Flow dividing assembly, heat exchanger and air conditioner

Abstract

The invention provides a flow dividing assembly, a heat exchanger and an air conditioner. The flow dividing assembly comprises a flow collecting pipe, a flow divider and a flow disturbing assembly; the flow divider is provided with a refrigerant inlet and a refrigerant outlet, and the flow collecting pipe is provided with refrigerant liquid dividing holes. And one end of the turbulent flow assembly communicates with the refrigerant outlet, the other end of the turbulent flow assembly communicates with the refrigerant liquid separation hole, a refrigerant flows into the flow divider through the refrigerant inlet, the refrigerant is subjected to first turbulent flow in the flow divider, and the refrigerant spirally flows in the turbulent flow assembly to be subjected to second turbulent flow. The flow divider conducts primary flow division on the refrigerant, concentrated impact of the refrigerant is reduced, primary distribution is achieved, then the turbulent flow assembly further weakens the influence of gravity on the refrigerant through centrifugal force generated by spiral flow, the refrigerant is evenly dispersed, and re-optimization is completed.

Description

Technical Field

[0001] This invention belongs to the field of air conditioner technology, specifically relating to a flow distribution component, a heat exchanger, and an air conditioner. Background Technology

[0002] Commonly used heat exchangers in air conditioning systems mainly include finned tube heat exchangers and microchannel heat exchangers. Compared with finned tube heat exchangers, microchannel heat exchangers can effectively reduce refrigerant charge and improve economy, attracting widespread attention and research from enterprises. Microchannel heat exchangers have multiple branches, and the manifold and microchannel flat tubes have resistance. When the heat exchanger is used as an evaporator, the distributor assembly causes uneven refrigerant distribution when distributing the refrigerant to the microchannel flat tubes. Uneven airflow distribution on the windward side of the heat exchanger directly affects its heat exchange efficiency, leading to increased power consumption and reduced economy and comfort. Therefore, it is necessary to distribute the refrigerant evenly to each inlet flat tube.

[0003] One related technology provides a microchannel heat exchanger that uses a distributor to divide the total refrigerant flow into four paths. The flat tubes of the heat exchanger are divided into four zones according to different proportions. Each zone's manifold corresponds to a refrigerant branch, and the refrigerant on each branch is further distributed to the flat tubes through a spray baffle. This technology solves the problem of uneven refrigerant distribution in existing microchannel heat exchangers for top-discharge air conditioners. However, the excessive number of internal zones in the manifold and the complex structure still result in uneven spraying from the spray holes. When the air conditioner is heating, the uneven distribution of refrigerant to the microchannel flat tubes during distribution in the outdoor unit's heat exchanger's manifold leads to low heat exchanger performance. Summary of the Invention

[0004] This invention provides a flow distribution component, a heat exchanger, and an air conditioner, which can solve the technical problem of uneven refrigerant distribution to each microchannel flat tube when the refrigerant is distributed in the flow distribution pipe of the outdoor unit heat exchanger.

[0005] This invention provides a flow splitting assembly, which includes a manifold, a flow splitter, and a flow disturbance component;

[0006] The distributor is provided with a refrigerant inlet and a refrigerant outlet, and the manifold has a refrigerant distribution hole;

[0007] One end of the turbulence component is connected to the refrigerant outlet, and the other end of the turbulence component is connected to the refrigerant distribution hole. The refrigerant flows into the distributor through the refrigerant inlet. The refrigerant undergoes a first turbulence in the distributor, and then a second turbulence occurs in the turbulence component through spiral flow.

[0008] In some embodiments, the refrigerant distribution hole includes at least a first distribution hole and a second distribution hole. In the axial direction of the manifold, the first distribution hole and the second distribution hole are spaced apart on the manifold. The opening cross-sectional area of ​​the first distribution hole and the second distribution hole is proportional to the airflow distribution in the corresponding area of ​​the heat exchanger, and each distribution hole is connected to one of the turbulence components.

[0009] In some embodiments, the refrigerant distribution hole includes a first distribution hole, a second distribution hole, and a third distribution hole. In the axial direction of the manifold, the second distribution hole is located in the middle of the manifold, and the first and third distribution holes are respectively located on both sides of the second distribution hole. The second distribution hole has the largest opening cross-sectional area.

[0010] In some embodiments, the turbulence assembly includes a turbulence shell and a swirling element, one end of the swirling element being connected to the refrigerant outlet and the other end of the swirling element being connected to the turbulence shell; the turbulence shell is connected to the manifold and has a communication port that is connected to the refrigerant distribution hole.

[0011] In some embodiments, the swirling element includes a swirling shell and helical blades, the helical blades being installed in the swirling shell, and a helical flow channel being formed between the outer edge of the helical blades and the inner wall of the swirling shell; a first end of the swirling shell is connected to the refrigerant outlet, a second end of the swirling shell is connected to the turbulence shell, and a portion of the helical blades extends into the cavity of the turbulence shell.

[0012] In some embodiments, the swirl element further includes an end cap, which is detachably connected to the first end of the swirl shell. The end cap has an end cap hole that communicates with the refrigerant outlet and can adjust the refrigerant flow rate into the swirl shell.

[0013] In some embodiments, the turbulence shell has a gradually increasing flared structure along the refrigerant outflow direction, and the larger end of the turbulence shell has the communication port.

[0014] In some embodiments, the turbulence shell has a fan-shaped structure, and a fan-shaped flow region is formed in the inner cavity of the turbulence shell. The swirling element is installed on the end face of the turbulence shell.

[0015] In some embodiments, the distributor includes a distributor body, a refrigerant inlet pipe, and a refrigerant outlet pipe. One end of the refrigerant inlet pipe has the refrigerant inlet, and the other end of the refrigerant inlet pipe is connected to the distributor body. The refrigerant outlet pipe includes a first branch pipe, a second branch pipe, and a third branch pipe. One end of the first branch pipe, the second branch pipe, and the third branch pipe are all connected to the separator body. The other end of the first branch pipe is connected to the turbulence-inducing component corresponding to the first liquid distribution hole. The other end of the second branch pipe is connected to the turbulence-inducing component corresponding to the second liquid distribution hole. The other end of the third branch pipe is connected to the turbulence-inducing component corresponding to the third liquid distribution hole.

[0016] In some embodiments, with the longitudinal section of the manifold as the projection plane, the first liquid distribution hole is located above the second liquid distribution hole, the third liquid distribution hole is located below the second liquid distribution hole, the diameter of the first branch pipe is d1, the diameter of the second branch pipe is d2, and the diameter of the third branch pipe is d3. The diameters d1, d2, and d3 satisfy the following condition: d2 > d1 > d3.

[0017] In some embodiments, the manifold is provided with two partitions, which divide the inner cavity of the manifold into a first chamber, a second chamber, and a third chamber. The first chamber has a first liquid distribution hole, the second chamber has a second liquid distribution hole, and the third chamber has a third liquid distribution hole.

[0018] It also includes a liquid collection pipe, which comprises a main liquid outlet pipe, a first liquid outlet pipe, a second liquid outlet pipe, and a third liquid outlet pipe. One end of each of the first, second, and third liquid outlet pipes is connected to the main liquid outlet pipe. The other end of the first liquid outlet pipe is connected to the first chamber, the other end of the second liquid outlet pipe is connected to the second chamber, and the other end of the third liquid outlet pipe is connected to the third chamber. The main liquid outlet pipe and the refrigerant inlet pipe are connected by a connecting pipe, and a one-way valve is provided on the connecting pipe.

[0019] A heat exchanger includes a flow splitting assembly, a gas collecting pipe, and a plurality of flat tubes. The flow splitting assembly is the flow splitting assembly described above. One end of the plurality of flat tubes is connected to the gas collecting pipe, and the other end of the plurality of flat tubes is connected to the gas collecting pipe. The number of flat tubes corresponding to the middle part of the gas collecting pipe is greater than the number of flat tubes corresponding to the ends of the gas collecting pipe.

[0020] An air conditioner includes a heat exchanger, wherein the heat exchanger is the heat exchanger described above.

[0021] The present invention provides a flow splitting component, a heat exchanger, and an air conditioner, which have the following beneficial effects:

[0022] In this invention, the turbulence-inducing component in the flow-dividing component primarily serves to further uniformly distribute the refrigerant. By inducing a spiral flow within the refrigerant, the component utilizes the centrifugal force generated by the rotation to create a larger dispersion area, reducing the impact of gravity on the stratification of the refrigerant gas-liquid mixture. This ensures that the microchannel flat tubes within the heat exchanger area receive refrigerant equally, thereby improving heat exchange efficiency and optimizing the overall system performance. The secondary turbulence of the turbulence-inducing component effectively solves the problem of uneven spraying from the injection holes, ensuring that the refrigerant is uniformly distributed before entering the flat tubes. This reduces localized excessively high or low pressures caused by uneven refrigerant distribution, enhancing system reliability. The flow divider and turbulence-inducing component work synergistically. First, the flow divider performs initial refrigerant diversion, reducing concentrated refrigerant impact and achieving initial distribution. Then, the turbulence-inducing component uses the centrifugal force generated by the spiral flow to further reduce the impact of gravity on the refrigerant, resulting in uniform refrigerant dispersion and further optimization. The combination of these two components solves the problem of uneven refrigerant distribution while minimizing additional resistance losses, improving heat exchange efficiency and system performance. Attached Figure Description

[0023] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0024] Figure 1 This is a schematic diagram of a heat exchanger according to an embodiment of the present invention;

[0025] Figure 2 This is a schematic diagram of a shunt component according to an embodiment of the present invention;

[0026] Figure 3 This is a schematic diagram of the manifold according to an embodiment of the present invention;

[0027] Figure 4 This is a schematic diagram of the first to third chambers according to an embodiment of the present invention;

[0028] Figure 5 This is a schematic diagram of the first to third dispensing holes according to an embodiment of the present invention;

[0029] Figure 6 This is a schematic diagram of a shunt according to an embodiment of the present invention;

[0030] Figure 7 This is a schematic diagram of the liquid collection tube according to an embodiment of the present invention;

[0031] Figure 8 This is a schematic diagram of the turbulence-disrupting component according to an embodiment of the present invention;

[0032] Figure 9 This is a schematic diagram of the helical blades extending into the turbulence shell according to an embodiment of the present invention;

[0033] Figure 10 This is a schematic diagram of a swirl element according to an embodiment of the present invention;

[0034] Figure 11 This is an exploded view of the swirl element according to an embodiment of the present invention;

[0035] Figure 12 This is a schematic diagram of three specifications of end caps according to an embodiment of the present invention;

[0036] Figure 13 This is a schematic diagram of the airflow distribution in a heat exchanger according to an embodiment of the present invention.

[0037] Attached Figure: 1-Manifold; 101-Refrigerant distribution hole; 111-First distribution hole; 112-Second distribution hole; 113-Third distribution hole; 102-Separator; 121-First chamber; 122-Second chamber; 123-Third chamber; 2-Diverter; 21-Refrigerant inlet; 201-Diverter body; 202-Refrigerant inlet pipe; 203-Refrigerant outlet pipe; 231-First branch pipe; 232-Second branch pipe; 233-Third branch pipe; 3-Breakflow assembly; 301-Breakflow shell; 311-Connecting port; 302-Swirl element; 321-Swirl shell; 322-Helical blade; 323-End cap; 324-End cap hole; 4-Liquid collecting pipe; 401-Liquid outlet main pipe; 402-First liquid outlet pipe; 403-Second liquid outlet pipe; 404-Third liquid outlet pipe; 405-Connecting pipe; 406-One-way valve; 5-Flat pipe; 6-Gas collecting pipe. Detailed Implementation

[0038] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0039] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0040] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used here to describe the spatial positional relationship of a device or feature as shown in the figure with other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device as described in the figure. For example, if a device in the figure is inverted, a device described as "above" or "on top of" other devices or structures will subsequently be positioned as "below" or "under" other devices or structures.

[0041] See also Figures 1 to 12 As shown, according to an embodiment of the present invention, a flow splitting assembly is provided, which includes a manifold 1, a flow splitter 2, and a flow turbulence assembly 3; the flow splitter 2 is provided with a refrigerant inlet 21 and a refrigerant outlet, and the manifold 1 has a refrigerant dispensing hole 101; one end of the flow turbulence assembly 3 is connected to the refrigerant outlet, and the other end of the flow turbulence assembly 3 is connected to the refrigerant dispensing hole 101. The refrigerant flows into the flow splitter 2 through the refrigerant inlet 21, and the refrigerant undergoes a first flow turbulence in the flow splitter 2, and the refrigerant undergoes a second flow turbulence by spiraling flow in the flow turbulence assembly 3.

[0042] Specifically, during heating, the outdoor heat exchanger acts as an evaporator. The throttled two-phase refrigerant first flows into the distributor 2 through the refrigerant inlet 21. The refrigerant undergoes its first turbulence in the distributor 2. After the initial turbulence, the refrigerant then flows into the turbulence assembly 3. The refrigerant undergoes a second turbulence in the turbulence assembly 3 through spiral flow. The centrifugal force generated by the rotation makes the refrigerant form a larger dispersion area, weakening the influence of gravity and ensuring that the microchannel flat tubes 5 in the corresponding heat exchanger area have an equal chance to obtain refrigerant, which flows into the heat exchanger for evaporative heat exchange and is then discharged from the heat exchanger.

[0043] In this embodiment, the turbulence component 3 primarily serves to further uniformly distribute the refrigerant within the flow distribution assembly. By allowing the refrigerant to flow in a spiral motion, the turbulence component 3 utilizes the centrifugal force generated by the rotation to create a larger dispersion area, reducing the impact of gravity on the stratification of the refrigerant gas-liquid mixture. This ensures that the microchannel flat tubes 5 within the heat exchanger area receive refrigerant equally, thereby improving heat exchange efficiency and optimizing the overall system performance. The secondary turbulence of the turbulence component 3 effectively solves the problem of uneven spraying from the injection holes, ensuring that the refrigerant is uniformly distributed before entering the flat tubes 5. This reduces localized excessively high or low pressures caused by uneven refrigerant distribution, enhancing system reliability. The flow distributor 2 and the turbulence component 3 work synergistically. First, the flow distributor 2 performs initial refrigerant distribution, reducing concentrated refrigerant impact and achieving initial distribution. Then, the turbulence component 3 utilizes the centrifugal force generated by the spiral flow to further reduce the impact of gravity on the refrigerant, ensuring uniform refrigerant dispersion and completing further optimization. The combination of these two components solves the problem of uneven refrigerant distribution while minimizing additional resistance losses, improving heat exchange efficiency and system performance.

[0044] See also Figures 1 to 7 , Figure 13 As shown, the refrigerant distribution hole 101 includes at least a first distribution hole 111 and a second distribution hole 112. In the axial direction of the manifold 1, the first distribution hole 111 and the second distribution hole 112 are spaced apart on the manifold 1. The opening cross-sectional area of ​​the first distribution hole 111 and the second distribution hole 112 is proportional to the air volume distribution in the corresponding area of ​​the heat exchanger, and each distribution hole is connected to a turbulence component 3.

[0045] Specifically, after the refrigerant enters the distributor 2 through the refrigerant inlet 21, the distributor 2 evenly divides the refrigerant into several branches, initially controlling the refrigerant flow rate and laying the foundation for subsequent fine distribution. The initially distributed refrigerant flows into the turbulence-inducing component 3, where centrifugal force is generated by the spiral flow rotation, further refining the uniformity of the gas-liquid mixture. The refrigerant flows out through the first liquid distribution hole 111 and the second liquid distribution hole 112 and enters the flat tube 5. The opening size of the liquid distribution hole is proportional to the airflow distribution in the corresponding area of ​​the heat exchanger, ensuring that the refrigerant flow rate matches the airflow.

[0046] In this embodiment, the refrigerant flow rate is rationally allocated according to the air volume in different areas of the heat exchanger. Areas with high air volume have a greater refrigerant demand; therefore, the cross-sectional area of ​​the liquid distribution orifice is increased to allow more refrigerant to flow into these areas, meeting their heat exchange requirements. Conversely, areas with low air volume have a smaller refrigerant demand; the cross-sectional area of ​​the liquid distribution orifice is correspondingly reduced to decrease the refrigerant inflow, avoid refrigerant waste, and improve refrigerant utilization efficiency. Ensuring that the refrigerant flow rate matches the air volume makes the evaporation and heat exchange process of the refrigerant more efficient in each area of ​​the heat exchanger. The coordinated operation of air volume and refrigerant flow rate facilitates the full absorption or release of heat, reduces local overheating or undercooling, and improves the overall performance of the heat exchanger. This configuration allows the heat exchanger to better adapt to differences in air volume distribution in different areas, achieving rational refrigerant allocation without the need for additional complex structures or control methods. It improves the heat exchanger's adaptability to different operating conditions, ensuring good heat exchange performance under various operating conditions.

[0047] In this embodiment, the distributor 2 first performs preliminary distribution of the refrigerant, ensuring that the refrigerant is evenly distributed from the main pipe to multiple branches. The turbulence-distributing component 3 then homogenizes the refrigerant by generating centrifugal force through spiral flow, further homogenizing the gas-liquid distribution of the refrigerant, reducing the influence of gravity, and ensuring that the refrigerant enters the distribution orifice in a relatively uniform state. The distribution orifice has an opening cross-sectional area proportional to the airflow distribution in the corresponding area of ​​the heat exchanger, achieving precise refrigerant distribution. In areas with high airflow, the distribution orifice opening is large, resulting in a larger refrigerant inflow; in areas with low airflow, the distribution orifice opening is small, resulting in a smaller refrigerant inflow, thus matching the refrigerant flow rate with the airflow to meet the heat exchange needs of different areas. The synergistic effect of these three components (distributor 2, turbulence-distributing component 3, and distribution orifice) realizes the complete process of refrigerant distribution from coarse allocation to uniform optimization and then to precise matching, improving the refrigerant utilization efficiency and heat exchanger performance, and ensuring that the heat exchange effect in each area of ​​the heat exchanger reaches its optimal level.

[0048] It is worth noting that, in conjunction with [see also] Figure 13 As shown, the principle behind setting the distribution orifice according to wind speed in this embodiment is as follows: In areas with high wind speed, the heat transfer coefficient on the wind side is large, and the refrigerant evaporation or condensation heat exchange on the inner side is more rapid. In order to allow more refrigerant to participate in the effective heat exchange process, more refrigerant needs to pass through the flat tube area with high wind speed, so that more refrigerant can be completely evaporated or condensed and subcooled. In areas with low wind speed, less refrigerant flows because the heat exchange capacity in areas with low wind speed is weak, and too much refrigerant will not be completely evaporated or condensed and subcooled. Therefore, the cross-sectional area of ​​the distribution orifice on the distributor 2 corresponding to the flat tube area with high flow rate will be larger, and the cross-sectional area of ​​the distribution orifice on the distributor 2 corresponding to the flat tube area with low flow rate will be smaller. This ensures that the required refrigerant flow rate for each flat tube area is correct and meets the actual needs.

[0049] See also Figures 1 to 7As shown, the refrigerant distribution hole 101 includes a first distribution hole 111, a second distribution hole 112 and a third distribution hole 113. In the axial direction of the manifold 1, the second distribution hole 112 is opened in the middle of the manifold 1, and the first distribution hole 111 and the third distribution hole 113 are respectively opened on both sides of the second distribution hole 112. The second distribution hole 112 has the largest opening cross-sectional area.

[0050] Specifically, the refrigerant first enters the distributor 2, where it undergoes initial turbulence and distribution through its internal structure. Next, the refrigerant flows into the turbulence-inducing component 3, where centrifugal force is generated in the spiral flow, further homogenizing the gas-liquid mixture. Finally, the refrigerant flows into the flat tube 5 through the first distribution hole 111, the second distribution hole 112, and the third distribution hole 113. The second distribution hole 112, located in the middle of the manifold 1, has the largest opening cross-sectional area, corresponding to the area with the largest airflow, thus distributing more refrigerant. The first distribution hole 111 and the third distribution hole 113 are located on the sides, with smaller opening cross-sectional areas, corresponding to areas with smaller airflow.

[0051] In this embodiment, the second dispensing hole 112 is located in the middle of the manifold 1 and has the largest opening cross-sectional area. The first dispensing hole 111 and the third dispensing hole 113 are located on either side of it and have smaller opening cross-sectional areas. This arrangement allows the refrigerant distribution to better meet the needs of the heat exchanger in actual operation. Specifically, since the middle of the manifold 1 is in a critical area of ​​airflow, the air volume is relatively large, and the demand for refrigerant is also higher. The second dispensing hole 112 has the largest opening cross-sectional area, which ensures that more refrigerant flows into the middle area of ​​the heat exchanger, fully meeting the heat exchange needs of this area and improving heat exchange efficiency. At the same time, the first dispensing hole 111 and the third dispensing hole 113 are located on either side of the second dispensing hole 112 and have smaller opening cross-sectional areas, which can provide an appropriate amount of refrigerant to the areas on both sides of the heat exchanger. Combined with the characteristics of airflow distribution, this makes the refrigerant distribution of the entire heat exchanger more reasonable. This layout matches the refrigerant inflow with the heat exchange requirements of each zone of the heat exchanger, avoiding refrigerant waste, optimizing the refrigerant flow path within the heat exchanger, and improving the overall heat exchange performance. Furthermore, this design helps reduce localized overheating or undercooling of the heat exchanger, improving the overall system's operational stability and reliability.

[0052] See also Figures 1 to 7As shown, the distributor 2 includes a distributor body 201, a refrigerant inlet pipe 202, and a refrigerant outlet pipe 203. One end of the refrigerant inlet pipe 202 has a refrigerant inlet 21, and the other end of the refrigerant inlet pipe 202 is connected to the distributor body 201. The refrigerant outlet pipe 203 includes a first branch pipe 231, a second branch pipe 232, and a third branch pipe 233. One end of the first branch pipe 231, the second branch pipe 232, and the third branch pipe 233 is connected to the distributor body. The other end of the first branch pipe 231 is connected to the turbulence-disrupting component 3 corresponding to the first liquid distribution hole 111. The other end of the second branch pipe 232 is connected to the turbulence-disrupting component 3 corresponding to the second liquid distribution hole 112. The other end of the third branch pipe 233 is connected to the turbulence-disrupting component 3 corresponding to the third liquid distribution hole 113.

[0053] Specifically, the refrigerant enters the distributor body 201 from the refrigerant inlet 21 through the refrigerant inlet pipe 202. Inside the distributor body 201, the refrigerant undergoes preliminary diversion and turbulence. The distributor body 201 is designed to distribute the refrigerant evenly to each branch, reducing the possibility of refrigerant concentrating on a particular area. The distributor body 201 evenly distributes the refrigerant to the first branch pipe 231, the second branch pipe 232, and the third branch pipe 233, with the other end of each branch pipe connected to the corresponding turbulence component 3. The refrigerant flows from the branch pipes into the turbulence component 3, where it undergoes spiral flow, generating centrifugal force. This centrifugal force further homogenizes the gas-liquid mixture of the refrigerant, weakening the influence of gravity on the refrigerant distribution. The turbulence component 3 ensures that the refrigerant achieves a high degree of uniformity before entering the distribution holes. After being processed by the turbulence component 3, the refrigerant flows into the corresponding flat pipe 5 through the first distribution hole 111, the second distribution hole 112, and the third distribution hole 113. The second liquid distribution hole 112 is located in the middle of the manifold 1, with the largest opening cross-sectional area, corresponding to the area with the largest air volume in the middle of the heat exchanger. The first liquid distribution hole 111 and the third liquid distribution hole 113 are located on both sides of the second liquid distribution hole 112, with smaller opening cross-sectional areas, corresponding to the areas with smaller air volume on both sides of the heat exchanger.

[0054] In this embodiment, the distributor body 201 receives refrigerant through the refrigerant inlet pipe 202 and performs preliminary diversion and turbulence on the refrigerant. The purpose of this step is to evenly distribute the refrigerant into the three branch pipes, ensuring that the refrigerant flow rate in each branch pipe is approximately equal. The arrangement of the distributor 2 reduces the non-uniformity of the refrigerant before it enters the turbulence assembly 3. Each branch pipe is connected to a turbulence assembly 3. In the turbulence assembly 3, the refrigerant undergoes spiral flow, generating centrifugal force. This centrifugal force further homogenizes the gas-liquid mixture of the refrigerant, weakening the influence of gravity on the refrigerant distribution. The turbulence assembly 3 refines the gas-liquid ratio of the refrigerant, ensuring that the refrigerant achieves higher uniformity before entering the dispensing orifice. The opening cross-sectional area of ​​the dispensing orifice is proportional to the airflow distribution in the corresponding area of ​​the heat exchanger. The second dispensing orifice 112 is located in the middle of the manifold 1, with the largest opening cross-sectional area, corresponding to the area with the largest airflow, ensuring that more refrigerant flows into the central area. The first dispensing orifice 111 and the third dispensing orifice 113 are located on either side of the second dispensing orifice 112, with smaller opening cross-sectional areas, corresponding to areas with smaller airflow, ensuring that the refrigerant inflow matches the airflow. The three branch pipes disperse the refrigerant from the distributor body 201 to different turbulence components 3, providing a multi-point input basis for further refined refrigerant distribution, ensuring that the refrigerant can simultaneously reach multiple areas of the heat exchanger. The three dispensing orifices adjust their opening cross-sectional areas according to the airflow distribution in different areas of the heat exchanger, achieving on-demand refrigerant distribution. This ensures that the refrigerant inflow matches the actual demand, avoids refrigerant waste, and improves heat exchange efficiency. This synergistic effect forms a hierarchical optimization mechanism, enabling the refrigerant to not only be evenly distributed but also accurately meet the needs of each area of ​​the heat exchanger, thereby significantly improving heat exchange efficiency and system performance.

[0055] See also Figures 1 to 7 As shown, with the longitudinal section of the manifold 1 as the projection plane, the first liquid distribution hole 111 is located above the second liquid distribution hole 112, and the third liquid distribution hole 113 is located below the second liquid distribution hole 112. The diameter of the first branch pipe 231 is d1, the diameter of the second branch pipe 232 is d2, and the diameter of the third branch pipe 233 is d3. The diameters d1, d2, and d3 satisfy the following condition: d2 > d1 > d3.

[0056] In this embodiment, this configuration achieves precise refrigerant flow distribution by adjusting the branch pipe diameter and the position of the dispensing orifice. The larger-diameter second branch pipe 232 provides more refrigerant to the central second dispensing orifice 112, matching the larger airflow in this area and ensuring efficient heat exchange. Simultaneously, the smaller-diameter first branch pipe 231 and third branch pipe 233 supply appropriate amounts of refrigerant to the upper and lower dispensing orifices, respectively, to accommodate the smaller airflow in these areas. Furthermore, the difference in branch pipe diameter helps optimize the inflow conditions of the turbulence-inducing component 3, enabling the refrigerant to generate a more stable turbulence effect upon entering the component, further improving heat exchange efficiency. Overall, this configuration enhances the performance of the heat exchanger, allowing it to better adapt to airflow distribution in different areas and achieve efficient energy utilization.

[0057] See also Figures 1 to 7 As shown, the manifold 1 is provided with two partitions 102, which divide the inner cavity of the manifold 1 into a first chamber 121, a second chamber 122, and a third chamber 123. The first chamber 121 has a first dispensing hole 111, the second chamber 122 has a second dispensing hole 112, and the third chamber 123 has a third dispensing hole 113. It also includes a collection pipe 4, which includes a main outlet pipe 401, a first outlet pipe 402, a second outlet pipe 403, and a third outlet pipe 404. One end of the liquid pipe 404, the first liquid outlet pipe 402, the second liquid outlet pipe 403, and the third liquid outlet pipe 404 are all connected to the main liquid outlet pipe 401. The other end of the first liquid outlet pipe 402 is connected to the first chamber 121, the other end of the second liquid outlet pipe 403 is connected to the second chamber 122, and the other end of the third liquid outlet pipe 404 is connected to the third chamber 123. The main liquid outlet pipe 401 and the refrigerant inlet pipe 202 are connected by a connecting pipe 405, and a one-way valve 406 is provided on the connecting pipe 405.

[0058] Specifically, during heating, the refrigerant flows in from the refrigerant inlet pipe 202, first entering the distributor 2. After the distributor 2 divides the refrigerant, two partition plates 102 inside the manifold 1 divide the inner cavity into a first chamber 121, a second chamber 122, and a third chamber 123. The refrigerant flows into the manifold 1 through the first liquid distribution hole 111, the second liquid distribution hole 112, and the third liquid distribution hole 113, respectively, and then flows into the flat tube 5 for heat exchange. During cooling, the refrigerant flows in the opposite direction. After heat exchange in the flat tube 5, the refrigerant flows into the three chambers through the first liquid distribution hole 111, the second liquid distribution hole 112, and the third liquid distribution hole 113, respectively. The refrigerant then flows into the first outlet pipe 402 to the third outlet pipe 404, and after converging in the main outlet pipe 401, it flows back into the refrigerant inlet pipe 202.

[0059] In this embodiment, the main outlet pipe 401 serves as the final confluence channel for the refrigerant. The refrigerant flowing from the three chambers is collected and then flows into the refrigerant inlet pipe 202 via the connecting pipe 405. The main outlet pipe 401 reduces resistance during refrigerant flow, ensuring smooth refrigerant flow. The one-way valve 406 on the connecting pipe 405 ensures that the refrigerant can only flow from the main outlet pipe 401 to the refrigerant inlet pipe 202, preventing reverse flow and improving system safety. The first outlet pipe 402, the second outlet pipe 403, and the third outlet pipe 404 are connected to the three chambers of the manifold 1, ensuring that the refrigerant can efficiently flow into the main outlet pipe 401 after heat exchange. This arrangement reduces resistance during refrigerant flow and ensures smooth refrigerant flow.

[0060] It is worth noting that, depending on the operating conditions, the refrigerant can only flow into the distributor 2 in one direction or be discharged from the liquid outlet main pipe 401. The function of the one-way valve 406 is to ensure that the refrigerant can only flow in one direction.

[0061] See also Figures 8 to 12 As shown, the turbulence assembly 3 includes a turbulence shell 301 and a swirling element 302. One end of the swirling element 302 is connected to the refrigerant outlet, and the other end of the swirling element 302 is connected to the turbulence shell 301. The turbulence shell 301 is connected to the manifold 1 and has a communication port 311, which is connected to the refrigerant distribution hole 101.

[0062] Specifically, the refrigerant flows in from the refrigerant inlet pipe 202, first entering the distributor body 201. The distributor 2 evenly distributes the refrigerant into three branch pipes, from which it flows into the swirling element 302. One end of the swirling element 302 is connected to the refrigerant outlet, and the other end is connected to the turbulence shell 301. The swirling element 302 guides the refrigerant into a spiral flow, generating centrifugal force. The centrifugal force further homogenizes the gas-liquid distribution of the refrigerant and weakens the effect of gravity on the stratification of the refrigerant gas-liquid mixture. The other end of the swirling element 302 is connected to the turbulence shell 301. The turbulence shell 301 has a certain space inside, allowing the refrigerant to be further mixed and homogenized within it. The turbulence shell 301 reduces the non-uniformity of the refrigerant before entering the distribution hole, ensuring that the refrigerant enters the distribution hole in a relatively uniform state. The refrigerant processed by the turbulence-disrupting component 3 enters the manifold 1 through the connecting port 311. The manifold 1 has two partition plates 102 that divide the inner cavity into a first chamber 121, a second chamber 122, and a third chamber 123. Each chamber has a dispensing hole through which the refrigerant flows into its corresponding chamber. The second dispensing hole 112 is located in the middle of the manifold 1, with the largest opening cross-sectional area, corresponding to the area with the largest airflow in the middle of the heat exchanger. The second dispensing hole 112 allows more refrigerant to flow into the central area, ensuring that the heat exchange demand in this area is met. The first dispensing hole 111 and the third dispensing hole 113 are located above and below the second dispensing hole 112, respectively, with smaller opening cross-sectional areas, corresponding to the areas with smaller airflow on both sides of the heat exchanger. These dispensing holes allow less refrigerant to flow into the side areas, ensuring that the refrigerant flow rate matches the airflow distribution. After flowing into each chamber of the manifold 1 through the dispensing holes, the refrigerant then flows into the corresponding flat tube 5 for heat exchange. During cooling, the refrigerant flows in the opposite direction to that during heating. After heat exchange in the flat tube 5, the refrigerant flows into the three chambers through the first liquid distribution hole 111, the second liquid distribution hole 112, and the third liquid distribution hole 113, respectively. Then, the refrigerant flows into the main liquid outlet pipe 401 through the first liquid outlet pipe 402, the second liquid outlet pipe 403, and the third liquid outlet pipe 404. After converging in the main liquid outlet pipe 401, it flows into the refrigerant inlet pipe 202 through the connecting pipe 405. The one-way valve 406 installed on the connecting pipe 405 ensures that the refrigerant can only flow from the main liquid outlet pipe 401 to the refrigerant inlet pipe 202, preventing the refrigerant from flowing in reverse.

[0063] In this embodiment, the refrigerant gas-liquid mixture is further refined through spiral flow, resulting in a more uniform distribution of the gas and liquid phases. This helps improve heat exchange efficiency because a uniform refrigerant distribution ensures consistent evaporative heat exchange efficiency across all parts of the heat exchanger. The refrigerant processed by the swirling element 302 enters the turbulence shell 301, which has a certain internal space to allow further mixing and homogenization of the refrigerant. This arrangement reduces the non-uniformity of the refrigerant before entering the distribution hole, ensuring that the refrigerant enters the distribution hole in a relatively uniform state. The turbulence shell 301 acts as a buffer, reducing the impact force of the refrigerant when entering the distribution hole and further optimizing the refrigerant distribution. Through the action of the swirling element 302 and the turbulence shell 301, the refrigerant achieves a high degree of uniformity before entering the distribution hole. This uniform refrigerant distribution ensures consistent evaporative heat exchange efficiency across all parts of the heat exchanger, thereby improving the overall performance of the heat exchanger. Uniform refrigerant distribution can prevent localized overheating or undercooling of the heat exchanger, reduce thermal stress and uneven condensation, and extend the service life of the heat exchanger. The spiral flow of the swirl element 302 can effectively solve the problem of uneven spraying from the injection holes, ensuring that the refrigerant is evenly distributed before entering the distribution hole. This can reduce localized excessively high or low pressure caused by uneven refrigerant distribution, enhancing the reliability of the system. The arrangement of the swirl element 302 and the baffle shell 301 can dynamically adjust the refrigerant distribution according to the airflow distribution in each area of ​​the heat exchanger, ensuring that the system maintains high heat exchange efficiency under different operating conditions. In this embodiment, when the refrigerant enters the swirl element 302, it only has the axial velocity of the baffle shell 301. Under the action of the spiral, after swirling, it undergoes centrifugal motion. The centrifugal motion is parallel to the diameter of the baffle shell 301 and is a portion of the kinetic energy converted. This portion of the kinetic energy is the refrigerant moving axially from the inlet of the front end cover hole 324, thus reducing the axial velocity of the refrigerant.

[0064] See also Figures 8 to 12 As shown, the swirling element 302 includes a swirling shell 321 and a helical blade 322. The helical blade 322 is installed in the swirling shell 321, and a helical flow channel is formed between the outer edge of the helical blade 322 and the inner wall of the swirling shell 321. The first end of the swirling shell 321 is connected to the refrigerant outlet, the second end of the swirling shell 321 is connected to the turbulence shell 301, and part of the helical blade 322 extends into the cavity of the turbulence shell 301.

[0065] Specifically, refrigerant flows into the first end of the vortex shell 321 from the branch pipe. A helical blade 322 is installed inside the vortex shell 321. The first end of the vortex shell 321 is connected to the refrigerant outlet, ensuring that the refrigerant can smoothly enter the vortex element 302. The helical blade 322 is installed in the vortex shell 321, and its outer edge forms a helical flow channel with the inner wall of the vortex shell 321. When the refrigerant enters the vortex shell 321, the helical blade 322 guides the refrigerant to flow in a helical pattern, generating centrifugal force. The refrigerant flows in a helical pattern within the helical flow channel. This flow pattern further homogenizes the gas-liquid distribution of the refrigerant and weakens the influence of gravity on the stratification of the refrigerant gas-liquid mixture. The arrangement of the helical blade 322 ensures that the refrigerant achieves a high degree of uniformity before entering the turbulence shell 301. The second end of the swirling shell 321 is connected to the turbulence shell 301, and part of the spiral blades 322 extend into the chamber of the turbulence shell 301. This arrangement ensures that the refrigerant is still affected by the spiral blades 322 when entering the turbulence shell 301, further optimizing the flow state of the refrigerant. The turbulence shell 301 has a certain space inside, allowing the refrigerant to be further mixed and homogenized within it. The arrangement of the turbulence shell 301 can reduce the non-uniformity of the refrigerant before entering the distribution hole, ensuring that the refrigerant enters the distribution hole in a relatively uniform state. The refrigerant treated by the turbulence shell 301 enters the manifold 1 through the connecting port 311. The manifold 1 is provided with two partition plates 102, which divide the inner cavity into a first chamber 121, a second chamber 122, and a third chamber 123. Each chamber has a distribution hole, through which the refrigerant flows into the corresponding chamber.

[0066] In this embodiment, the helical blades 322 are installed inside the vortex shell 321, forming a helical flow channel between their outer edge and the inner wall of the vortex shell 321. When the refrigerant flows into the vortex shell 321 from the refrigerant outlet, the helical blades 322 guide the refrigerant to flow helically along the helical flow channel. This helical flow can effectively increase the flow path length of the refrigerant, causing the refrigerant to generate centrifugal force during the flow process. The centrifugal force can further homogenize the gas-liquid distribution of the refrigerant and weaken the influence of gravity on the stratification of the refrigerant gas-liquid mixture. Through helical flow, the gas-liquid mixture of the refrigerant is refined, making the gas and liquid phases more evenly distributed. This helps to improve heat exchange efficiency because a uniform refrigerant distribution can ensure that the evaporation heat exchange efficiency of each part of the heat exchanger is consistent. The centrifugal force generated by the helical flow can effectively reduce the non-uniformity of the refrigerant before entering the turbulence shell 301. With this setting, the refrigerant has already achieved a high degree of uniformity when entering the turbulence shell 301, providing a good foundation for further optimization. The spiral flow of the 322 spiral blades can effectively solve the problem of uneven spraying from the injection hole, ensuring that the refrigerant is evenly distributed before entering the distribution hole. This can reduce local pressure that is too high or too low due to uneven refrigerant distribution and enhance the reliability of the system.

[0067] In other embodiments, the swirling element 302 can consist of spiral grooves and guide vanes. The spiral grooves are spirally distributed along the inner wall of the swirling shell 321, and the guide vanes extend outward from the bottom of the spiral grooves, forming multiple guiding channels. The refrigerant flows into the swirling shell 321 from the refrigerant outlet and flows spirally along the spiral grooves. The guide vanes can further guide the refrigerant flow, increasing the flow path length and generating centrifugal force, thereby homogenizing the gas-liquid distribution of the refrigerant. The swirling element 302 can also employ a multi-stage swirling structure, including multiple swirling shells 321 and spiral blades 322. Each swirling shell 321 and spiral blade 322 forms a swirling unit. Multiple swirling units are connected in series or parallel. The refrigerant flows into the first swirling unit from the refrigerant outlet, generates spiral flow through the spiral blades 322, and then sequentially passes through multiple swirling units, further optimizing the gas-liquid distribution of the refrigerant. This multi-stage swirling structure can generate centrifugal force multiple times, further homogenizing the gas-liquid distribution of the refrigerant.

[0068] See also Figures 8 to 12 As shown, the swirl element 302 also includes an end cap 323, which is detachably connected to the first end of the swirl shell 321. The end cap 323 is provided with an end cap hole 324, which is connected to the refrigerant outlet. The end cap hole 324 can adjust the refrigerant flow rate into the swirl shell 321.

[0069] In this embodiment, the end cap 323 is provided with an end cap hole 324, which communicates with the refrigerant outlet. By adjusting the size or shape of the end cap hole 324, the refrigerant flow rate into the vortex shell 321 can be controlled. This flow rate adjustment function can flexibly adjust the refrigerant distribution according to different operating conditions, ensuring that the system maintains optimal heat exchange efficiency under various operating conditions. The end cap 323 and the first end of the vortex shell 321 are detachably connected, facilitating the adjustment or replacement of the end cap hole 324. This design allows for convenient operation when the refrigerant flow rate needs to be adjusted, without replacing the entire vortex element 302, reducing maintenance costs and operational complexity. By adjusting the flow rate of the end cap hole 324, the distribution of refrigerant within the vortex shell 321 can be further optimized. Ensuring that the refrigerant has a suitable flow rate when entering the vortex shell 321 helps the vortex element 302 generate better spiral flow, thereby homogenizing the gas-liquid distribution of the refrigerant. The adjustability of the end cap hole 324 allows the system to adapt to different operating conditions. For example, under different ambient temperatures, airflow distributions, or heat exchange requirements, the refrigerant distribution can be optimized by adjusting the flow rate of the end cap orifice 324, ensuring that the system is always in a state of high-efficiency operation.

[0070] As a specific implementation method, this embodiment has three sets of turbulence components 3 corresponding to the liquid distribution hole. The three turbulence components 3 are equipped with end caps 323 of three different specifications according to the different refrigerant distribution requirements. The end cap holes 324 on the end caps 323 are of different sizes. The larger the diameter of the end cap hole 324, the greater the refrigerant flow rate.

[0071] See also Figures 8 to 12 As shown, along the refrigerant outflow direction, the turbulence shell 301 has a gradually increasing flared structure, and the large end of the turbulence shell 301 has a connecting port 311.

[0072] Specifically, the refrigerant, guided by the helical blades 322 in the swirl element 302, generates a spiral flow and centrifugal force, making the gas-liquid mixture of the refrigerant more uniform. Part of the helical blades 322 extend into the chamber of the turbulence shell 301, ensuring that the refrigerant is still influenced by the helical blades 322 when entering the turbulence shell 301. After flowing out of the swirl element 302, the refrigerant enters the smaller end of the turbulence shell 301. Due to the gradually increasing flared structure of the turbulence shell 301, the flow path of the refrigerant gradually widens as it enters the turbulence shell 301. The flared structure of the turbulence shell 301 causes the refrigerant to gradually slow down and further mix during flow. The flared structure reduces the non-uniformity of the refrigerant before entering the distribution hole, ensuring that the refrigerant enters the distribution hole in a more uniform state. The larger end of the turbulence shell 301 has a connecting port 311. After further homogenization in the turbulence shell 301, the refrigerant flows into the manifold 1 through the connecting port 311. After the refrigerant enters the manifold 1 through the connecting port 311, it flows into the corresponding chamber through the liquid distribution hole. The manifold 1 is provided with two partition plates 102, which divide the inner cavity into a first chamber 121, a second chamber 122 and a third chamber 123. Each chamber has a liquid distribution hole, and the refrigerant flows into the corresponding chamber through these liquid distribution holes.

[0073] In this embodiment, the flared structure gradually widens the flow path of the refrigerant as it enters the turbulence shell 301, reducing the impact force on the refrigerant. This design effectively reduces the non-uniformity of the refrigerant before entering the distribution hole, ensuring that the refrigerant enters the distribution hole in a more uniform state. The flared structure acts as a buffer, reducing the impact force of the refrigerant when entering the distribution hole and further optimizing the refrigerant distribution. This buffering effect helps reduce pressure fluctuations of the refrigerant during flow and improves the stability of the system. In the chamber of the turbulence shell 301, the refrigerant continues to be affected by the spiral blades 322, further homogenizing the gas-liquid distribution. The flared structure reduces the resistance of the refrigerant during flow, allowing the refrigerant to achieve higher uniformity before entering the distribution hole. The flared structure reduces the non-uniformity of the refrigerant before entering the distribution hole, ensuring that the refrigerant has already achieved a high degree of uniformity when entering the distribution hole. This design helps improve heat exchange efficiency because a uniform refrigerant distribution ensures consistent evaporative heat exchange efficiency in all parts of the heat exchanger.

[0074] See also Figures 8 to 12 As shown, the turbulence shell 301 has a fan-shaped structure, and a fan-shaped flow region is formed in the inner cavity of the turbulence shell 301. The swirling element 302 is installed on the end face of the turbulence shell 301. Specifically, the axis of the swirling shell 321 is perpendicular to the end face of the turbulence shell 301, so that the refrigerant is injected into the turbulence shell 301 under the action of the spiral blades 322, and then decelerated in the turbulence shell 301. In other embodiments, the turbulence shell 301 can also be triangular, trumpet-shaped, or trapezoidal.

[0075] In this embodiment, the fan-shaped turbulence shell 301 cooperates with the vertically installed swirl member 302, causing the refrigerant to be injected into the turbulence shell 301 in a specific direction under the action of the helical blades 322. This precise guidance ensures that the refrigerant has a clear flow direction when entering the turbulence shell 301, reducing disordered flow and eddy current generation, and improving flow efficiency. The fan-shaped flow area matches the structure and layout of the heat exchanger, making the refrigerant flow path more closely fit the heat exchanger settings, ensuring that the refrigerant can more evenly cover the heat exchange area, and improving heat exchange efficiency. The refrigerant decelerates in the turbulence shell 301, and the flow velocity decreases, which helps the refrigerant gas and liquid phases to mix further. During the deceleration process, the refrigerant fully collides and mixes in the fan-shaped flow area, making the gas-liquid distribution more uniform, weakening the stratification phenomenon caused by gravity, and improving heat exchange efficiency. The fan-shaped turbulence shell 301 makes the flow of the refrigerant more stable before entering the distribution hole, reducing the non-uniformity caused by velocity differences, ensuring that the refrigerant enters the distribution hole in a more uniform state, and further optimizing the distribution. The fan-shaped flow area allows the refrigerant to cover all areas of the heat exchanger more evenly, avoiding excessive or insufficient refrigerant in some areas. This ensures consistent heat exchange efficiency in all parts of the heat exchanger, improving overall heat exchange efficiency. Uniform refrigerant distribution also prevents local overheating or undercooling of the heat exchanger, reduces thermal stress and uneven condensation, and extends the service life of the heat exchanger.

[0076] In one specific implementation, the first liquid distribution hole 111, the second liquid distribution hole 112 and the third liquid distribution hole 113 are square holes, and the connecting port 311 on the turbulence shell 301 is also square. The turbulence shell 301 is welded to the manifold 1, and the size of the connecting port 311 is set in accordance with the size of the liquid distribution hole.

[0077] A heat exchanger includes a flow distribution assembly, a gas collecting pipe 6, and a plurality of flat tubes 5. The flow distribution assembly is the flow distribution assembly described above. One end of the plurality of flat tubes 5 is connected to the gas collecting pipe 1, and the other end of the plurality of flat tubes 5 is connected to the gas collecting pipe 6. The number of flat tubes 5 corresponding to the middle part of the gas collecting pipe 1 is greater than the number of flat tubes 5 corresponding to the end part of the gas collecting pipe 1.

[0078] In this embodiment, the number of flat tubes 5 in the middle of the manifold 1 is greater than that at the ends, matching the characteristics of large air volume and high heat exchange demand in the middle. More flat tubes 5 ensure sufficient refrigerant for heat exchange in the middle region, improving heat exchange efficiency. The distribution holes are set with opening cross-sectional areas according to the air volume distribution; the second distribution hole 112 in the middle has a large opening to provide more refrigerant for the middle flat tubes 5; the distribution holes on both sides have small openings to adapt to situations where there are fewer flat tubes 5 at the ends and lower heat exchange demand. Precise distribution ensures full utilization of refrigerant and avoids waste. The synergy between the number of flat tubes 5 and the refrigerant distribution ensures uniform heat exchange in all areas of the heat exchanger, reducing local overheating or undercooling, lowering the risk of thermal stress and uneven condensation, and extending the life of the heat exchanger. Whether it's a microchannel heat exchanger or a finned tube heat exchanger, the heat exchanger (i.e., condenser) of a household split air conditioner outdoor unit, and the use of an axial fan for air delivery, the airflow distribution on the heat exchanger follows this trend. That is, where there are more flat tubes, the corresponding air velocity of the heat exchanger is greater, the airflow is greater, and the refrigerant flow requirement is also greater.

[0079] An air conditioner includes a heat exchanger, wherein the heat exchanger is as described above.

[0080] It will be readily understood by those skilled in the art that the aforementioned advantageous methods can be freely combined and superimposed without conflict.

[0081] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above are merely preferred embodiments of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A shunt component, characterized in that, include: The manifold (1), the splitter (2), and the turbulence-disrupting assembly (3) are included. The distributor (2) is provided with a refrigerant inlet (21) and a refrigerant outlet, and the manifold (1) has a refrigerant distribution hole (101); One end of the turbulence component (3) is connected to the refrigerant outlet, and the other end of the turbulence component (3) is connected to the refrigerant distribution hole (101). The refrigerant flows into the distributor (2) through the refrigerant inlet (21). The refrigerant undergoes a first turbulence in the distributor (2), and then undergoes a second turbulence by spiraling flow in the turbulence component (3).

2. The shunt component according to claim 1, characterized in that, The refrigerant distribution hole (101) includes at least a first distribution hole (111) and a second distribution hole (112). In the axial direction of the manifold (1), the first distribution hole (111) and the second distribution hole (112) are spaced apart on the manifold (1). The opening cross-sectional area of ​​the first distribution hole (111) and the second distribution hole (112) is proportional to the air volume distribution in the corresponding area of ​​the heat exchanger, and each distribution hole is connected to one of the turbulence components (3).

3. The shunt component according to claim 2, characterized in that, The refrigerant distribution hole (101) also includes a third distribution hole (113). In the axial direction of the manifold (1), the second distribution hole (112) is opened in the middle of the manifold (1). The first distribution hole (111) and the third distribution hole (113) are respectively opened on both sides of the second distribution hole (112). The second distribution hole (112) has the largest opening cross-sectional area.

4. The shunt component according to claim 1, characterized in that, The turbulence assembly (3) includes a turbulence shell (301) and a swirling element (302). One end of the swirling element (302) is connected to the refrigerant outlet, and the other end of the swirling element (302) is connected to the turbulence shell (301). The turbulence shell (301) is connected to the manifold (1), and the turbulence shell (301) has a communication port (311) that is connected to the refrigerant distribution hole (101).

5. The shunt component according to claim 4, characterized in that, The swirling element (302) includes a swirling shell (321) and a helical blade (322). The helical blade (322) is installed in the swirling shell (321), and a helical flow channel is formed between the outer edge of the helical blade (322) and the inner wall of the swirling shell (321). The first end of the swirling shell (321) is connected to the refrigerant outlet, and the second end of the swirling shell (321) is connected to the turbulence shell (301). A portion of the helical blade (322) extends into the cavity of the turbulence shell (301).

6. The shunt component according to claim 5, characterized in that, The swirling element (302) further includes an end cap (323), which is detachably connected to the first end of the swirling shell (321). The end cap (323) is provided with an end cap hole (324), which is connected to the refrigerant outlet. The end cap hole (324) can adjust the refrigerant flow rate into the swirling shell (321).

7. The shunt component according to claim 4, characterized in that, Along the refrigerant outflow direction, the turbulence shell (301) has a flared structure, and the larger end of the turbulence shell (301) has the connecting port (311).

8. The shunt assembly according to claim 7, characterized in that, The turbulence shell (301) has a fan-shaped structure, and a fan-shaped flow area is formed in the inner cavity of the turbulence shell (301). The swirling element (302) is installed on the end face of the turbulence shell (301).

9. The shunt component according to claim 3, characterized in that, The distributor (2) includes a distributor body (201), a refrigerant inlet pipe (202), and a refrigerant outlet pipe (203). One end of the refrigerant inlet pipe (202) has the refrigerant inlet (21), and the other end of the refrigerant inlet pipe (202) is connected to the distributor body (201). The refrigerant outlet pipe (203) includes a first branch pipe (231), a second branch pipe (232), and a third branch pipe (233). The first branch pipe (231), the second branch pipe (232), and the third branch pipe (233) are connected to the distributor body (201). 32) and one end of the third branch pipe (233) are connected to the main body (201) of the distributor. The other end of the first branch pipe (231) is connected to the turbulence component (3) corresponding to the first liquid distribution hole (111). The other end of the second branch pipe (232) is connected to the turbulence component (3) corresponding to the second liquid distribution hole (112). The other end of the third branch pipe (233) is connected to the turbulence component (3) corresponding to the third liquid distribution hole (113).

10. The shunt assembly according to claim 9, characterized in that, With the longitudinal section of the manifold (1) as the projection plane, the first liquid distribution hole (111) is located above the second liquid distribution hole (112), the third liquid distribution hole (113) is located below the second liquid distribution hole (112), the diameter of the first branch pipe (231) is d1, the diameter of the second branch pipe (232) is d2, and the diameter of the third branch pipe (233) is d3. The diameters d1, d2, and d3 satisfy the following condition: d2 > d1 > d3.

11. The shunt assembly according to claim 10, characterized in that, The manifold (1) is provided with two partitions (102), which divide the inner cavity of the manifold (1) into a first chamber (121), a second chamber (122) and a third chamber (123). The first chamber (121) has a first liquid distribution hole (111), the second chamber (122) has a second liquid distribution hole (112), and the third chamber (123) has a third liquid distribution hole (113). It also includes a liquid collection pipe (4), which includes a main liquid outlet pipe (401), a first liquid outlet pipe (402), a second liquid outlet pipe (403), and a third liquid outlet pipe (404). One end of the first liquid outlet pipe (402), the second liquid outlet pipe (403), and the third liquid outlet pipe (404) are all connected to the main liquid outlet pipe (401). The other end of the first liquid outlet pipe (402) is connected to the first chamber (121), the other end of the second liquid outlet pipe (403) is connected to the second chamber (122), and the other end of the third liquid outlet pipe (404) is connected to the third chamber (123). The main liquid outlet pipe (401) and the refrigerant inlet pipe (202) are connected by a connecting pipe (405), and a one-way valve (406) is provided on the connecting pipe (405).

12. A heat exchanger comprising a flow distribution assembly, a gas collecting pipe (6), and a plurality of flat tubes (5), characterized in that, The diversion assembly is any one of claims 1 to 11, wherein one end of the plurality of flat tubes (5) is connected to the collecting pipe (1), the other end of the plurality of flat tubes (5) is connected to the gas collecting pipe (6), and the number of flat tubes (5) corresponding to the middle part of the collecting pipe (1) is greater than the number of flat tubes (5) corresponding to the end of the collecting pipe (1).

13. An air conditioner, comprising a heat exchanger, characterized in that, The heat exchanger is the heat exchanger described in claim 12.

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