Header component, variable shunting heat exchanger and air conditioner

Abstract

The utility model relates to the technical field of household appliances, and discloses a collecting pipe component which comprises a collecting pipe and discrete elements. The dispersing element is arranged in a refrigerant circulation path and used for dispersing the refrigerant flowing into the collecting pipe. In this way, the gas-liquid mixing uniformity of the refrigerant in the header component 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 electrical appliance technology, for example, to a header component, a variable split-flow heat exchanger and an air conditioner. Background Art

[0002] The header component is a common component connected to the heat exchanger. It can divide the refrigerant flowing in from the liquid inlet through multiple branch pipes so that the refrigerant can flow to different heat exchange paths of the heat exchanger. When the air conditioner is in heating mode, the heating performance of the air conditioner is better when the multiple heat exchange paths of the outdoor heat exchanger are connected in parallel.

[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] The existing heat exchanger header has the phenomenon of uneven liquid distribution, which affects the heat exchange effect 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 a manifold component, a variable split heat exchanger and an air conditioner to solve the problem of separation of the refrigerant gas-liquid two-phase state after flowing into the manifold, resulting in uneven gas-liquid mixing, affecting the refrigerant distribution stability of the manifold component, and further affecting the heat exchange efficiency of the heat exchanger.

[0009] In some embodiments, the manifold component includes a manifold and a discrete element, which is disposed in a path where the refrigerant flows and is used to discrete the refrigerant flowing into the manifold.

[0010] In some embodiments, the variable split heat exchanger includes a header member 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 provided in the embodiment of the present disclosure includes a manifold and a discrete element, wherein the discrete element is connected to the path of the refrigerant flow and is used to disperse the refrigerant flowing into the manifold. In this way, the gas-liquid two-phase refrigerant can be dispersed under the action of the discrete element, reducing the difference in the amount of refrigerant between the manifold distribution of different refrigerants, improving the mixing degree of the gas-liquid two-phase refrigerant, improving the certainty and stability of the amount of refrigerant diverted from the manifold to the branch pipe, and improving the uniformity of the liquid separation of the manifold assembly to the refrigerant, thereby improving the heat exchange efficiency of the heat exchanger and the operating stability of the air conditioner.

[0014] 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

[0015] 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:

[0016] Figure 1 is a structural schematic diagram of a manifold component provided by an embodiment of the present disclosure;

[0017] Figure 2 yes Figure 1 A magnified view of a selected portion;

[0018] Figure 3 yes Figure 1 another enlarged view of a selected portion;

[0019] Figure 4 is a schematic diagram of the structure of a filter provided by an embodiment of the present disclosure;

[0020] Figure 5 is a schematic diagram of the structure of a discrete element provided by an embodiment of the present disclosure;

[0021] Figure 6 is a structural schematic diagram of another manifold component provided by an embodiment of the present disclosure;

[0022] Figure 7 is a structural schematic diagram of another manifold component provided by an embodiment of the present disclosure;

[0023] Figure 8is a bottom view of a header component provided by an embodiment of the present disclosure;

[0024] Fig. 9 is a refrigerant flow distribution diagram of each branch when the angle a is 45 degrees provided in an embodiment of the present disclosure;

[0025] Fig.10 is a refrigerant flow distribution diagram of each branch when the angle a is 160 degrees provided in an embodiment of the present disclosure;

[0026] Fig.11 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;

[0027] Fig.12 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;

[0028] Fig.13 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;

[0029] Fig.14 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;

[0030] Fig.15 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;

[0031] Fig.16 is a schematic structural diagram of a variable split flow heat exchanger provided by an embodiment of the present disclosure;

[0032] Fig.17 This is a schematic diagram of the gas pipe structure of a heat exchanger of a comparative example;

[0033] Fig.18 is a schematic diagram of the air pipe structure of a heat exchanger provided in an embodiment of the present disclosure;

[0034] Fig.19 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. 20 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.

[0036] Reference numerals:

[0037] 100, manifold; 101, first liquid inlet end; 102, first manifold section; 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, 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 Tube; 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 tube; 301, heat exchange fin; 310, first heat exchange flow path; 320, second heat exchange flow path; 330, third heat exchange flow path. DETAILED DESCRIPTION

[0038] 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.

[0039] 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.

[0040] 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.

[0041] 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.

[0042] Unless otherwise stated, the term "plurality" means two or more.

[0043] 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.

[0044] 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.

[0045] 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.

[0046] The embodiment of the present disclosure provides a header component. Optionally, the header component provided by the embodiment of the present disclosure can be used as a liquid pipe structure of a heat exchanger.

[0047] Optionally, the header component includes a header 100 and discrete elements 160. The discrete elements 160 are disposed in a path where the refrigerant flows, and are used to mix the refrigerant flowing into the header 100.

[0048] 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.

[0049] 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.

[0050] 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.

[0051] 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.

[0052] 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.

[0053] 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.

[0054] 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.

[0055] 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.

[0056] 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.

[0057] 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.

[0058] 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. Figure 2 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.

[0059] 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.

[0060] 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 Figure 5 As shown in C and D, or, the shape of the filter mesh is irregular, such as Figure 5 As shown in B. It can be understood that the filter mesh is the aforementioned liquid balancing hole.

[0061] 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 Figure 5 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 Figure 4 shown.

[0062] 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.

[0063] 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.

[0064] Optionally, the manifold component further includes a first branch pipe 120, and the first branch pipe 120 is connected to the manifold 100. Optionally, the first branch pipe 120 is used to communicate with the first heat exchange flow path 310 of the heat exchanger, and the refrigerant in the manifold 100 flows into the first heat exchange flow path 310 through the first branch pipe 120, wherein the discrete element 160 is connected to the upstream of the refrigerant flow path flowing into the first branch pipe 120.

[0065] The first branch pipe 120 is connected to the manifold and the first heat exchange flow path 310, and is used to conduct the refrigerant in the inner cavity of the manifold to the first heat exchange flow path 310 for heat exchange. In the embodiment of the present disclosure, a discrete element 160 is provided upstream of the refrigerant flow path of the first branch pipe 120, so that before the refrigerant flows into the first branch pipe 120, the discrete element 160 breaks up the gas-liquid two-phase refrigerant, thereby improving the stability of the refrigerant flowing into the first branch pipe 120. The upstream of the refrigerant flow path of the first branch pipe 120 can be understood as the section before flowing into the first branch pipe 120. It can be understood that when the air conditioner is running in the cooling mode and the heating mode, the flow path of the refrigerant is opposite, and the upstream here can be understood as the flow path of the air conditioner when it is running in one of the operating modes, such as the refrigerant flow path when the air conditioner is running in the heating mode.

[0066] Optionally, the discrete element 160 is disposed between a first connecting point 112 between the separation pipe segment 111 and the outflow pipe segment 113 and a second connecting point 121 between the first branch pipe 120 and the header 100 .

[0067] Optionally, the manifold 100 includes a first liquid inlet end 101, and the first branch pipe 120 is disposed near the first liquid inlet end 101.

[0068] Optionally, the position where the first liquid inlet end 101 of the manifold 100 is connected to the liquid inlet connecting end of the liquid inlet pipe 110 has a closing structure, which can be seen in Figure 1 At the location pointed to by 101.

[0069] Optionally, the first liquid inlet end 101 is a lower liquid inlet of the manifold 100 .

[0070] Optionally, the manifold is integrally formed, or the manifold, a plurality of branch pipes and the liquid inlet pipe are integrally formed. The embodiments of the present disclosure do not impose too many restrictions on the specific forming method of the manifold component.

[0071] Optionally, 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, where 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.

[0072] 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.

[0073] like Figure 8 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.

[0074] 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.

[0075] 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.

[0076] 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. 9 ), 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.10), 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.

[0077] 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.

[0078] 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.

[0079] 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.

[0080] The first branch pipe 120 is located at a distance of 70 mm (e.g. Fig.11 ), 80 mm (such as Fig.12 ), 85 mm (such as Fig.13 ), 90 mm (such as Fig.14 ) and 100 mm (such as Fig.15). 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.

[0081] 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.

[0082] 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.

[0083] Optionally, the manifold assembly further includes a liquid pipe valve component 130, a second branch pipe 140, and a third branch pipe 150. The liquid pipe valve component 130 is connected to the manifold 100, and the liquid pipe valve component 130 includes a liquid valve inlet end and a liquid valve outlet end; and the second branch pipe 140 and the third branch pipe 150 are connected to one side of the liquid pipe outlet end of the liquid pipe valve component 130, wherein the second branch pipe 140 includes a second branch pipe end connected to the manifold 100, and the third branch pipe 150 includes a third branch pipe end connected to the manifold 100, and the second branch pipe end is located above the third branch pipe end.

[0084] Optionally, the manifold component of the heat exchanger also includes: a liquid pipe valve component 130 and a second branch pipe 140, the liquid pipe valve component 130 is connected to the manifold 100, the liquid pipe valve component 130 can be a one-way valve or a solenoid valve, used to make the manifold 100 unidirectionally conductive from one end where the liquid inlet pipe 110 is provided to the other end, wherein the first branch pipe 120 is connected between the liquid pipe valve component 130 and the liquid inlet pipe 110; the second branch pipe 140 is connected to the manifold 100 on one side of the conductive direction of the liquid pipe valve component 130. In this way, a liquid pipe valve component 130 is arranged on the collecting pipe 100, and the flow direction of the liquid pipe valve component 130 is to flow from the first branch pipe 120 toward the second branch pipe 140, so that when the refrigerant enters the collecting pipe 100 through the liquid inlet pipe 110, the refrigerant can enter the first branch pipe 120 and the second branch pipe 140 side by side, and when the refrigerant flows in the opposite direction, the collecting pipe 100 is intercepted by the liquid pipe valve component 130, so that the second branch pipe 140 and the first branch pipe 120 are connected in series, and a single refrigerant flow path can be formed. By setting the liquid pipe valve component 130, different numbers of refrigerant flow paths can be formed under cooling conditions and heating conditions, thereby improving the heat exchange efficiency of the heat exchanger.

[0085] It can be understood that when the collecting pipe 100 is vertically arranged, the conduction direction of the liquid pipe valve component 130 in the working state is from bottom to top, and the first branch pipe 120 is connected to the lower side of the liquid pipe valve component 130, and the second branch pipe 140 is connected to the upper side of the liquid pipe valve component 130.

[0086] Optionally, the manifold component of the heat exchanger further includes: a third branch pipe 150, which is also connected to the manifold 100 on one side of the conducting direction of the liquid pipe valve component 130, and the other end of the third branch pipe 150 is respectively connected to different heat exchange paths of the heat exchanger with the other end of the first branch pipe 120 and the other end of the second branch pipe 140. In this way, 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, and when the heat exchanger is used as a condenser, the refrigerant enters the manifold 100 through the third branch pipe 150, 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 manifold 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 path, thereby improving the efficiency of heating and cooling.

[0087] 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.

[0088] Optionally, the second branch pipe 140 is connected to the manifold 100 on one side of the conducting direction of the liquid pipe valve component 130, and is used to be connected to the second heat exchange flow path 320 of the variable split heat exchanger. The third branch pipe 150 is connected to the manifold 100 on one side of the conducting direction of the liquid pipe valve component 130, and is used to be connected to the third heat exchange flow path 330 of the variable split heat exchanger. The third heat exchange flow path 330 is located at the upper part of the second heat exchange flow path 320. 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.

[0089] In this way, at present, the arrangement mode of multiple branch pipes is mostly to arrange the heat exchange flow paths of the corresponding heat exchangers in sequence from bottom to top, that is, the heat exchange flow path on the lower side of the heat exchanger is connected to a relatively lower position on the manifold 100 through a branch pipe, and the heat exchange flow path on the upper side is connected to a relatively upper position on the direct current pipe through a branch pipe. When the liquid-phase refrigerant flows into the manifold 100 through the liquid inlet pipe 110, the liquid pipe valve component 130 is conducted by the impact force of the refrigerant. At this time, the refrigerant is accelerated and rushes straight through the liquid pipe valve component 130, resulting in its mass flow rate flowing to the branch pipe far away from the liquid pipe valve component 130, that is, at a high point, being higher than the mass flow rate in the branch pipe relatively close to the liquid pipe valve component 130, that is, at a low point. Moreover, the heat exchange flow path connected to the branch pipe at the low point needs to flow through a one-way valve again after heat exchange, which increases the pressure loss of the branch and further reduces the mass flow rate of the branch, thereby causing the mass flow rate of the branch pipe at the low point to be further reduced relative to the mass flow rate of the branch pipe at the high point, resulting in overall uneven flow distribution. In order to achieve uniform flow diversion, the connection point between the second branch pipe 140 and the collecting pipe 100 is connected to a high point, and the connection point between the third branch pipe 150 and the collecting pipe 100 is connected to a low point, and the other end of the second branch pipe 140 is lower than the other end of the third branch pipe 150, and is connected to the heat exchange flow path at a low point on the heat exchanger, while the other end of the third branch pipe 150 is connected to the heat exchange flow path at a high point on the heat exchanger, thereby increasing the mass flow rate of the heat exchange flow path entering the bottom point, balancing the pressure loss of this part of the heat exchange flow path due to the need to pass through a one-way valve again, thereby balancing the flow diversion effect and making the overall flow diversion more uniform.

[0090] 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.

[0091] 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

[0092] Table 1

[0093] 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

[0094] Table 2

[0095] Optionally, the second branch pipe 140 includes a first connecting pipe 141 directly connected to the manifold 100, and the third branch pipe 150 includes a second connecting pipe 151 directly connected to the manifold 100, wherein the angle between the first connecting pipe 141 and the manifold 100 is smaller than the angle between the second connecting pipe 151 and the manifold 100. In this way, the original flow trend of the refrigerant rushing into the third branch pipe 150, resulting in uneven liquid separation between the second branch pipe 140 and the third branch pipe 150, is further broken. The refrigerant is made 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 manifold 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 manifold 100 can be greater than 45° and less than or equal to 90°.

[0096] Optionally, the first connecting pipe 141 is connected in parallel with the port of the manifold 100; and / or the second connecting pipe 151 is vertically connected to the side wall of the manifold 100. In this way, the refrigerant in the manifold 100 can directly rush into the second branch pipe 140 after passing through the liquid pipe valve component 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.

[0097] 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.

[0098] 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 6 shown.

[0099] Optionally, the header component of the heat exchanger further includes: a fourth branch pipe, which is connected to the side wall of the header pipe 100 between the third branch pipe 150 and the liquid pipe valve component 130 .

[0100] 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.

[0101] 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.

[0102] 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.

[0103] 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.

[0104] 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.

[0105] Optionally, a closing structure is provided at one end of the manifold 100, and one end of the liquid inlet pipe 110 is inserted into the closing structure and welded to the closing structure. In this way, by using the closing structure at one end of the manifold 100 to insert part of the liquid inlet pipe 110 into the interior thereof and welding, the stability of the connection between the two can be improved, and the risk of refrigerant leakage can be reduced.

[0106] 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.

[0107] 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.

[0108] 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.

[0109] 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.

[0110] 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.

[0111] The disclosed embodiment also provides an air pipe structure of a variable split heat exchanger.

[0112] 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.

[0113] 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 air 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, and the third air pipe branch 250 is connected to the second air 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. Among them, the first air pipe branch 230 is connected to the first height of the air collecting pipe 200, the air intake pipe 210 is connected to the second height of the air collecting pipe 200, and the first height is greater than or equal to the second height.

[0114] In the air pipe structure provided by the embodiment of the present disclosure, the first air pipe branch 230 is connected to the first height of the air collecting pipe 200, the air intake pipe 210 is connected to the 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.

[0115] 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.

[0116] 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 connected to 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.

[0117] 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 connected to the first position, and the air intake pipe 210 is connected to the second position.

[0118] When the first air duct branch 230 is flush with the air intake pipe 210, the first air duct branch 230 and the air intake pipe 210 are symmetrically connected at the first height of the collecting pipe 200. This symmetrical setting 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.

[0119] 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 connected to the first position, and the air intake pipe 210 is connected to the bottom of the second position.

[0120] When the air inlet pipe 210 is connected to the lower part of the first air pipe branch 230, the air inlet pipe 210 can be connected to the lower part of the second position, so that 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 further reduced. Optionally, the second air pipe branch 240 and the third air pipe branch 250 are connected to the lower part of 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, which improves the uniformity of the flow direction of the refrigerant flowing out of different shunt pipes.

[0121] 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 connected to the lower part of 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.

[0122] 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.

[0123] Air pipe structure 1- Refrigerant mass flow ratio Air pipe structure 2-refrigerant mass flow ratio The third heat exchange path 24.23％ 26.05％ Second heat exchange path 27.35％ 30.38％ The first heat exchange path 48.41％ 43.57％

[0124] Table 3

[0125] 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.17 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.18 . 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 manifold component used in the variable split flow heat exchanger in the embodiment of the present disclosure is such as Figure 1 shown.

[0126] 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.

[0127] 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.

[0128] 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.

[0129] 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.

[0130] 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 disposed between the branch pipes and the flow splitting pipes, different flow paths can be generated under cooling conditions and heating conditions, thereby improving the overall performance of the variable flow splitting heat exchanger.

[0131] 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.

[0132] 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.

[0133] Combination Fig.19 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.

[0134] Combination Fig. 20 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 in a non-conducting state, and the refrigerant continues to enter the second branch pipe 140 and flows into the second heat exchange flow path 320 for heat exchange. After heat exchange, it 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 through 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, which can accelerate the circulation and increase the heat transfer coefficient, thereby improving the high-temperature cooling capacity.

[0135] In some embodiments, an air conditioner includes the variable split heat exchanger described above.

[0136] 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.

[0137] 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: The header (100) and 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).

2. The header member according to claim 1, 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).

3. The header member according to claim 2, 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.

4. The header member according to claim 2, 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.

5. The header member according to claim 2, 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.

6. The header member according to any one of claims 2 to 5, characterized in that: The discrete element (160) includes a filter screen.

7. The header member according to claim 6, characterized in that the filter screen include: A first net portion (161) 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).

8. The header member according to claim 7, characterized in that A hollow portion is provided between the first net portion (161) and the second net portion (162).

9. The header member according to claim 7, characterized in that The aperture of at least some of the meshes of the second net part (162) is smaller than the aperture of the meshes of the first net part (161).

10. The header member according to claim 2, characterized in that Also includes: The first branch pipe (120) is connected to the header pipe (100).

11. The header member according to claim 10, 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 second connection point (121) between the first branch pipe (120) and the header (100) is e, Among them, e≥20mm.

12. The header member according to claim 10, 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.

13. The header member according to claim 12, characterized in that Also includes: A liquid pipe valve component (130) is connected to the manifold (100), and the liquid pipe valve component (130) comprises a liquid valve inlet end and a liquid valve outlet end; and, The second branch pipe (140) and the third branch pipe (150) are connected to one side of the liquid pipe outflow end of the liquid pipe valve component (130). The second branch pipe (140) includes a second branch pipe end connected to the header pipe (100), the third branch pipe (150) includes a third branch pipe end connected to the header pipe (100), and the second branch pipe end is located above the third branch pipe end.

14. A variable split flow heat exchanger, characterized in that: include: The header member according to any one of claims 1 to 13; 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.

15. The variable split heat exchanger according to claim 14, 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 duct branch pipe (250), the second heat exchange flow path (320) is connected between the second branch pipe (140) and the second air duct branch pipe (240), and the third heat exchange flow path (330) is connected between the third branch pipe (150) and the first air duct branch pipe (230).

16. An air conditioner, characterized in that: Comprising the variable split heat exchanger as claimed in claim 14 or 15.

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