Liquid pipe structure of heat exchanger, variable shunting heat exchanger and air conditioner

Abstract

The utility model relates to the technical field of household appliances, and discloses a liquid pipe structure of a heat exchanger, which comprises a collecting pipe, a liquid inlet pipe and a first branch pipe, the liquid inlet pipe is communicated with one end of the collecting pipe; the first branch pipe is connected to the side wall of the collecting pipe and communicates with the interior of the collecting pipe. The included angle between the projection of the liquid inlet pipe and the projection of the first branch pipe in the axial direction of the collecting pipe is larger than or equal to 90 degrees. According to the heat exchanger, liquid-phase refrigerants can fully flow into the heat exchanger, the heat exchange effect of the heat exchanger is guaranteed, the distribution uniformity of the liquid-phase refrigerants is improved, the whole heat exchanger can achieve the effect of simplifying the structure and the process, and the distribution uniformity of the liquid-phase refrigerants can be guaranteed. The utility model further discloses the variable flow dividing heat exchanger and an air conditioner.

Description

Technical Field

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

[0002] At present, the heat exchanger cannot perform optimally under both cooling and heating conditions with the same flow path design. By designing the flow path of the refrigerant, different flow paths are provided under cooling and heating conditions. Under heating conditions, when the variable split heat exchanger is used as an evaporator, the refrigerant in its tubes is in the low temperature and low pressure zone, and the heat transfer performance is mainly constrained by the heat transfer coefficient and the pressure drop. It is suitable for a relatively large number of branches. While ensuring the heat transfer coefficient, the pressure drop is greatly reduced to increase the system pressure, thereby increasing the low-temperature heating capacity. Under cooling conditions, when the variable split heat exchanger is used as a condenser, the refrigerant in its tubes is in the high temperature and high pressure zone and is not sensitive to the pressure drop. The heat transfer performance is mainly affected by the heat transfer coefficient. It is suitable for a small number of branches to accelerate the circulation and increase the heat transfer coefficient, thereby increasing the high-temperature cooling capacity.

[0003] Since multi-branch heat exchange is required under heating conditions, refrigerant diversion is required. At present, in order to improve the uniformity of refrigerant diversion, Y-shaped tees are often used to connect the diversion branches. However, since the Y-shaped tees need to be connected to the pipeline, the interfaces are more complicated, and since there will be certain errors in the production process of the Y-shaped tees, there will be slight differences when connecting different individual Y-shaped tees to the pipeline during the mass production process, resulting in poor product consistency and increased difficulty in production and processing.

[0004] Therefore, it can be seen that how to simplify the structure of the refrigeration system, improve product consistency, and maintain the uniformity of the refrigerant diversion has become a technical problem that needs to be urgently solved by technical personnel in this field.

[0005] 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

[0006] 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.

[0007] The embodiments of the present disclosure provide a liquid pipe structure of a heat exchanger, a variable shunt heat exchanger and an air conditioner to solve the problem that the connection of shunt branches using a Y-shaped tee has a complex process, many interfaces and poor product consistency.

[0008] In some embodiments, the liquid pipe structure of the heat exchanger includes: a header, a liquid inlet pipe, and a first branch pipe. The liquid inlet pipe is connected to one end of the header; the first branch pipe is connected to the side wall of the header and is connected to the inside of the header; wherein the angle between the projection of the liquid inlet pipe and the first branch pipe along the axial direction of the header is greater than or equal to 90 degrees.

[0009] In some embodiments, the variable split heat exchanger includes: the liquid pipe structure of the heat exchanger described above.

[0010] In some embodiments, an air conditioner includes: the variable split heat exchanger described above.

[0011] The liquid pipe structure of the heat exchanger, the variable split flow heat exchanger and the air conditioner provided by the embodiments of the present disclosure can achieve the following technical effects:

[0012] By directly connecting the first branch pipe to the side wall of the manifold, there is no need to use a Y-shaped tee for connection, which can effectively reduce the number of interfaces and simplify the process, avoid the influence of the error of the Y-shaped tee in the production process on the connection between the branch pipe and the manifold, and keep the connection structure between the branch pipe and the manifold consistent, thereby improving the consistency of the product. At the same time, since the current liquid inlet pipe will produce centrifugal force in the process of passing the refrigerant, the refrigerant will produce gas-liquid separation under the action of centrifugal force, and then the part of one side wall close to the liquid inlet pipe is liquid phase refrigerant, and the part of the other side wall close to the liquid inlet pipe is gas phase refrigerant. And the state of gas-liquid separation will still continue to a certain extent when entering the manifold, at this time, the gas phase and liquid phase distribution of the refrigerant are very uneven. Therefore, it is easy to cause the refrigerant gas phase flow rate entering the first branch pipe to be high, thereby affecting the heat exchange efficiency. And by setting the first branch pipe to have an angle greater than or equal to 90 degrees between the projection along the axis of the manifold and the projection of the liquid inlet pipe. Under the centrifugal force of the liquid inlet pipe, the liquid phase refrigerant will be distributed in large quantities on the side of the manifold away from the liquid inlet pipe after entering the manifold. Therefore, the first branch pipe is set at an angle of more than 90 degrees relative to the liquid inlet pipe, so that the first branch pipe can be connected to the side of the manifold away from the liquid inlet pipe, that is, the side where the liquid phase refrigerant is more distributed. The refrigerant that can fully flow into the liquid phase ensures the heat exchange effect and improves the uniformity of the liquid phase refrigerant diversion. The whole can not only simplify the structure and process, but also ensure the uniformity of the liquid phase refrigerant diversion.

[0013] 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

[0014] 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:

[0015] Figure 1 is a schematic diagram of a liquid pipe structure of a heat exchanger provided in an embodiment of the present disclosure;

[0016] Figure 2 yes Figure 1 A front view of the liquid pipe structure of the heat exchanger shown;

[0017] Figure 3 is a schematic structural diagram of another liquid inlet pipe provided in an embodiment of the present disclosure;

[0018] Figure 4 is a schematic structural diagram of another liquid inlet pipe provided in an embodiment of the present disclosure;

[0019] Figure 5 yes Figure 1 A bottom view of a liquid pipe structure of a heat exchanger is shown;

[0020] Figure 6 is a refrigerant flow distribution diagram of each branch when the angle a is 45 degrees provided in an embodiment of the present disclosure;

[0021] Figure 7 is a refrigerant flow distribution diagram of each branch when the angle a is 160 degrees provided in an embodiment of the present disclosure;

[0022] Figure 8 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;

[0023] Fig. 9 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;

[0024] Fig.10 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;

[0025] Fig.11 It is a refrigerant flow distribution diagram of each branch provided by the embodiment of the present disclosure, in which the first branch pipe is located at 90 mm from the liquid inlet pipe connecting the manifold;

[0026] Fig.12 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;

[0027] Fig.13 is a structural schematic diagram of a manifold component provided by an embodiment of the present disclosure;

[0028] Fig.14 yes Fig.13 A magnified view of a selected portion;

[0029] Fig.15 yes Fig.13 another enlarged view of a selected portion;

[0030] Fig.16 is a schematic diagram of the structure of a filter provided by an embodiment of the present disclosure;

[0031] Fig.17 is a schematic diagram of the structure of a discrete element provided by an embodiment of the present disclosure;

[0032] Fig.18 is a schematic structural diagram of a variable split flow heat exchanger provided by an embodiment of the present disclosure;

[0033] Fig.19 is a schematic diagram of the air pipe structure of a heat exchanger provided in an embodiment of the present disclosure;

[0034] Fig. 20 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.21 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, collecting pipe; 101, closing structure; 110, liquid inlet pipe; 111, bending part; 112, first connecting point; 113, outflow pipe section; 120, first branch pipe; 121, second connecting point; 130, liquid pipe one-way valve; 140, second branch pipe; 150, third branch pipe; 160, discrete element; 161, first net part; 162, second net part; 200, air collecting pipe; 210, air inlet pipe; 220, air pipe one-way valve; 230, first branch pipe; 240, second branch pipe; 250, third branch pipe; 300, heat exchange pipe; 301, heat exchange fin; 310, first heat exchange flow path; 320, second heat exchange flow path; 330, third heat exchange flow path. DETAILED DESCRIPTION

[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] Combination Figure 1-Figure 5As shown, the embodiment of the present disclosure provides a liquid pipe structure of a heat exchanger including: a header 100, a liquid inlet pipe 110, and a first branch pipe 120. The liquid inlet pipe 110 is connected to one end of the header 100; the first branch pipe 120 is connected to the side wall of the header 100 and is connected to the inside of the header 100; wherein the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the header 100 is greater than or equal to 90 degrees.

[0047] By adopting the liquid pipe structure of the heat exchanger provided by the embodiment of the present disclosure, by directly connecting the first branch pipe 120 to the side wall of the manifold 100, there is no need to use a tee for connection, which can effectively reduce the number of interfaces and simplify the process, avoid the influence of the error of the Y-shaped tee in the production link on the connection between it and the pipeline, make the connection structure between the branch pipe and the manifold 100 consistent, and improve the consistency of the product. At the same time, since the current liquid inlet pipe 110 will produce centrifugal force in the process of passing the refrigerant, the refrigerant will produce gas-liquid separation under the action of centrifugal force, and then the part of one side wall close to the liquid inlet pipe 110 is liquid phase refrigerant, and the part of the other side wall close to the liquid inlet pipe 110 is gas phase refrigerant. And the state of gas-liquid separation will still continue to a certain extent when entering the manifold 100, at this time, the gas phase and liquid phase distribution of the refrigerant are very uneven. Therefore, it is easy to cause the gas phase flow rate of the refrigerant entering the first branch pipe 120 to be high, thereby affecting the heat exchange efficiency. By setting the first branch pipe 120 so that the angle between the projection along the axial direction of the manifold 100 and the projection of the liquid inlet pipe 110 is greater than or equal to 90 degrees. Under the centrifugal force of the liquid inlet pipe 110, the liquid-phase refrigerant will be distributed in large quantities on the side of the manifold 100 away from the liquid inlet pipe 110 after entering the manifold 100. Therefore, setting the first branch pipe 120 to have an angle of more than 90 degrees relative to the liquid inlet pipe 110 can enable the first branch pipe 120 to be connected to the side of the manifold 100 away from the liquid inlet pipe 110, that is, the side where the liquid-phase refrigerant is more distributed. The refrigerant that can fully flow into the liquid phase ensures the heat exchange effect and improves the uniformity of the liquid-phase refrigerant diversion. The whole can not only simplify the structure and process, but also ensure the uniformity of the liquid-phase refrigerant diversion.

[0048] Combination Figure 2 As shown, the liquid inlet pipe 110 includes at least a bent portion 111. It can be understood that since this solution is to solve the problem of uneven distribution of refrigerant gas and liquid caused by the centrifugal force of the liquid inlet, the liquid inlet pipe 110 adapted to this solution needs to have a part of the bent section so that the liquid inlet pipe 110 can change the flow direction of the internal refrigerant and produce a certain centrifugal effect on the refrigerant inside the liquid inlet pipe 110.

[0049] It can be understood that, taking the curved structure of the bend 111 as an example, when the refrigerant passes through the liquid inlet pipe 110, due to the effect of centrifugal force, the liquid phase refrigerant near the outer arc portion of the curved structure is more distributed, while the gas phase refrigerant near the inner arc portion of the curved structure is more distributed. And this gas-liquid separation effect will continue to a certain extent after entering the manifold 100 through the liquid inlet pipe 110, resulting in the distribution of more liquid phase refrigerant in part of the manifold 110 near one side wall, and more gas phase refrigerant in part of the other side wall in the opposite direction.

[0050] It is understandable that the specific shape of the liquid inlet pipe 110 is not limited, and it can be a U-shaped, L-shaped, multi-stage wavy shape (see Figure 2-Figure 4 ) and other shapes.

[0051] like Figure 5 As shown, the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 refers to the angle between the projections of the central axis of the liquid inlet pipe 110 and the central axis of the first branch pipe 120 along the axial direction of the manifold 100 is set to angle a.

[0052] Optionally, the angle between the projection of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is greater than or equal to 145 degrees and less than or equal to 180 degrees. In this way, by setting the angle between the projection of the first branch pipe 120 along the axial direction of the manifold 100 and the projection of the liquid inlet pipe 110 to be between 145 degrees and 180 degrees, the contact point between the first branch pipe 120 and the manifold 100 can be closer to the side of the manifold 100 away from the liquid inlet pipe 110. Since the refrigerant enters the manifold 100 under the action of centrifugal force, more liquid-phase refrigerant is distributed on the side away from the liquid inlet pipe 110, thereby allowing more liquid-phase refrigerant to enter the first branch pipe 120, reducing the proportion of gas-phase refrigerant entering the first branch pipe 120, and making the diversion of the liquid-phase refrigerant more uniform.

[0053] Preferably, the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is equal to 160 degrees. In this way, by setting the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 to 160 degrees, the liquid phase refrigerant and the gas phase refrigerant entering the first branch pipe 120 can be balanced, the proportion of the liquid phase refrigerant and the gas phase refrigerant in each branch is kept balanced, and the uniformity of the refrigerant diversion is further improved.

[0054] Combination Figure 6-Figure 7 As shown, the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is set to 45 degrees ( Figure 6 ), and the angle between the projections of the liquid inlet pipe 110 and the first branch pipe 120 along the axial direction of the manifold 100 is set to 160 degrees ( Figure 7), 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.

[0055] Optionally, the distance from the connection point of the first branch pipe 120 and the manifold 100 to the end of the manifold 100 connected to the liquid inlet pipe 110 is greater than or equal to 25 mm and less than or equal to 100 mm. In this way, the setting position of the first branch pipe 120 is controlled within 25 mm to 100 mm from the point where the liquid inlet pipe 110 connects to the manifold 100. After the refrigerant of this part enters the manifold 100 from the liquid inlet pipe 110, the gas phase refrigerant and the liquid phase refrigerant are properly mixed, and the uniformity of the refrigerant mixing is high. Therefore, setting the first branch pipe 120 within this position range can improve the uniformity of the gas phase refrigerant and the liquid phase refrigerant entering the first branch pipe 120.

[0056] Optionally, the distance from the connection point of the first branch pipe 120 and the manifold 100 to the end of the manifold 100 connected to the liquid inlet pipe 110 is greater than or equal to 70 mm and less than or equal to 90 mm. In this way, the first branch pipe 120 is further set to be within 60 mm to 80 mm from the point where the liquid inlet pipe 110 connects to the manifold 100, so that the liquid-phase refrigerant and the gas-phase refrigerant can be mixed more evenly, the influence caused by the separation of the gas-phase refrigerant and the liquid-phase refrigerant caused by the centrifugal force can be better eliminated, and the uniformity of the refrigerant diversion can be improved.

[0057] Optionally, the distance between the connection point of the first branch pipe 120 and the manifold 100 and the end of the manifold 100 connected to the liquid inlet pipe 110 is 80 mm. In this way, the first branch pipe 120 is set at a distance of 80 mm from the point where the liquid inlet pipe 110 connects to the manifold 100, so that the gas phase and liquid phase of the refrigerant are mixed in the best state, the uniformity of the refrigerant mixing is improved, and the refrigerant diversion effect is improved.

[0058] Combination Figure 8-Figure 12 As shown, the first branch pipe 120 is located at a distance of 70 mm (eg, Figure 8 ), 80 mm (such as Fig. 9 ), 85 mm (such as Fig.10 ), 90 mm (such as Fig.11 ) and 100 mm (such as Fig.12). 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.

[0059] Optionally, the distance from the connection point between the first branch pipe 120 and the manifold 100 to the end where the manifold 100 is connected to the liquid inlet pipe 110 is L, and the diameter of the arc-shaped portion of the liquid inlet pipe 110 is R, wherein L is greater than or equal to 2R and less than or equal to 4R. Preferably, L=2.6R. In this way, the diameter of the liquid inlet pipe 110 affects the centrifugal force during the liquid inlet process. By setting the distance between the connection point between the first branch pipe 120 and the manifold 100 and the connection point between the liquid inlet pipe 110 and the manifold 100 to between 2 and 4 times the diameter of the liquid inlet pipe 110, the influence of the refrigerant gas-liquid separation caused by the centrifugal force generated by the liquid inlet pipe 110 can be better eliminated, the refrigerant can be kept uniform and stable, and the diversion effect can be improved.

[0060] Optionally, the liquid pipe structure of the heat exchanger also includes: a liquid pipe one-way valve 130 and a second branch pipe 140, wherein the liquid pipe one-way valve 130 is arranged on the collecting pipe 100, and is used to make the collecting pipe 100 unidirectionally conductive from one end where the liquid inlet pipe 110 is arranged to the other end, wherein the first branch pipe 120 is connected between the liquid pipe one-way valve 130 and the liquid inlet pipe 110; the second branch pipe 140 is connected to the collecting pipe 100 on one side of the conductive direction of the liquid pipe one-way valve 130. In this way, a liquid pipe one-way valve 130 is arranged on the manifold 100, and the flow direction of the liquid pipe one-way valve 130 is to flow from the first branch pipe 120 toward the second branch pipe 140, so that when the refrigerant enters the manifold 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 manifold 100 is intercepted by the liquid pipe one-way valve 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 one-way valve 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.

[0061] The liquid pipe one-way valve 130 may be a common one-way valve or a solenoid valve controlled by control logic. The solenoid valve has the function of conducting in one flow direction of the refrigerant and closing in another flow direction of the refrigerant after being controlled.

[0062] It can be understood that when the manifold 100 is vertically arranged, the conduction direction of the liquid pipe one-way valve 130 is from bottom to top, and the first branch pipe 120 is arranged on the lower side of the liquid pipe one-way valve 130, and the second branch pipe 140 is arranged on the lower side of the liquid pipe one-way valve 130.

[0063] Optionally, the liquid pipe structure 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 check valve 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 check valve 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.

[0064] 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.

[0065] Optionally, the connection point between the second branch pipe 140 and the header 100 is higher than the connection point between the third branch pipe 150 and the header 100 ; the height of the other end of the second branch pipe 140 is lower than the height of the other end of the third branch pipe 150 . 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 collecting pipe 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 collecting pipe 100 through the liquid inlet pipe 110, the liquid pipe one-way valve 130 is turned on by the impact force of the refrigerant. At this time, the refrigerant is accelerated and rushes straight through the liquid pipe one-way valve 130, resulting in its mass flow rate in the branch pipe far away from the liquid pipe one-way valve 130, which is at a high point, being higher than the mass flow rate in the branch pipe relatively close to the liquid pipe one-way valve 130, which is at a low point, and 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. , further reducing the mass flow of the branch, thereby causing the mass flow of the branch at the low point to be further reduced relative to the mass flow of the branch at the high point, resulting in uneven overall flow diversion. In order to achieve uniform flow diversion, the connection point between the second branch pipe 140 and the manifold 100 is set at a high point, and the connection point between the third branch pipe 150 and the manifold 100 is set at 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 the 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 the high point on the heat exchanger, thereby increasing the mass flow of the heat exchange flow path entering the bottom point, balancing the pressure loss caused by the need to pass through a one-way valve again for this part of the heat exchange flow path, thereby balancing the diversion effect and making the overall diversion more uniform.

[0066] 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.

[0067] 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

[0068] Table 1

[0069] 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

[0070] Table 2

[0071] Optionally, one end of the second branch pipe 140 is connected in parallel with the port of the manifold 100, and one end of the third branch pipe 150 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 check valve 130, further increasing the flow rate entering the second branch pipe 140, better balancing the flow diversion 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 diversion uniformity effect.

[0072] Optionally, the liquid pipe structure of the heat exchanger further includes: a fourth branch pipe, which is arranged on the side wall of the manifold 100 between the third branch pipe 150 and the liquid pipe one-way valve 130 .

[0073] 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.

[0074] 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.

[0075] 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.

[0076] 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.

[0077] 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.

[0078] Optionally, a closing structure 101 is provided at one end of the manifold 100, and one end of the liquid inlet pipe 110 is inserted into the closing structure 101 and welded to the closing structure 101. In this way, by using the closing structure 101 at one end of the manifold 100 to insert part of the liquid inlet pipe 110 into the inside thereof and welding, the stability of the connection between the two can be improved, and the risk of refrigerant leakage can be reduced.

[0079] Optionally, the other end of the header 100 is also provided with a closing structure 101, and one end of the second branch pipe 140 is inserted into the closing structure 101 and welded to the closing structure 101. In this way, the stability of the connection between the header 100 and the second branch pipe 140 can also be improved.

[0080] Optionally, the manifold 100 and the closing structure 101 are integrally formed, so as to effectively simplify the structure, reduce interfaces, improve the overall consistency, and reduce the overall risk of refrigerant leakage.

[0081] It can be understood that the closing structure 101 is a structure in which the diameter of the mouth of the manifold 100 is gradually reduced, and it can be directly formed by the manifold 100 through processes such as stamping or spinning.

[0082] Combination Figure 13-Figure 17 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.

[0083] 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.

[0084] 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.

[0085] 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.

[0086] Optionally, the manifold assembly further includes a liquid inlet pipe 110. The liquid inlet pipe 110 includes a bend portion 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 bend portion 111, and enters the manifold 100 through the discrete element 160.

[0087] Optionally, the bend 111 of the liquid inlet pipe 110 may be a U-shaped pipe. The refrigerant flows in the U-shaped bend 111, which has a certain centrifugal and accelerating effect, and is conducive to liquid separation between different branch pipes after entering the manifold 100.

[0088] Taking the U-shaped bending portion 111 of the liquid inlet pipe 110 as an example, after the refrigerant passes through the U-shaped bending portion 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. 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.

[0089] 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.

[0090] 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.

[0091] Optionally, the bending portion 111 is an arc-shaped structure, the curvature of the arc-shaped structure is r, and the distance between the bending portion 111 and the first connecting point 112 of the outflow pipe section 113 and the discrete element 160 is H, wherein the larger r is, the larger H is.

[0092] The greater the curvature r of the bend 111, the greater the curvature of the bend 111, and thus the greater the centrifugal effect on the refrigerant. At this time, the distance H between the bend 111 and the first connection 112 of the outflow pipe section 113 and the discrete element 160 can be set according to 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 r is, the greater H is, 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.

[0093] Optionally, the distance between the bottom end of the discrete element 160 and the bottom end of the bending portion 111 is h1, where h1≥50 mm. Fig.14 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 bending portion 111 and the refrigerant can fully play its role, so that the setting of the discrete element 160 does not increase the resistance to the refrigerant separated from the bending portion 111.

[0094] Optionally, the distance between the first connecting point 112 of the bend 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 the separation and acceleration of the bend 111. Optionally, h2≥10mm, or h2≥20mm.

[0095] 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.17 As shown in C and D, or, the shape of the filter mesh is irregular, such as Fig.17As shown in B. It can be understood that the filter mesh is the aforementioned liquid balancing hole.

[0096] 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.17 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.16 shown.

[0097] 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.

[0098] 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.

[0099] 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.

[0100] 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.

[0101] Optionally, the discrete element 160 is disposed between the first connecting point 112 between the bending portion 111 and the outflow pipe segment 113 and the second connecting point 121 between the first branch pipe 120 and the manifold 100 .

[0102] 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.

[0103] 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 Fig.13 At the location pointed to by 101.

[0104] Optionally, the first liquid inlet end 101 is a lower liquid inlet of the manifold 100 .

[0105] 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 molding method of the manifold component.

[0106] Optionally, the distance between the first connection point 112 between the bent portion 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 dispersed by the discrete elements 160 flows into the first branch pipe 120 again. Optionally, e≥30mm.

[0107] Combination Figure 18-Figure 21 As shown, an embodiment of the present disclosure provides a variable split heat exchanger including: the liquid pipe structure of the heat exchanger mentioned above.

[0108] The variable split flow heat exchanger provided in this embodiment adopts the liquid pipe structure of the heat exchanger described above, and its effects are the same as those described above for the liquid pipe structure of the heat exchanger, which will not be described in detail here.

[0109] Optionally, the variable split flow heat exchanger further includes: a plurality of heat exchange flow paths composed of a gas pipe structure of the heat exchanger and a heat exchange pipe 300. In this way, a complete variable split flow heat exchange structure can be formed, so that the variable split flow heat exchanger can have the purpose of having 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.

[0110] Combination Fig.18 Optionally, the air pipe structure of the heat exchanger includes an air collecting pipe 200, an air inlet pipe 210, an air pipe one-way valve 220, a first diverter pipe 230, a second diverter pipe 240 and a third diverter pipe 250. The air inlet pipe 210 is connected to one end of the air collecting pipe 200, the air pipe one-way valve 220 is arranged on the air collecting pipe 200, and its conducting direction is one-way conduction from the other side to the side where the air inlet pipe 210 is arranged, the first diverter pipe 230 is connected between the air inlet pipe 210 and the air pipe one-way valve 220, the second diverter pipe 240 is connected to the air collecting pipe 200 on the other side of the air pipe one-way valve 220, and the third diverter pipe 250 is connected to the air collecting pipe 200 on the lower side of the second diverter pipe 240. In this way, when the first branch pipe 230, the second branch pipe 240 and the third branch pipe 250 converge into the collecting pipe 200 at the same time, the air pipe one-way valve 220 can be turned on to directly discharge the refrigerant through the intake pipe 210, which is conducive to the side-by-side flow of multiple heat exchange paths. Conversely, when the refrigerant flows into the collecting pipe 200 from the intake pipe 210, the air pipe one-way valve 220 can be closed, so that the refrigerant first passes through the first branch pipe 230 and then through the second branch pipe 240 and finally through the third branch pipe 250, forming a series of heat exchange paths, thereby having different numbers of heat exchange paths under cooling and heating conditions, better meeting the different requirements of cooling conditions and cooling conditions for the number of heat exchange paths, and improving the overall performance of the variable split heat exchanger.

[0111] In order to further improve the consistency of the product, the first shunt pipe 230, the second shunt pipe 240 and the third shunt 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.

[0112] It can be understood that the connection mode between the first branch pipe 230, the second branch pipe 240 and the third branch pipe 250 and the gas 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.

[0113] The multiple 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 shunt pipe 250, the second heat exchange flow path 320 is connected between the second branch pipe 140 and the second shunt pipe 240, and the third heat exchange flow path 330 is connected between the third branch pipe 150 and the first shunt pipe 230. In this way, by setting a plurality of heat exchange flow paths respectively correspondingly arranged between the branch pipes and the shunt pipes, different flow paths can be generated under cooling conditions and heating conditions, thereby improving the overall performance of the variable shunt heat exchanger.

[0114] 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.

[0115] 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 gas pipe check valve 220 in the second heat exchange flow path 320 and the first heat exchange flow path 310, and improve the uniformity of the diversion.

[0116] Combination Fig. 20 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 one-way valve 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 branch pipe 230, the second branch pipe 240 and the third branch pipe 250 respectively. At this time, the air pipe one-way valve 220 in the collecting pipe 200 is also in a conducting 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.

[0117] Combination Fig.21As shown, in the case where the variable flow 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 gas pipe check valve 220 is in a non-conducting state. After the refrigerant enters the collecting pipe 200 and is in the upper half of the gas pipe check valve 220, it flows into the third heat exchange flow path 330 through the first split 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 check valve 130 in the collecting pipe 100 is also in a non-conducting state under the action of pressure, and the refrigerant continues to enter the second branch pipe 140 and flows into the second heat exchange flow path 330. After heat exchange in the flow path 320, it flows into the lower half of the collecting pipe 200 at the lower side of the gas pipe one-way valve 220 through the second branch pipe 240, and continues to flow into the third branch pipe 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 one-way valve 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.

[0118] In some embodiments, an air conditioner includes: the variable split heat exchanger described above.

[0119] The effects of the air conditioner provided by the embodiment of the present disclosure are the same as those described above for the liquid pipe structure of the heat exchanger, and are not described in detail here.

[0120] 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 liquid pipe structure of a heat exchanger, characterized in that: include: A header (100); A liquid inlet pipe (110) connected to one end of the manifold (100); A first branch pipe (120) connected to a side wall of the header (100) and in communication with the interior of the header (100); The angle between the projections 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.

2. The liquid pipe structure of the heat exchanger according to claim 1, characterized in that: The angle between the projections 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.

3. The liquid pipe structure of the heat exchanger according to claim 2, characterized in that: The angle between the projections 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.

4. The liquid pipe structure of the heat exchanger according to claim 1, characterized in that: The distance from the connection point between the first branch pipe (120) and the manifold (100) to the end of the manifold (100) connected to the liquid inlet pipe (110) is greater than or equal to 25 mm and less than or equal to 100 mm.

5. The liquid pipe structure of the heat exchanger according to claim 4, characterized in that: The distance from the connection point between the first branch pipe (120) and the manifold (100) to the end of the manifold (100) connected to the liquid inlet pipe (110) is greater than or equal to 70 mm and less than or equal to 90 mm.

6. The liquid pipe structure of the heat exchanger according to any one of claims 1 to 5, characterized in that: Also includes: A liquid pipe one-way valve (130) is arranged on the manifold (100) and is used to allow the manifold (100) to conduct one-way from one end where the liquid inlet pipe (110) is arranged to the other end, wherein the first branch pipe (120) is connected between the liquid pipe one-way valve (130) and the liquid inlet pipe (110); The second branch pipe (140) is connected to the manifold (100) on the conducting direction side of the liquid pipe one-way valve (130).

7. The liquid pipe structure of the heat exchanger according to claim 6, characterized in that: Also includes: The third branch pipe (150) is also connected to the collecting pipe (100) on the conducting direction side of the liquid pipe one-way valve (130), and the other end of the third branch pipe (150) is respectively connected to different heat exchange flow 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).

8. The liquid pipe structure of the heat exchanger according to claim 7, characterized in that: 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).

9. The liquid pipe structure of the heat exchanger according to claim 7, characterized in that: The connection point between the second branch pipe (140) and the header (100) is higher than the connection point between the third branch pipe (150) and the header (100); the height of the other end of the second branch pipe (140) is lower than the height of the other end of the third branch pipe (150).

10. The liquid pipe structure of the heat exchanger according to claim 9, characterized in that: One end of the second branch pipe (140) is connected in parallel to the port of the header (100), and one end of the third branch pipe (150) is vertically connected to the side wall of the header (100).

11. The liquid pipe structure of the heat exchanger according to any one of claims 1 to 5, characterized in that: A connecting hole is provided on the collecting pipe (100), and the end of the first branch pipe (120) is butted against the connecting hole.

12. The liquid pipe structure of the heat exchanger according to any one of claims 1 to 5, characterized in that: The diameter of the liquid inlet pipe (110) is smaller than the diameter of the header pipe (100), and one end of the liquid inlet pipe (110) is inserted into one end of the header pipe (100).

13. The liquid pipe structure of the heat exchanger according to claim 12, characterized in that: One end of the collecting pipe (100) is provided with a closing structure (101), and one end of the liquid inlet pipe (110) is inserted into the closing structure (101) and welded to the closing structure (101).

14. A variable split flow heat exchanger, characterized in that: The liquid pipe structure of the heat exchanger comprises the liquid pipe structure of any one of claims 1 to 13.

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

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