance component includes a heat exchange tube 300, a valve component, etc. The number of resistance components through which the refrigerant flows after flowing out of the second liquid distribution tube 152 includes the sum of the number of heat exchange tubes 300 in the second heat exchange flow path 320 and the number of valve components, and the number of resistance components through which the refrigerant flows after flowing out of the first liquid distribution tube 151 includes the number of heat exchange tubes 300 in the third heat exchange flow path 330. If the refrigerant flows out of the first liquid distribution tube 151 also flows through the valve component, then the number of resistance components through which the refrigerant flows after flowing out of the first liquid distribution tube 151 includes the sum of the number of heat exchange tubes 300 in the third heat exchange flow path 330 and the number of valve components.

[0050] Optionally, the number of valve components in the resistance component through which the refrigerant flows after flowing out of the second liquid-distributing tube 152 may be the number of valve components in the process from the second liquid-distributing end 1521 of the second liquid-distributing tube 152 to the flow out of the gas collecting tube 200. Similarly, the number of valve components in the resistance component through which the refrigerant flows after flowing out of the first liquid-distributing tube 151 may be the number of valve components in the process from the first liquid-distributing end 1511 of the first liquid-distributing tube 151 to the flow out of the gas collecting tube 200. Optionally, the number of heat exchange tubes 300 in the second heat exchange flow path 320 and the number of heat exchange tubes 300 in the third heat exchange flow path 330 are measured under the condition that the length of the heat exchange tubes 300 is the same. When the length of the heat exchange tubes 300 in the second heat exchange flow path 320 is different from the length of the heat exchange tubes 300 in the third heat exchange flow path 330, the heat exchange tubes 300 in the two heat exchange flow paths are converted to the same length before the number is counted. Optionally, the number of resistance components is counted when the heat exchanger is used as an evaporator.

[0051] When the resistance component flowing out of the second liquid dispensing tube 152 includes the first valve component, and the resistance component flowing out of the first liquid dispensing tube 151 includes the 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 is converted into the resistance generated by the second valve component and then the number is 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.

[0052] 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 liquid distribution pipe 152 flows through 3 heat exchange tubes and 1 one-way valve, and the refrigerant flowing out of the first liquid distribution pipe 151 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, then 1 one-way valve is converted into 3 heat exchange tubes, and then the number of resistance components is counted separately.

[0053] The refrigerant flowing out of the second liquid distribution pipe 152 flows through at least one valve component. Optionally, the valve component through which the second liquid distribution pipe 152 flows can be Fig.16 The air pipe valve component 220 in the heat exchanger. Optionally, the refrigerant flowing out of the first liquid distribution pipe 151 may not flow through the valve component. Optionally, the number of valve components through which the refrigerant flowing out of the second liquid distribution pipe 152 and the first liquid distribution pipe 151 flows is counted when the heat exchanger is used as an evaporator.

[0054] Optionally, the valve component includes a one-way valve, a solenoid valve, a three-way valve, etc.

[0055] Since the number of resistance components through which the refrigerant flows out of the second liquid distribution pipe 152 is greater than the number of resistance components through which the refrigerant flows out of the first liquid distribution pipe 151, or the refrigerant flows out of the second liquid distribution pipe 152 through at least one valve component, the second heat exchange flow path 320 located at the lower part needs to overcome more flow resistance when flowing out of the air pipe structure, that is, the pressure loss of the refrigerant flowing through the second heat exchange flow path 320 is greater than the pressure loss of the refrigerant flowing through the third heat exchange flow path 330. It can be seen that the second heat exchange flow path 320 requires a larger amount of refrigerant than the third heat exchange flow path 330 to balance the gravity, valve resistance, etc. that need to be overcome during the flow process.

[0056] In the disclosed embodiment, the second liquid distributing tube 152 is located below the first liquid distributing tube 151 , so that, under the action of gravity, more refrigerant can flow into the second heat exchange path 320 through the second liquid distributing tube 152 , thereby improving the uniformity of the refrigerant flow in the second heat exchange path 320 and the third heat exchange path 330 .

[0057] Optionally, the liquid distribution branch pipe further includes a main pipe section 140 , the main pipe section 140 is connected to the manifold 100 , and the first liquid distribution pipe 151 and the second liquid distribution pipe 152 are respectively connected to the main pipe section 140 .

[0058] In this way, the refrigerant in the manifold 100 flows into the first liquid distributor 151 and the second liquid distributor 152 respectively after being divided by the main section 140. Since the second liquid distributor 152 is arranged at the lower part of the first liquid distributor 151, under the action of gravity, more liquid refrigerant will flow into the second liquid distributor 152, and then flow into the second heat exchange flow path 320 located at the lower part. That is, the arrangement of the liquid distributor branch pipe makes the amount of refrigerant distributed to the second heat exchange flow path 320 greater than that to the third heat exchange flow path 330, so that the second heat exchange flow path 320 can have more refrigerant to overcome the resistance such as gravity during the flow process, thereby improving the heat exchange uniformity of each heat exchange flow path of the entire heat exchanger.

[0059] Optionally, the manifold 100 and the liquid-distributing branch pipe are integrally formed, or the main pipe section 140 of the liquid-distributing branch pipe, the first liquid-distributing pipe 151 and the second liquid-distributing pipe 152 are integrally formed.

[0060] Optionally, the main pipe section 140 includes a first main pipe connecting end 141 connected to the collecting pipe 100, and a second main pipe connecting end 142 connected to the first liquid distributing pipe 151 and the second liquid distributing pipe 152, wherein the distance between the first main pipe connecting end 141 and the second main pipe connecting end 142 is H1, 10mm≤H1≤40mm.

[0061] Optionally, the second liquid-distributing end 1521 of the second liquid-distributing tube 152 is disposed at the lower portion of the second main pipe connecting end 142, and the first liquid-distributing end 1511 of the first liquid-distributing tube 151 is disposed at the upper portion of the second main pipe connecting end 142. That is, relative to the second main pipe connecting end 142, the first liquid-distributing end 1511 is located at the upper portion, and the second liquid-distributing end 1521 is located at the lower portion. The first liquid-distributing end 1511, the second main pipe connecting end 142, and the second liquid-distributing end 1521 are not necessarily limited to be on the same vertical line.

[0062] After passing through the main pipe section 140, the refrigerant flows into the first liquid distributing pipe 151 and the second liquid distributing pipe 152 respectively. At this time, the horizontal length of the main pipe section 140 should not be too long, otherwise, too much refrigerant will be diverted to the second liquid distributing pipe 152 under the action of gravity, so that too much refrigerant flows into the second heat exchange flow path 320, and too little refrigerant flows into the third heat exchange flow path 330. In the embodiment of the present disclosure, 10mm≤H1≤40mm, such as Figure 3 As shown, in this way, while increasing the refrigerant distribution amount of the second heat exchange flow path 320, the refrigerant amount in the third heat exchange flow path 330 will not be too small, thereby improving the uniformity of the refrigerant flow between the heat exchange flow paths of the heat exchanger.

[0063] Optionally, the first liquid distribution tube 151 includes a first connection end 1512 for connecting to the third heat exchange flow path 330, wherein the shortest distance between the first connection end 1512 and the outer wall of the collecting tube 100 is H2, 15mm≤H2≤90mm; and / or, the second liquid distribution tube 152 also includes a second connection end 1522 for connecting to the second heat exchange flow path 320, wherein the shortest distance between the second connection end 1522 and the outer wall of the collecting tube 100 is H3, 15mm≤H3≤90mm.

[0064] The first connection end 1512 can be understood as the first expansion connection end where the first liquid distributing tube 151 is expanded and connected to the third heat exchange flow path 330 . Similarly, the second connection end 1522 can be understood as the second expansion connection end where the second liquid distributing tube 152 is expanded and connected to the second heat exchange flow path 320 .

[0065] Typically, the heat exchange tubes 300 of the heat exchange flow path of the heat exchanger are connected to the branch pipes of the manifold assembly by expansion welding, and during expansion welding, a closing structure is provided at the connection between the heat exchange tubes 300 and the branch pipes to improve the connection stability between the two. The shortest distance between the first connection end 1512 or the second connection end 1522 and the outer wall of the manifold 100 should not be too large, otherwise, too much refrigerant will flow into the second heat exchange flow path 320 through the second liquid distributor 152 under the action of gravity, and the third heat exchange flow path 330 located at the top will obtain too little refrigerant, thereby reducing the uniformity of the refrigerant amount between the heat exchange flow paths of the heat exchanger. Figure 4 As shown, the shortest distance between the first connection end 1512 and the outer wall of the manifold 100 is H2, 15mm≤H2≤90mm, further, 35mm≤H2≤70mm. Similarly, the shortest distance between the second connection end 1522 and the outer wall of the manifold 100 is H3, 15mm≤H3≤90mm, further, 35mm≤H3≤70mm. In this way, while increasing the refrigerant distribution amount of the second heat exchange flow path 320, the refrigerant amount in the third heat exchange flow path 330 will not be too small. The uniformity of the refrigerant flow between the heat exchange flow paths of the heat exchanger is improved.

[0066] Optionally, the outer diameter of the main pipe section 140 is greater than or equal to 4 mm, and less than or equal to 7 mm. Optionally, the outer diameter of the main pipe section 140 may be 4 mm or 5 mm, etc. The refrigerant flowing in the manifold 100 has the power to flow upward during the flow process, so more refrigerant will flow upward along the manifold 100, and then flow to the liquid separation branch for liquid separation. In this way, the amount of refrigerant distributed to the first branch pipe 120 located at the lower part of the manifold 100 is reduced. In the disclosed embodiment, the outer diameter of the main pipe section 140 should not be too large, so as not to cause too much refrigerant to enter the liquid separation branch, thereby ensuring the refrigerant distribution amount of the first branch pipe 120, and thereby improving the liquid separation uniformity of the entire manifold component.

[0067] Optionally, the outer diameter of the header 100 is greater than or equal to 9 mm and less than or equal to 13 mm. In order to increase the flow rate of the refrigerant in the header 100, the outer diameter of the header 100 should not be too large. Optionally, the outer diameter of the header 100 can be 9 mm, 10 mm or 12 mm, etc.

[0068] Optionally, the first liquid distribution tube 151 includes a first arc-shaped curved pipe section 1513 and a first straight pipe section 1514 that are interconnected, and the second liquid distribution tube 152 includes a second arc-shaped curved pipe section 1523 and a second straight pipe section 1524 that are interconnected, wherein the first arc-shaped curved pipe section 1513 and the second arc-shaped curved pipe section 1523 are connected, and the first straight pipe section 1514 and the second straight pipe section 1524 extend in parallel and in the same direction.

[0069] Optionally, the first arc-shaped bend pipe segment 1513 and the second arc-shaped bend pipe segment 1523 are combined to form a U-shape; and / or, the projections of the first straight pipe segment 1514 and the second straight pipe segment 1524 in the vertical direction overlap; and / or, the horizontal distance L2 between the two ends of the first arc-shaped bend pipe segment 1513 is less than or equal to the length of the first straight pipe segment 1514L1, and the horizontal distance L4 between the two ends of the second arc-shaped bend pipe segment 1523 is less than or equal to the length of the second straight pipe segment 1524L3. Compared with the first straight pipe section 1514, the horizontal distance between the two ends of the first arc-shaped bend pipe section 1513 is shorter. Similarly, compared with the second straight pipe section 1524, the horizontal distance between the two ends of the second arc-shaped bend pipe section 1523 is shorter. In this way, the curvature of the first arc-shaped bend pipe section 1513 and the second arc-shaped bend pipe section 1523 are both larger. The refrigerant flowing out of the main pipe section 140 will form a centrifugal acceleration effect through the first arc-shaped bend pipe section 1513 and the second arc-shaped bend pipe section 1523, further increasing the flow rate of the refrigerant in the heat exchanger, thereby improving the heat exchange efficiency of the heat exchanger.

[0070] Optionally, the distance between the first straight pipe section 1514 and the second straight pipe section 1524 is H4, 15 mm ≤ H4 ≤ 30 mm.

[0071] The distance between the first straight pipe section 1514 and the second straight pipe section 1524 can also be the vertical distance between the first liquid separation end 1511 and the second liquid separation end 1521. 15mm≤H4≤30mm, further, 17mm≤H4≤26mm. The third heat exchange flow path 330 includes a first heat exchange tube connected to the first liquid separation end 1511, and the second heat exchange flow path 320 includes a second heat exchange tube connected to the second liquid separation end 1521, wherein the first heat exchange tube and the second heat exchange tube are arranged adjacent to each other. In this way, the vertical distance between the first liquid separation end 1511 and the second liquid separation end 1521 is approximately the width of a U-shaped hairpin tube, that is, the vertical spacing between the first liquid separation end 1511 and the second liquid separation end 1521 is not large, so that while increasing the refrigerant distribution amount of the second heat exchange flow path 320, the amount of refrigerant in the third heat exchange flow path 330 is not too small. The uniformity of the refrigerant flow between the heat exchange paths of the heat exchanger is improved. Optionally, H4 can be 17.5 mm, 19.5 mm, 21 mm or 25 mm. Optionally, in H4, the middle of the first liquid separation end 1511 and the middle of the second liquid separation end 1521 can be measured respectively, such as Figure 5 shown.

[0072] Optionally, the vertical distance H6 between the first liquid separation end 1511 and the second main pipe connecting end 142 is greater than or equal to 8 mm, and less than or equal to 15 mm; and / or, the vertical distance H7 between the second liquid separation end 1521 and the second main pipe connecting end 142 is greater than or equal to 8.5 mm, and less than or equal to 16 mm; and / or, the vertical distance between the first liquid separation end 1511 and the second main pipe connecting end 142 is greater than or equal to the vertical distance between the second liquid separation end 1521 and the second main pipe connecting end 142. In the vertical direction, the second main pipe connecting end 142 is roughly arranged between the first liquid separation end 1511 and the second liquid separation end 1521, or the vertical spacing between the first liquid separation end 1511 and the second main pipe connecting end 142 is slightly greater than the vertical spacing between the second liquid separation end 1521 and the second main pipe connecting end 142, so that more refrigerant flows into the second heat exchange flow path 320.

[0073] Optionally, the header 100 includes an upper sealed end 103 , wherein the first main pipe connecting end 141 and the upper sealed end 103 are spaced apart along the length direction of the header 100 .

[0074] The upper end of the manifold 100 is provided with an upper sealed end 103, and the flow of the refrigerant in the manifold has an upward flow tendency. During the upward flow of the refrigerant, a part of the refrigerant flows into the first branch pipe for liquid separation, and the other part of the refrigerant continues to flow upward to the upper sealed end 103 of the manifold 100 under the action of the flow pressure. The gas-liquid two-phase refrigerant will flow back after rushing to the upper sealed end 103, and the refluxed refrigerant will mix with the refrigerant rushing upward. In this way, the setting of the upper sealed end 103 improves the gas-liquid mixing uniformity of the gas-liquid two-phase refrigerant, thereby improving the certainty of the amount of refrigerant flowing into the liquid separation branch pipe.

[0075] Optionally, the distance between the first main pipe connecting end 141 and the upper sealing end 103 is H5, wherein H5 ≥ 20 mm. Figure 5 As shown. In this way, the mixing effect of the gas-liquid two-phase refrigerant between the first main pipe connecting end 141 and the upper sealing end 103 is improved. Optionally, in H5, the middle of the first main pipe connecting end 141 can be measured.

[0076] Optionally, the main pipe section 140 is arranged in the horizontal direction; or, the angle between the main pipe section 140 and the horizontal direction is less than or equal to the first preset angle, and the first main pipe connecting end 141 of the main pipe section 140 is located above the second main pipe connecting end 142, so that the main pipe section 140 is inclined downward from the manifold 100 to the branch pipe. Optionally, the first preset angle is less than or equal to 15 degrees, so that the main pipe section 140 is arranged in a slightly inclined shape, so that the refrigerant can flow toward the second liquid distribution pipe 152 under the action of gravity, thereby increasing the amount of refrigerant flowing into the second heat exchange flow path 320.

[0077] Optionally, the main pipe section 140 is arranged in the horizontal direction so that the liquid distribution branch pipe is a Y-shaped three-way pipe arranged horizontally.

[0078] The liquid distribution branch pipe includes a Y-type three-way pipe. Figures 1 to 7 As shown, the main pipe section 140, the first liquid distributing pipe 151 and the second liquid distributing pipe 152 of the Y-shaped three-way pipe are all extended in the horizontal direction, and the main pipe section 140, the first liquid distributing pipe 151 and the second liquid distributing pipe 152 are arranged in the same vertical plane, and further, the first straight pipe section 1514 of the first liquid distributing pipe 151 is parallel to the second straight pipe section 1524 of the second liquid distributing pipe 152. In the embodiment of the present disclosure, the Y-shaped three-way pipe is used as the first branch pipe, which improves the versatility of the first branch pipe.

[0079] Optionally, the angle between the main pipe section 140 and the horizontal direction is less than or equal to a first preset angle, and the first main pipe connecting end 141 of the main pipe section 140 is located above the second main pipe connecting end 142. Optionally, the first preset angle is less than or equal to 15°.

[0080] Optionally, the header member is further provided with discrete elements 160 .

[0081] Optionally, the discrete element 160 is disposed in a path where the refrigerant flows, and is used to mix the refrigerant flowing into the manifold 100 .

[0082] The header is a flow collecting and diverting component of the heat exchanger. The refrigerant flowing into the header can be diverted through multiple branch pipes and then flow into different heat exchange paths of the heat exchanger. Among them, the uniformity, certainty and stability of liquid separation are important indicators for the header to play a diverting role.

[0083] The manifold component provided by the embodiment of the present disclosure is provided with a discrete element 160 in the path of the refrigerant circulation to disperse the gaseous refrigerant and the liquid refrigerant flowing into the manifold, and the gas-liquid two-phase refrigerant is dispersed at the discrete element 160, thereby improving the uniformity of the gas-liquid mixing of the gas-liquid two-phase refrigerant. In this way, the certainty and accuracy of the refrigerant distribution amount when the manifold distributes the refrigerant each time are improved, and the liquid separation effect of the manifold component is improved, thereby improving the heat exchange efficiency of the heat exchanger and the operating stability of the air conditioner.

[0084] Optionally, the manifold assembly further includes a liquid inlet pipe 110. The liquid inlet pipe 110 includes a separation pipe section 111 and an outflow pipe section 113 that are interconnected, the outflow pipe section 113 is connected to the manifold 100, and the discrete element 160 is disposed in the outflow pipe section 113. The refrigerant enters the outflow pipe section 113 after passing through the separation pipe section 111, and enters the manifold 100 through the discrete element 160.

[0085] Optionally, the separation pipe section 111 of the liquid inlet pipe 110 may be a U-shaped pipe. The refrigerant flows in the U-shaped separation pipe section 111, which has a certain centrifugal and accelerating effect, and is conducive to liquid separation between different branch pipes after entering the manifold 100.

[0086] Taking the U-shaped separation pipe section 111 of the liquid inlet pipe 110 as an example, after the refrigerant passes through the U-shaped separation pipe section 111, due to the centrifugal force, the liquid refrigerant in the two-phase refrigerant gathers on the outside of the U-shaped curved wall, and the gaseous refrigerant gathers in the middle of the U-shaped curved wall, forming an unevenly mixed gas-liquid two-phase state, which affects the certainty of the amount of refrigerant entering each branch pipe, especially the certainty of the amount of refrigerant entering the first branch pipe 120 close to the first liquid inlet end 101. For the first branch pipe 120, it may even happen that under the same operating conditions, the amount of refrigerant flowing into the first branch pipe 120 at different times varies greatly, affecting the heat exchange effect of the heat exchanger.

[0087] It can be understood that the specific shape of the liquid inlet pipe 110 can also be an L-shape, a multi-stage wavy shape, etc.

[0088] The manifold assembly provided in the embodiment of the present disclosure and the setting of the discrete elements 160 can break up the gas-liquid two-phase refrigerant flowing out of the liquid inlet pipe 110, thereby improving the uniformity of the mixed flow of the gas-liquid two-phase refrigerant, thereby reducing the difference in the amount of refrigerant flowing into the first branch pipe 120 at different times under the same working condition, improving the certainty of the amount of refrigerant flowing into the first branch pipe 120, and simultaneously improving the stability of the amount of refrigerant flowing into other branches, thereby improving the heat exchange stability of the heat exchanger.

[0089] Optionally, the discrete element 160 may be a plate-like structure with holes, or other structures, and the material of the discrete element 160 may be metal or fabric. Optionally, the discrete element 160 has a plurality of liquid equalizing holes to break up and mix the gas-liquid two-phase refrigerant. Optionally, the discrete element 160 includes a multi-layer liquid equalizing structure, and each layer of the liquid equalizing structure is provided with liquid equalizing holes, thereby improving the mixing effect of the discrete element 160 on the gas-liquid two-phase refrigerant. Optionally, the liquid equalizing holes in the multi-layer liquid equalizing structure are staggered with each other. Optionally, the liquid equalizing holes of the discrete element 160 are greater than or equal to 5 mm to prevent the liquid equalizing holes from throttling the refrigerant.

[0090] Optionally, the separation pipe segment 111 is an arc-shaped structure, the curvature of the arc-shaped structure is r, and the distance between the separation pipe segment 111 and the first connecting point 112 of the outflow pipe segment 113 and the discrete element 160 is H, wherein the larger r is, the larger H is.

[0091] The greater the curvature r of the separation pipe section 111, the greater the arc of the separation pipe section 111, and thus the greater the centrifugal effect on the refrigerant. At this time, the distance H between the first connection point 112 between the separation pipe section 111 and the outflow pipe section 113 and the discrete element 160 can be set according to the size of the curvature r of the arc structure, so that the discrete element 160 is set at a better discrete position. In the embodiment of the present disclosure, the greater the r, the greater the H, which improves the discrete effect of the discrete element 160 on the refrigerant, while at the same time, the discrete element 160 does not excessively block the flow of the refrigerant.

[0092] Optionally, the distance between the bottom end of the discrete element 160 and the bottom end of the separation tube section 111 is h1, where h1≥50 mm. Fig. 9 As shown, h1≥50mm, so that the discrete element 160 breaks up the refrigerant after centrifugal acceleration while ensuring that the centrifugal acceleration of the separation pipe section 111 and the refrigerant is fully exerted, so that the setting of the discrete element 160 does not increase the resistance to the refrigerant separated by the separation pipe section 111.

[0093] Optionally, the distance between the first connection point 112 between the separation pipe section 111 and the outflow pipe section 113 and the bottom end of the discrete element 160 is h2, wherein h2≥5mm. In this way, the setting of the discrete element 160 does not increase the resistance to the refrigerant after separation and acceleration by the separation pipe section 111. Optionally, h2≥10mm, or h2≥20mm.

[0094] Optionally, the discrete element 160 includes a filter. The filter-type discrete element 160 improves the uniformity of the mixed flow of the gas-liquid two-phase refrigerant. Optionally, the shape of the filter mesh hole includes a polygonal hole, such as Fig.12 As shown in C and D, or, the shape of the filter mesh is irregular, such as Fig.12 As shown in B. It can be understood that the filter mesh is the aforementioned liquid balancing hole.

[0095] The filter net includes a first net portion 161 and a second net portion 162. The first net portion 161 is connected to the inner wall of the outflow pipe section 113, and the second net portion 162 is connected to the first net portion 161, and covers the first net portion 161. A preset distance is set between the second net portion 162 and the inner wall of the outflow pipe section 113. It can be understood that at least part of the second net portion 162 is not connected to the inner wall of the outflow pipe section 113, or the entire outer edge of the second net portion 162 is not connected to the inner wall of the outflow pipe section 113. In this way, the mixing effect of the filter net on the gas-liquid two-phase refrigerant is improved. Optionally, the first net portion 161 is a horizontal mesh, such as Fig.12 The second net portion 162 includes an arc shape A, an inverted basin shape B, an inverted angle shape C or an irregular shape, such as Fig.11 shown.

[0096] Optionally, a hollow portion is provided between the first net portion 161 and the second net portion 162. The provision of the hollow portion reduces the pressure loss of the refrigerant flow while the first net portion 161 and the second net portion 162 simultaneously play a mixing role.

[0097] Optionally, the aperture of at least part of the mesh of the second mesh 162 is smaller than the aperture of the mesh of the first mesh 161. For the filter mesh structure in which the second mesh 162 is connected to the upper part of the first mesh 161, when the refrigerant flows through the second mesh 162, since the area of ​​the second mesh 162 is larger than the area of ​​the first mesh 161, the second mesh 162 has a greater mixing effect on the refrigerant, and the refrigerant will form a partial reflux at the second mesh 162. The aperture of at least part of the mesh of the second mesh 162 is smaller than the aperture of the mesh of the first mesh 161, or the aperture of all the mesh of the second mesh 162 is smaller than the aperture of the mesh of the first mesh 161. In this way, the mixing effect of the filter on the refrigerant is further improved.

[0098] Optionally, the manifold component is provided with a liquid branch pipe and a discrete element 160 at the same time. The liquid branch pipe is provided at the upper part of the manifold 100, near the upper sealing end 103, and the discrete element 160 is provided at the lower part of the first liquid inlet end 101 of the manifold 100. That is, in the manifold component provided in the embodiment of the present disclosure, the liquid branch pipe is provided at the upper part, and the discrete element 160 is provided at the lower part, thereby improving the uniformity of the refrigerant distribution to each heat exchange flow path of the heat exchanger. If only the discrete element 160 is provided, the discrete element 160 can play a role in mixing the gas-liquid two-phase refrigerant, but the distance from the liquid branch pipe to the discrete element 160 is relatively far, and the distance between the two may be greater than the distance of the vertical arrangement of ten heat exchange tubes in the heat exchanger. For a larger heat exchanger, the distance between the two may even be greater than the distance of the vertical arrangement of fifteen heat exchange tubes in the heat exchanger. It can be seen that the refrigerant after mixing through the discrete element 160 needs to flow upward for a long distance before reaching the liquid separation branch. At this time, the connection positions of the third heat exchange flow path 330 and the second heat exchange flow path 320 of the heat exchanger with the manifold 100 are extremely important, and when the connection positions of the third heat exchange flow path 330 and the second heat exchange flow path 320 with the manifold 100 are different, the difference in the amount of refrigerant distributed between the two is large. In the disclosed embodiment, a liquid separation branch is used to simultaneously distribute refrigerant to the third heat exchange flow path 330 and the second heat exchange flow path 320, which further improves the certainty of the amount of refrigerant distributed between the two.

[0099] Optionally, the manifold component is provided with a liquid branch pipe, a discrete element 160 and a liquid pipe valve component 130 at the same time. The liquid branch pipe is provided at the upper part of the manifold 100, near the upper sealing end 103. The discrete element 160 is provided at the lower part of the first liquid inlet end 101 of the manifold 100. The liquid pipe valve component 130 is provided between the liquid branch pipe and the discrete element 160. The discrete element 160 improves the mixing effect of the gas-liquid two-phase refrigerant. After the refrigerant is evenly mixed, a part flows into the first branch pipe 120, and the other part flows upward to the liquid pipe valve component 130. Compared with the manifold 100, the inner diameter of the liquid pipe valve component 130 is thinner. In this way, the refrigerant will produce an acceleration effect after flowing through the liquid pipe valve component 130. The accelerated refrigerant can flow more smoothly to the liquid branch pipe at a relatively upper position. In this way, the fluidity of the refrigerant in the manifold component is improved. At the same time, the arrangement of the liquid pipe valve component 130 can block the upward flow of part of the refrigerant, so that the first branch pipe 120 located at the lower part can be allocated with the refrigerant it needs. It can be seen that the manifold component provided in the embodiment of the present disclosure can balance the refrigerant amount distribution of the first heat exchange flow path 310, the second heat exchange flow path 320 and the third heat exchange flow path 330, thereby improving the overall heat exchange effect of the heat exchanger.

[0100] Optionally, the manifold component further includes a first branch pipe 120, which is connected to the manifold 100, wherein the distance between the first connection point 112 between the separation pipe section 111 and the outflow pipe section 113 and the second connection point 121 between the first branch pipe 120 and the manifold 100 is e, e≥20mm. In this way, the refrigerant after being dispersed by the discrete elements 160 flows into the first branch pipe 120. Optionally, e≥30mm.

[0101] Optionally, the angle between the separation pipe section 111 of the liquid inlet pipe 110 and the projection of the first branch pipe 120 along the axial direction of the collecting pipe 100 is greater than or equal to 90 degrees; and / or, the angle between the separation pipe section of the liquid inlet pipe 110 and the projection of the first branch pipe 120 along the axial direction of the collecting pipe 100 is greater than or equal to 145 degrees and less than or equal to 180 degrees; and / or, the angle between the separation pipe section of the liquid inlet pipe 110 and the projection of the first branch pipe 120 along the axial direction of the collecting pipe 100 is equal to 160 degrees; and / or, the separation pipe section 111 of the liquid inlet pipe 110 is U-shaped.

[0102] like Fig.13 As shown, the angle between the separation pipe section 111 of the liquid inlet pipe 110 and the projection of the first branch pipe 120 along the axial direction of the collecting pipe 100 refers to the angle between the central axis of the liquid inlet pipe 110 and the projection of the central axis of the first branch pipe 120 along the axial direction of the collecting pipe 100 is set to angle a.

[0103] Optionally, the angle between the projection of the separation pipe section 111 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.

[0104] Preferably, the angle between the separation pipe section 111 of the liquid inlet pipe 110 and the projection of 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 projection 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.

[0105] The angle between the projection of the separation pipe section 111 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 ( Fig.14 ), 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 ( Fig.15 ), 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.

[0106] Optionally, the distance from the second connection point 121 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. 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 relatively high. Therefore, the first branch pipe 120 is set within this position range, which can improve the uniformity of the gas phase refrigerant and the liquid phase refrigerant entering therein.

[0107] Optionally, the distance from the second connection point 121 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 70 mm and less than or equal to 90 mm. In this way, the first branch pipe 120 is further arranged 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.

[0108] Optionally, the distance between the second connection point 121 between the first branch pipe 120 and the manifold 100 and the end where the manifold 100 is 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 is connected 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 further improved.

[0109] Optionally, the manifold 100 includes a first manifold section 102 located at the lower part of the liquid pipe valve component 130, wherein the vertical distance between the first branch pipe 120 and the second connection point 121 of the manifold 100 to the top of the first manifold section 102 is greater than or equal to 15 mm and less than or equal to 40 mm. The liquid pipe valve component 130 has a liquid blocking function, and the vertical distance between the first branch pipe 120 and the second connection point 121 of the manifold 100 to the top of the first manifold section 102 is limited to 15 to 40 mm. In this way, the distance between the pipe mouth of the first branch pipe 120 and the liquid pipe valve component 130 is closer, and the liquid pipe valve component 130 has a better liquid blocking function, which can allow more refrigerant to enter the first branch pipe 120, thereby improving the uniformity of refrigerant distribution between the heat exchange flow paths of the variable split heat exchanger. Optionally, the second connection point 121 between the first branch pipe 120 and the manifold 100 can be measured at the center position of the first branch pipe 120. Compared with other variable flow split heat exchangers, the variable flow split heat exchanger provided in the embodiment of the present disclosure does not have a liquid distributor. The liquid pipe valve component 130 provided in the embodiment of the present disclosure can block liquid and accelerate the flow of refrigerant while playing a unidirectional conduction role, thereby improving the uniformity of the distribution of refrigerant among multiple heat exchange flow paths.

[0110] Optionally, the distance from the second connection point 121 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 second connection point 121 between the first branch pipe 120 and the manifold 100 relative to 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.

[0111] Optionally, the manifold 100 and the closing structure provided therewith are integrally formed, so as to effectively simplify the structure, reduce interfaces, improve the overall consistency, and reduce the overall risk of refrigerant leakage.

[0112] It can be understood that the closing structure is a structure in which the diameter of the mouth of the manifold 100 gradually decreases, and it can be directly formed by the manifold 100 through processes such as stamping or spinning.

[0113] Combination Fig.16 As shown, an embodiment of the present disclosure provides a variable split heat exchanger including: the above-mentioned header component of the heat exchanger.

[0114] The variable split heat exchanger provided in this embodiment adopts the above-mentioned header component of the heat exchanger, and its effects are the same as those described above for the effects of the header component of the heat exchanger, which will not be repeated here.

[0115] The disclosed embodiment also provides an air pipe structure of a variable split heat exchanger.

[0116] Optionally, the trachea structure includes an air collecting pipe 200, an air intake pipe 210, an trachea valve component 220, a first trachea branch 230, a second trachea branch 240 and a third trachea branch 250, the trachea valve component 220 is connected to the air collecting pipe 200, and the trachea valve component 220 includes 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, the first trachea branch 230 is connected to one side of the air valve conduction outflow end, and the second trachea branch 240 and the third trachea branch 250 are connected to one side of the air valve conduction inlet end.

[0117] Optionally, the air pipe structure of the variable split heat exchanger includes an air collecting pipe 200, an air inlet pipe 210, an air pipe valve component 220, a first air pipe branch pipe 230, a second air pipe branch pipe 240 and a third air pipe branch pipe 250. The air inlet pipe 210 is connected to the air collecting pipe 200, and the air pipe valve component 220 is connected to the air collecting pipe 200. Optionally, the air pipe valve component 220 includes a one-way valve or a solenoid valve, and its conduction direction is one-way conduction from the other side to the side where the air inlet pipe 210 is provided. The air pipe 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. The first air collecting pipe section 201 is located in the conduction section, and the first air pipe branch pipe 230 is connected to the first air collecting pipe section 201, which is used to communicate with the air inlet pipe 210. The third heat exchange flow path 330 of the variable split heat exchanger is connected, the second air pipe branch 240 is connected to the second collecting pipe section 202, and is used to be connected to the second heat exchange flow path 320 of the variable split heat exchanger, and the second heat exchange flow path 320 is connected to the lower part of the third heat exchange flow path 330, the third air pipe branch 250 is connected to the second collecting pipe section 202, and is used to be connected to the first heat exchange flow path 310 of the variable split heat exchanger, and the first heat exchange flow path 310 is connected to the lower part of the second heat exchange flow path 320.

[0118] 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.

[0119] 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.

[0120] 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.

[0121] 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.

[0122] The first heat exchange flow path 310 is connected between the first branch pipe 120 and the third gas branch pipe 250, the second heat exchange flow path 320 is connected between the second liquid distribution pipe 152 and the second gas branch pipe 240, and the third heat exchange flow path 330 is connected between the first liquid distribution pipe 151 and the first gas branch pipe 230. In this way, by providing a plurality of heat exchange flow paths respectively disposed between the branch pipes and the flow distribution pipes, different flow paths can be generated under cooling conditions and heating conditions, thereby improving the overall performance of the variable flow distribution heat exchanger.

[0123] 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.

[0124] 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.

[0125] Combination Fig.18 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 152 and the first branch pipe 151 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.

[0126] Combination Fig.19 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 first liquid distribution pipe 151. At this time, the liquid pipe valve component 130 in the collecting pipe 100 is in a non-conducting state, and the refrigerant continues to enter the second liquid distribution pipe 152 and flows into the second heat exchange flow path 32 0 after heat exchange through the second gas pipe branch pipe 240 into the lower half of the collecting pipe 200 located below the gas pipe valve component 220, and from this part continues to flow into the third gas pipe branch pipe 250, and after heat exchange through the first heat exchange flow path 310, flows into the part of the collecting pipe 100 located below 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.

[0127] In some embodiments, an air conditioner includes the variable split heat exchanger described above.

[0128] The effects of the air conditioner provided by the embodiment of the present disclosure are the same as those described above for the effect of the header component of the heat exchanger, and are not described in detail here.

[0129] 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 header component, characterized in that: include: A header (100); The liquid distribution branch pipe is connected to the collecting pipe (100), and comprises a first liquid distribution pipe (151) and a second liquid distribution pipe (152). The first liquid distribution pipe (151) is used to be connected to the third heat exchange flow path (330) of the heat exchanger; the second liquid distribution pipe (152) is used to be connected to the second heat exchange flow path (320) of the heat exchanger, and the second liquid distribution pipe (152) is located below the first liquid distribution pipe (151), wherein: The number of resistance components through which the refrigerant flows after flowing out of the second liquid distribution tube (152) is greater than the number of resistance components through which the refrigerant flows after flowing out of the first liquid distribution tube (151), or the refrigerant flows through at least one valve component after flowing out of the second liquid distribution tube (152).

2. The header member according to claim 1, characterized in that The dispensing branch also includes: The main pipe section (140) is in communication with the manifold (100), and the first liquid distribution pipe (151) and the second liquid distribution pipe (152) are respectively in communication with the main pipe section (140).

3. The header member according to claim 2, characterized in that The main pipe section (140) comprises a first main pipe communication end (141) connected to the manifold (100), and a second main pipe communication end (142) connected to the first liquid distributing pipe (151) and the second liquid distributing pipe (152). The distance between the first main pipe connecting end (141) and the second main pipe connecting end (142) is H1, and 10 mm ≤ H1 ≤ 40 mm.

4. The header member according to claim 2, characterized in that The first liquid distributing pipe (151) comprises a first connecting end (1512) for communicating with the third heat exchange flow path (330), wherein the shortest distance between the first connecting end (1512) and the outer wall of the collecting pipe (100) is H2, 15 mm ≤ H2 ≤ 90 mm; and / or, The second liquid distributing pipe (152) further comprises a second connecting end (1522) for communicating with the second heat exchange flow path (320), wherein the shortest distance between the second connecting end (1522) and the outer wall of the collecting pipe (100) is H3, 15 mm ≤ H3 ≤ 90 mm; and / or, The outer diameter of the main pipe section (140) is greater than or equal to 4 mm and less than or equal to 7 mm; and / or The outer diameter of the collecting pipe (100) is greater than or equal to 9 mm and less than or equal to 13 mm.

5. The header member according to claim 2, characterized in that The first liquid distributing pipe (151) comprises a first arc-shaped curved pipe section (1513) and a first straight pipe section (1514) which are interconnected, and the second liquid distributing pipe (152) comprises a second arc-shaped curved pipe section (1523) and a second straight pipe section (1524) which are interconnected. The first arc-shaped curved pipe section (1513) and the second arc-shaped curved pipe section (1523) are connected, and the first straight pipe section (1514) and the second straight pipe section (1524) are parallel and extend in the same direction.

6. The header member according to claim 5, characterized in that The projections of the first straight pipe section (1514) and the second straight pipe section (1524) in the vertical direction overlap; and / or, The shortest distance between the two ends of the first curved pipe segment (1513) is less than or equal to the length of the first straight pipe segment (1514), and the shortest distance between the two ends of the second curved pipe segment (1523) is less than or equal to the length of the second straight pipe segment (1524); and / or, The distance between the first straight pipe section (1514) and the second straight pipe section (1524) is H4, 15mm≤H4≤30mm.

7. The header member according to claim 3, characterized in that The header (100) includes an upper sealed end (103), The first main pipe connecting end (141) and the upper sealing end (103) are arranged at intervals along the pipe length direction of the collecting pipe (100).

8. The header member according to claim 7, characterized in that The distance between the first main pipe connecting end (141) and the upper sealing end (103) is H5. Among them, H5≥20mm.

9. The header member according to claim 3, characterized in that The main pipe section (140) is arranged in the horizontal direction so that the liquid distribution branch pipe is a Y-shaped three-way pipe arranged horizontally; or, The angle between the main pipe section (140) and the horizontal direction is less than or equal to a first preset angle, and the first main pipe connecting end (141) of the main pipe section (140) is located above the second main pipe connecting end (142).

10. The header member according to any one of claims 1 to 9, characterized in that: Also includes: The discrete element (160) is arranged in a path where the refrigerant flows, and is used to discrete the refrigerant flowing into the header (100).

11. The header member according to claim 10, characterized in that Also includes: The liquid inlet pipe (110) comprises a separation pipe section (111) and an outflow pipe section (113) which are connected to each other. The outflow pipe section (113) is connected to the manifold (100). The discrete element (160) is arranged in the outflow pipe section (113). The refrigerant passes through the separation pipe section (111) and enters the outflow pipe section (113), and then passes through the discrete element (160) and enters the collecting pipe (100).

12. The header member according to claim 11, characterized in that The separation pipe section (111) is an arc-shaped structure, the curvature of the arc-shaped structure is r, the distance between the first connection point (112) between the separation pipe section (111) and the outflow pipe section (113) and the discrete element (160) is H, Among them, the larger r is, the larger H is.

13. The header member according to claim 11, characterized in that The distance between the bottom end of the discrete element (160) and the bottom end of the separation pipe section (111) is h1, Among them, h1≥50mm.

14. The header member according to claim 11, characterized in that The distance between the first connection point (112) between the separation pipe section (111) and the outflow pipe section (113) and the bottom end of the discrete element (160) is h2. Among them, h2≥5mm.

15. The header member according to any one of claims 11 to 14, characterized in that The discrete element (160) includes a filter screen.

16. The header member according to claim 11, characterized in that Also includes: The first branch pipe (120) is connected to the header pipe (100). The distance between the first connecting point (112) between the separation pipe section (111) and the outflow pipe section (113) and the second connecting point (121) between the first branch pipe (120) and the header (100) is e, and e≥20 mm.

17. The header member according to claim 11, characterized in that The angle between the projections of the separation pipe section (111) of the liquid inlet pipe (110) and the first branch pipe (120) along the axial direction of the collecting pipe (100) is greater than or equal to 90 degrees; and / or, The included angle between the projection of the separation pipe section of the liquid inlet pipe (110) and the first branch pipe (120) along the axial direction of the collecting pipe (100) is greater than or equal to 145 degrees and less than or equal to 180 degrees; and / or, The angle between the projection of the separation pipe section of the liquid inlet pipe (110) and the first branch pipe (120) along the axial direction of the collecting pipe (100) is equal to 160 degrees; and / or, The separation pipe section (111) of the liquid inlet pipe (110) is U-shaped.

18. A variable split flow heat exchanger, characterized in that: include: A header member as claimed in any one of claims 1 to 17; and, A plurality of heat exchange flow paths, each heat exchange flow path is connected to a header (100) of a header component through a branch pipe.

19. The variable split heat exchanger according to claim 18, characterized in that: Also included is a tracheal structure, wherein The air pipe structure comprises an air collecting pipe (200), an air inlet pipe (210), an air pipe valve component (220), a first air pipe branch pipe (230), a second air pipe branch pipe (240) and a third air pipe branch pipe (250); the air pipe valve component (220) is connected to the air collecting pipe (200), and the air pipe valve component (220) 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 (200) is connected to the air inlet pipe (210), the first air pipe branch pipe (230) is connected to one side of the air valve conduction outflow end, the second air pipe branch pipe (240) and the third air pipe branch pipe (250) are connected to one side of the air valve conduction inflow end, 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), wherein 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 liquid distribution pipe (152) and the second air pipe branch pipe (240), and the third heat exchange flow path (330) is connected between the first liquid distribution pipe (151) and the first air pipe branch pipe (230).

20. An air conditioner, characterized in that: Comprising a variable split heat exchanger as claimed in claim 18 or 19.

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