Flow divider and air conditioner

Abstract

This application relates to the field of air conditioning technology and discloses a distributor and an air conditioner. The distributor includes: a cylindrical body with an inlet hole at the inlet end and multiple distribution holes at the outlet end; a first flow channel, a second flow channel, a transition cavity, a first jet cavity, a second jet cavity, and a flow equalization cavity formed inside the cylindrical body; the first starting end of the first flow channel is connected to the inlet hole, and the first ending end is connected to the transition cavity; the second starting end of the second flow channel is connected to the inlet hole, and the second ending end is connected to the transition cavity; the transition cavity is connected to the first jet cavity and the second jet cavity; the first jet cavity is connected to the first jet cavity through a first jet hole; the flow equalization cavity is connected to the multiple distribution holes and to the second jet cavity through a second jet hole; the cross-sectional area of ​​the second ending end is larger than the cross-sectional area of ​​the second starting end. The distributor provided by this application can fully mix gaseous refrigerant and liquid refrigerant, enabling the distributor to achieve uniform flow distribution.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and in particular to a splitter and an air conditioner. Background Technology

[0002] The heat exchangers used in most mainstream air conditioners on the market typically consist of a combination of copper tubes and aluminum fins. Cooling or heating is achieved through heat exchange between the refrigerant flowing inside the copper tubes and the air outside the copper tubes and aluminum fins. To improve the heat exchanger's efficiency, current technology often designs the heat exchanger with a multi-channel flow structure. Before the refrigerant enters the heat exchanger, a distributor is used to split the refrigerant into multiple streams that enter the heat exchanger in parallel, effectively increasing the contact area between the refrigerant and the heat exchanger.

[0003] However, in actual applications, most of the refrigerant entering the distributor is in a gas-liquid two-phase mixed state. Before entering the distributor, the refrigerant is affected by gravity, centrifugal force and other factors, and its flow pattern is mostly stratified flow or asymmetric annular flow. This results in the gaseous refrigerant and liquid refrigerant not being fully mixed, which ultimately makes it difficult for the distributor to achieve uniform distribution of the refrigerant. Summary of the Invention

[0004] This application discloses a distributor and an air conditioner that can fully mix gaseous refrigerant and liquid refrigerant, enabling the distributor to achieve uniform distribution.

[0005] To achieve the above objectives, this application discloses a shunt, comprising: A cylindrical body having an inlet end and an outlet end, the inlet end having an inlet hole, and the outlet end having multiple diversion holes; The first flow channel is formed inside the cylinder, and the two ends of the first flow channel are a first starting end and a first ending end, respectively. The first starting end is connected to the inlet hole. The second flow channel is formed inside the cylinder and along the radial direction of the cylinder. The first flow channel is distributed around the outer periphery of the second flow channel. The two ends of the second flow channel are a second starting end and a second ending end, respectively. The second starting end is connected to the inlet hole, and the cross-sectional area of ​​the second ending end is larger than the cross-sectional area of ​​the second starting end. A transition cavity is formed inside the cylinder and connects the first termination end and the second termination end. A first jet cavity is formed inside the cylinder and is connected to the transition cavity; A second jet cavity is formed inside the cylinder. Along the radial direction of the cylinder, the first jet cavity surrounds the outer periphery of the second jet cavity. The second jet cavity communicates with the transition cavity and is connected to the first jet cavity through a first jet hole. The cross-sectional area of ​​the first jet hole is smaller than the cross-sectional area of ​​the first termination end, and the orientation direction of the first jet hole forms an angle with the orientation direction of the first termination end. A flow equalization cavity is formed inside the cylinder and is connected to a plurality of flow distribution holes. The flow equalization cavity is also connected to a second jet cavity through a second jet hole.

[0006] In some embodiments of this application, the inner wall of the second flow channel is inclined relative to the axial direction of the cylinder and extends from the second starting end to the second ending end away from the axis of the cylinder; And / or, the first flow channel is formed with a narrow portion located between the first starting end and the first ending end, the cross-sectional area of ​​the narrow portion being smaller than the cross-sectional area of ​​the rest of the first flow channel excluding the narrow portion.

[0007] In some embodiments of this application, the first flow channel includes a first segment and a second segment that are connected. The end of the first segment away from the second segment is formed as the first starting end, and the end of the second segment away from the first segment is formed as the first ending end. The cross-sectional area of ​​the first starting end is greater than the cross-sectional area of ​​the connection between the first segment and the second segment.

[0008] In some embodiments of this application, the first flow channel includes a first segment and a second segment that are connected. The end of the first segment away from the second segment is formed as the first starting end, and the end of the second segment away from the first segment is formed as the first ending end. The cross-sectional area of ​​the first ending end is greater than the cross-sectional area of ​​the connection between the first segment and the second segment.

[0009] In some embodiments of this application, the inner wall of the second segment is configured as an arcuate surface, and the side of the second segment opposite to the axis of the cylinder is the outer side of the arcuate surface.

[0010] In some embodiments of this application, the cylindrical body includes a shell portion and a first inner portion, the shell portion having the inlet end and the outlet end, and the first inner portion being disposed inside the shell portion; The first embedded portion extends from the inlet end along the axial direction of the cylinder to the outlet end. The peripheral side surface of the first embedded portion is spaced apart from the inner side wall of the shell portion to form the first flow channel. The first embedded portion is provided with a second flow channel.

[0011] In some embodiments of this application, the radius of the second starting end is R1, and the radius of the cavity of the housing portion corresponding to the first embedded portion is R2, where R1 / R2≥0.2 and R1 / R2≤0.4; And / or, the radius of the cavity corresponding to the first embedded part of the housing portion is R2, the radius of the second termination end is R3, R3 / R2≥0.3, and R3 / R2≤0.5.

[0012] In some embodiments of this application, a wide portion is formed between the two ends of the first embedded portion, and the cross-sectional area of ​​the wide portion is greater than the cross-sectional area of ​​the rest of the first embedded portion excluding the wide portion.

[0013] In some embodiments of this application, the radius of the cavity corresponding to the first embedded portion of the housing portion is R2, the radius of the wide portion is R4, R4 / R2≥0.6, and R4 / R2≤0.8.

[0014] On the other hand, this application discloses an air conditioner that includes a splitter as described above.

[0015] Compared with the prior art, this application has at least the following beneficial effects: In this embodiment, an inlet hole is provided at the inlet end of the cylinder, forming a first flow channel and a second flow channel inside the cylinder. The first starting end of the first flow channel is connected to the inlet hole, and the second starting end of the second flow channel is also connected to the inlet hole. This allows the two-phase refrigerant received from the inlet hole to flow into the first and second flow channels respectively, achieving the separation of gaseous and liquid refrigerant. The liquid refrigerant flows along the first flow channel through the transition cavity into the first jet cavity, while the gaseous refrigerant flows along the second flow channel through the transition cavity into the second jet cavity. Simultaneously, the first jet cavity and the second jet cavity are connected through the first jet hole, allowing... The cross-sectional area of ​​the first jet orifice is smaller than that of the first termination end, which can accelerate the liquid refrigerant out of the first jet orifice. By utilizing the angle formed between the orientation direction of the first jet orifice and the orientation direction of the first termination end, the flow direction of the liquid refrigerant is changed, so that the liquid refrigerant forms a rotating jet after being accelerated out of the jet orifice. This rotating jet can impact the gaseous refrigerant when it is ejected into the second jet cavity, so that the gaseous refrigerant and liquid refrigerant are uniformly mixed in the second jet cavity and flow through the second jet orifice into the flow equalization cavity. It then flows out through multiple flow splitting orifices, realizing the uniform flow splitting of the two-phase refrigerant by the flow splitter.

[0016] Furthermore, by designing the cross-sectional area of ​​the second termination end to be larger than that of the second starting end, the second flow channel can accelerate the gaseous refrigerant and eject it into the transition cavity. At this time, if the gaseous refrigerant in the second flow channel is mixed with liquid refrigerant, the accelerated gaseous refrigerant can squeeze out this part of the liquid refrigerant, causing this part of the liquid refrigerant to flow around in the transition cavity and mix with the liquid refrigerant ejected from the first flow channel into the transition cavity and flow into the first jet cavity. This achieves further separation of the gaseous and liquid refrigerants, thereby improving the mixing effect of the gaseous and liquid refrigerants in the second jet cavity. The uniform separation effect of the splitter on the two-phase refrigerant is further improved. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the structure of a shunt provided in an embodiment of this application; Figure 2 This is a cross-sectional structural schematic diagram of a shunt provided in an embodiment of this application; Figure 3 This is a partial cross-sectional structural diagram of a shunt provided in an embodiment of this application; Figure 4 This is a schematic diagram of the structure of an embedded portion of a first jet hole with continuous slits provided in an embodiment of this application; Figure 5 This is a schematic diagram of the structure of an embedded part having uniformly arranged first jet holes provided in an embodiment of this application; Figure 6 This is a schematic diagram of the structure of an embedded part with a spirally arranged first jet hole provided in an embodiment of this application; Figure 7 This is a schematic diagram of a cylindrical second embedded portion provided in an embodiment of this application; Figure 8 This is a schematic diagram of a frustum-shaped second embedded portion provided in an embodiment of this application; Figure 9 This is a schematic diagram of another frustum-shaped second embedded portion provided in an embodiment of this application; Figure 10 This is a structural schematic diagram of an air conditioner provided in an embodiment of this application.

[0019] Explanation of main figure symbols 100. Diverter; 10. Cylinder body; 10a. Inlet end; 10b. Outlet end; 10c. Inlet hole; 10d. Diverter hole; 101. Shell part; 102. First inner part; 102a. Wide part; 103. Second inner part; 11. First flow channel; 11a. First starting end; 11b. First ending end; 11c. Narrow section; 111. First segment; 112. Second segment; 12. Second flow channel; 12a. Second starting end; 12b. Second ending end; 13. Transition cavity; 14. First jet cavity; 14a. First jet orifice; 15. Second jet cavity; 15a. Second jet orifice; 16. Flow equalization cavity; 200. Air conditioner; x, radial direction; y, axial direction. Detailed Implementation

[0020] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0021] In this application, the terms "upper," "lower," "left," "right," "front," "rear," "top," "bottom," "inner," "outer," "middle," "vertical," "horizontal," "lateral," and "longitudinal" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated device, element, or component to having a specific orientation, or to be constructed and operated in a specific orientation.

[0022] Furthermore, in addition to indicating location or positional relationship, some of the aforementioned terms may also have other meanings. For example, the term "above" may also be used in some cases to indicate a certain dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0023] Furthermore, the terms "installation," "setup," "equipped with," "connection," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral structure; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium, or an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0024] Furthermore, the terms "first," "second," etc., are primarily used to distinguish different devices, components, or parts (which may be the same or different in specific type and construction), and are not intended to indicate or imply the relative importance or quantity of the indicated devices, components, or parts. Unless otherwise stated, "a plurality of" means two or more.

[0025] Before explaining the technical solution of this application, the inventive concept of this application will be explained first.

[0026] In existing air conditioning heat exchange systems, distributors are multi-branch flow channels used to distribute gas-liquid two-phase refrigerant to the heat exchanger. However, the refrigerant is often in a gas-liquid two-phase mixed state before entering the distributor. Influenced by gravity and flow inertia, its flow pattern is often stratified or asymmetric annular, resulting in insufficient mixing of the gas and liquid phases, making it difficult for the distributor to achieve uniform flow distribution. This problem directly affects the heat exchanger's heat exchange efficiency and the system's operational stability, causing an imbalance in the refrigerant phase distribution across the branches.

[0027] For example, in air conditioning cooling mode, when the refrigerant flows through horizontally arranged pipes into the distributor, the gas phase concentrates in the upper region of the pipes due to density differences, while the liquid phase deposits in the lower region, forming a stratified flow phenomenon. In this technical scenario, the gas-liquid distribution at the inlet of the distributor exhibits significant asymmetry, resulting in some branches being dominated by gaseous refrigerant while others are dominated by liquid refrigerant, leading to uneven heat load distribution across different areas of the heat exchanger.

[0028] To address the aforementioned issues, this application discloses a refrigerant distributor and an air conditioner, designed to improve the uniformity of refrigerant distribution.

[0029] The following will describe the scheme of this application in detail with reference to the accompanying drawings.

[0030] like Figure 1 and 2 As shown, this application discloses a shunt 100, comprising: The cylinder 10 has an inlet end 10a and an outlet end 10b. The inlet end 10a is provided with an inlet hole 10c, and the outlet end 10b is provided with a plurality of diversion holes 10d.

[0031] The first flow channel 11 is formed inside the cylinder 10. The two ends of the first flow channel 11 are a first starting end 11a and a first ending end 11b, respectively. The first starting end 11a is connected to the inlet hole 10c.

[0032] The second flow channel 12 is formed inside the cylinder 10. Along the radial direction x of the cylinder 10, the first flow channel 11 is distributed around the outer periphery of the second flow channel 12. The two ends of the second flow channel 12 are a second starting end 12a and a second ending end 12b, respectively. The second starting end 12a is connected to the inlet hole 10c. The cross-sectional area of ​​the second ending end 12b is larger than that of the second starting end 12a. The transition cavity 13 is formed inside the cylinder 10 and is connected to the first ending end 11b and the second ending end 12b.

[0033] The first jet cavity 14 is formed inside the cylinder 10 and is connected to the transition cavity 13.

[0034] The second jet cavity 15 is formed inside the cylinder 10. Along the radial direction x of the cylinder 10, the first jet cavity 14 is distributed around the outer periphery of the second jet cavity 15. The second jet cavity 15 is connected to the transition cavity 13 and is connected to the first jet cavity 14 through the first jet hole 14a. The cross-sectional area of ​​the first jet hole 14a is smaller than the cross-sectional area of ​​the first termination end 11b, and the orientation direction of the first jet hole 14a forms an angle with the orientation direction of the first termination end 11b.

[0035] The flow equalization cavity 16 is formed inside the cylinder 10. The flow equalization cavity 16 is connected to a plurality of the flow distribution holes 10d, and the flow equalization cavity 16 is connected to the second jet cavity 15 through the second jet hole 15a.

[0036] For ease of understanding, the following explains some key terms in this embodiment: A distributor 100 is a device used to distribute fluid (such as refrigerant) from one inlet channel to multiple outlet channels. Its main function is to achieve uniform distribution of fluid to optimize the operating efficiency of subsequent systems.

[0037] The cylinder 10 constitutes the main structure of the distributor 100, and its interior contains various chambers and channels for fluid flow.

[0038] Inlet end 10a is the inlet area where fluid enters the cylinder 10, while outlet end 10b is the outlet area where fluid leaves the cylinder 10. Inlet orifice 10c is a specific inlet provided on inlet end 10a, used to guide fluid into the distributor 100. Distributor orifice 10d are multiple outlets provided on outlet end 10b, used to distribute fluid to different branches.

[0039] The first flow channel 11 and the second flow channel 12 are channels inside the cylinder 10 used to guide fluid flow. The first flow channel 11 has a first starting end 11a and a first ending end 11b, wherein the first starting end 11a communicates with the inlet hole 10c. The second flow channel 12 has a second starting end 12a and a second ending end 12b, wherein the second starting end 12a also communicates with the inlet hole 10c. The radial direction x refers to the direction perpendicular to the central axis of the cylinder 10.

[0040] The transition cavity 13 is an intermediate chamber inside the cylinder 10, which serves to collect fluids from the first termination end 11b of the first flow channel 11 and the second termination end 12b of the second flow channel 12.

[0041] The first jet chamber 14 and the second jet chamber 15 are chambers inside the cylinder 10 for further fluid processing. The first jet chamber 14 is connected to the transition chamber 13. The second jet chamber 15 is also connected to the transition chamber 13 and is connected to the first jet chamber 14 through a first jet hole 14a. The first jet hole 14a is a channel connecting the first jet chamber 14 and the second jet chamber 15.

[0042] The flow equalization chamber 16 is the final chamber inside the cylinder 10. Its function is to receive the fluid from the second jet chamber 15 and communicate with the second jet chamber 15 through the second jet hole 15a, so as to evenly distribute the fluid to each flow distribution hole 10d.

[0043] Understandably, the cylinder 10 is the outer shell of the distributor 100, and its interior forms various channels and chambers for fluid flow. The cylinder 10 can be made of various materials and manufactured using various processes, such as injection molding or metal processing. The cylinder 10 has an inlet end 10a and an outlet end 10b. The inlet end 10a is provided with an inlet hole 10c for receiving the fluid to be distributed. The outlet end 10b is provided with multiple distribution holes 10d for discharging the distributed fluid. For example, the inlet hole 10c can be a circular opening, while the distribution holes 10d can be multiple small holes evenly distributed on the outlet end 10b.

[0044] Understandably, the first flow channel 11 can be a simple straight pipe channel with a constant cross-sectional area over its entire length.

[0045] Understandably, a second flow channel 12 is also formed inside the cylinder 10. The second flow channel 12 can be a conical channel with a cross-sectional area that gradually increases along the fluid direction, or its inner wall can be designed in a stepped shape, so that the area at the outlet is larger than that at the inlet. The transition cavity 13 can be a simple circular or square chamber with a volume sufficient to contain and mix the fluids from the two flow channels. The first jet cavity 14 can be an annular chamber with a smooth inner wall to reduce fluid resistance.

[0046] It is understandable that the first jet orifice 14a can be one or more small orifices, the direction of which can be perpendicular to the mainstream direction of the fluid or set at a certain angle to generate a jet effect.

[0047] The flow equalization chamber 16 can be a large circular chamber with its inner wall designed to be smooth or have a flow guiding structure to promote uniform distribution of fluid.

[0048] In this application, the distributor, through the aforementioned structural design, guides the two-phase refrigerant (gas and liquid phases) into the distributor 100 via the inlet 10c to two parallel flow channels: a first flow channel 11 and a second flow channel 12. Since the first flow channel 11 surrounds the outer periphery of the second flow channel 12, and both are connected to the inlet 10c, the initially entering refrigerant is preliminarily segmented. For example, the portion with a higher liquid content may tend to flow along the wall of the cylinder 10, thus entering more of the first flow channel 11, while the portion with a higher gas content may tend to flow along the center, thus entering more of the second flow channel 12.

[0049] In the second flow channel 12, because the cross-sectional area of ​​its second terminal end 12b is larger than that of its second starting end 12a, the fluid undergoes an expansion process as it flows through it. This expansion effect helps to reduce the flow velocity and may promote the initial mixing of the gas and liquid phases, reducing stratification.

[0050] Subsequently, the fluids from the first termination end 11b of the first flow channel 11 and the second termination end 12b of the second flow channel 12 converge into the transition cavity 13. In the transition cavity 13, the fluids from the two flow channels undergo their first convergence and mixing.

[0051] Next, the mixed fluid enters the first jet cavity 14 and the second jet cavity 15 from the transition cavity 13. The first jet cavity 14 surrounds the outer periphery of the second jet cavity 15, and the second jet cavity 15 is connected to the first jet cavity 14 through the first jet hole 14a. Crucially, the cross-sectional area of ​​the first jet hole 14a is smaller than the cross-sectional area of ​​the first termination end 11b, and the orientation of the first jet hole 14a forms an angle with the orientation of the first termination end 11b. This design causes the fluid to form a high-speed jet as it passes through the first jet hole 14a, and is ejected into the first jet cavity 14 at a certain angle. This high-speed, oblique jet can disturb and shear the fluid within the first jet cavity 14, thereby enhancing the mixing effect of the gas and liquid phases, breaking the original stratified or asymmetric flow pattern, and promoting a more uniform dispersion of the gas and liquid phases.

[0052] Finally, the thoroughly mixed fluid enters the flow equalization chamber 16 from the second jet chamber 15 through the second jet orifice 15a. The flow equalization chamber 16 acts as a buffer and redistribution area, further ensuring that the fluid is more uniform before entering the multiple flow dividers 10d. This guarantees that the refrigerant flowing out of each flow divider 10d has a similar gas-liquid ratio and flow rate, achieving uniform refrigerant distribution and effectively solving the problem of uneven flow distribution caused by uneven mixing of the refrigerant gas and liquid phases.

[0053] Considering that if the inner wall of the second flow channel 12 is designed as a straight cylinder or a constant cross section, when the fluid flows inside the second flow channel 12, the velocity distribution at the second terminal end 12b may be uneven due to the boundary layer effect or fluid inertia. This may affect the flow splitting efficiency and uniformity, or even generate local eddies or dead zones, thereby reducing the overall performance of the flow splitter.

[0054] In some embodiments, the inner wall of the second flow channel 12 is inclined relative to the axial direction y of the cylinder 10, and extends from the second starting end 12a to the second ending end 12b away from the axis of the cylinder 10.

[0055] It is understandable that the inner wall of the second flow channel 12 is inclined relative to the axial direction y of the cylinder 10, meaning that the inner wall surface of the second flow channel 12 is not parallel to the axis of the cylinder 10, but rather has an inclination angle. This inclination design can effectively guide the fluid flow direction and adjust the velocity and pressure distribution of the fluid within the flow channel. For example, the inner wall can be designed as a conical surface, that is, gradually expanding or contracting from the second starting end 12a to the second ending end 12b; or, the inner wall can be designed as an arc-shaped surface with a certain curvature to guide the fluid more smoothly. In addition, the inner wall can also be designed as a stepped inclination, that is, segmented inclination. Extending from the second starting end 12a to the second ending end 12b and away from the axis of the cylinder 10, the direction of inclination is clearly defined, that is, the inner wall of the second flow channel 12 gradually expands outward from the second starting end 12a to the second ending end 12b, away from the central axis of the cylinder 10. This expansion design helps to slow down the fluid velocity, reduce local pressure, and guide the fluid to diffuse radially outward, preparing for subsequent mixing or splitting. For example, the inner wall can be inclined outward to form a diffusion section, such that the cross-sectional area of ​​the second termination end 12b is greater than the cross-sectional area of ​​the second starting end 12a; or, the inclination angle can be optimized according to the fluid properties and the required diversion effect, for example, a constant inclination angle or a variable inclination angle can be used.

[0056] By designing the inner wall of the second flow channel 12 to be inclined relative to the axial direction y of the cylinder 10, and extending it from the second starting end 12a to the second ending end 12b away from the axis of the cylinder 10, the second flow channel 12 forms a gradually expanding channel. When fluid enters from the inlet hole 10c and flows through the second flow channel 12, the fluid velocity gradually decreases due to the expansion of the channel, while the pressure is restored. More importantly, this expansion design can effectively guide the fluid to diffuse radially outward, making the velocity and pressure distribution on the cross-section of the fluid more uniform when it reaches the second ending end 12b. This helps to reduce the local eddies or dead zones that may be generated at the second ending end 12b, thereby ensuring that the fluid can enter the subsequent transition cavity 13 more smoothly and uniformly, and be fully mixed with the fluid from the first flow channel 11.

[0057] Considering that if the internal structure of the flow channel fails to effectively guide and stabilize the fluid, it may cause unnecessary turbulence or uneven flow velocity before the fluid enters the transition cavity 13, thereby affecting the subsequent jet and flow equalization effect and reducing the overall flow splitting performance and uniformity of the splitter 100.

[0058] In some embodiments, the first flow channel 11 is formed with a narrow portion 11c located between the first starting end 11a and the first ending end 11b, and the cross-sectional area of ​​the narrow portion 11c is smaller than the cross-sectional area of ​​the rest of the first flow channel 11 excluding the narrow portion 11c.

[0059] The narrow section 11c refers to a locally contracting region within the first flow channel 11. This region is designed to actively regulate the flow pattern of the fluid passing through the first flow channel 11. The narrow section 11c can be constructed in various geometries; for example, it can be an annular contraction section with its inner wall bulging towards the center of the flow channel; or it can be one or more local protrusions to reduce the fluid flow area. Simultaneously, the cross-sectional area of ​​the narrow section 11c is smaller than the cross-sectional area of ​​the rest of the first flow channel 11 excluding the narrow section 11c. This design causes the fluid velocity to increase and the pressure to decrease as it passes through the narrow section 11c. This change in cross-sectional area allows for the conversion of fluid kinetic and pressure energy, thereby accelerating or decelerating the fluid and helping to suppress unstable fluid flow within the flow channel. For example, this can be achieved by providing an annular flange on the inner wall of the first flow channel 11, with the inner diameter of the flange being smaller than the inner diameter of other parts of the first flow channel 11; or it can be achieved by forming one or more inwardly protruding structures on the wall of the first flow channel 11 to reduce the local flow area.

[0060] By providing a narrow section 11c in the first flow channel 11, the fluid must pass through a region with a reduced cross-sectional area as it flows from the first starting end 11a to the first ending end 11b. When the fluid flows through the narrow section 11c, its velocity increases significantly according to Bernoulli's principle, while the local pressure decreases. This increase in velocity helps convert the fluid's kinetic energy into pressure energy and accelerates the fluid, thus pre-treating its flow pattern before it enters the transition cavity 13. The design of the narrow section 11c effectively rectifyes and accelerates the fluid, suppressing eddies or irregular flows that may occur within the first flow channel 11, allowing the fluid to enter the transition cavity 13 in a more stable and concentrated jet form. This optimization of the fluid flow pattern ensures that the fluid entering the transition cavity 13 from the first flow channel 11 has more consistent momentum and directionality, laying a good foundation for the subsequent mixing and flow equalization processes in the transition cavity 13, the first jet cavity 14, the second jet cavity 15 and the flow equalization cavity 16, thereby improving the overall flow distribution uniformity of the distributor 100.

[0061] In practical applications, if the inlet structure of the first flow channel 11 is not properly designed, the fluid may encounter large local resistance when entering the first flow channel 11, resulting in uneven flow velocity, pressure fluctuation, or even eddies, thereby affecting the stable transmission of the fluid in the first flow channel 11 and the subsequent diversion effect.

[0062] In some embodiments, the first flow channel 11 includes a first segment 111 and a second segment 112 that are connected. The end of the first segment 111 away from the second segment 112 is formed as the first starting end 11a, and the end of the second segment 112 away from the first segment 111 is formed as the first ending end 11b. The cross-sectional area of ​​the first starting end 11a is greater than the cross-sectional area of ​​the connection between the first segment 111 and the second segment 112.

[0063] Specifically, the first flow channel 11 is constructed to consist of at least two interconnected segments, namely a first segment 111 and a second segment 112. This segmented design allows the first flow channel 11 to have different geometric characteristics in different regions, thereby enabling better control of the fluid flow within it. The first segment 111 is the starting part of the first flow channel 11, and its end away from the second segment 112 is designed as a first starting end 11a, serving as the inlet for the fluid to enter the first flow channel 11. This first starting end 11a typically communicates with the inlet orifice 10c, responsible for receiving the initial fluid. The second segment 112 is the subsequent part of the first flow channel 11, and its end away from the first segment 111 is designed as a first terminating end 11b, serving as the outlet for the fluid to leave the first flow channel 11, and communicating with the transition cavity 13. This structure ensures that the fluid flow path within the first flow channel 11 is continuous and orderly. Furthermore, the cross-sectional area of ​​the first starting end 11a is designed to be larger than the cross-sectional area at the junction of the first segment 111 and the second segment 112. This means that the first segment 111 gradually narrows from the inlet towards its connection with the second segment 112. This narrowing channel can accelerate the incoming fluid, converting the fluid's static pressure energy into dynamic pressure energy, which helps stabilize fluid flow, reduce local pressure loss, and suppress the formation of eddies. For example, the first segment 111 can be designed as a cone or have a stepped narrowing cross-section, while the first starting end 11a can be circular, elliptical, or rectangular, as long as its area is larger than the area of ​​the connection.

[0064] The solution of this application divides the first flow channel 11 into a connected first segment 111 and a second segment 112, and specifically sets the cross-sectional area of ​​the first starting end 11a to be larger than the cross-sectional area of ​​the connection between the first segment 111 and the second segment 112. Thus, when the fluid enters the first flow channel 11, it first passes through a gradually narrowing channel. This narrowing structure can effectively rectify and accelerate the fluid, converting the fluid's static pressure energy into dynamic pressure energy, thereby reducing local pressure loss at the inlet and suppressing the generation of eddies. In this way, the fluid can enter the second segment 112 in a more stable and uniform state, and finally reach the transition cavity 13. This segmented design and optimized cross-sectional area at the inlet make the fluid flow within the first flow channel 11 smoother and more controllable.

[0065] In this manner, the inner wall of the first segment 111 is inclined relative to the axial direction y of the cylinder 10, and extends from the first starting end 11a to the second segment 112 and away from the axis of the cylinder 10.

[0066] The inner wall of the first section 111 is designed to be inclined relative to the axial direction y of the cylinder 10, and this inclination extends from the first starting end 11a to the second section 112 and away from the axis of the cylinder 10, so that the first section 111 forms a gradually expanding channel. When the fluid enters from the first starting end 11a with a relatively small cross-sectional area and flows through the gradually expanding first section 111, the fluid velocity gradually decreases, and the fluid pressure is restored. This design can effectively reduce the energy loss of the fluid inside the flow channel and avoid local high-pressure or low-pressure areas caused by excessive flow velocity or abrupt changes in the flow channel, thereby suppressing the formation of eddies. Through this gentle expansion, the fluid can fill the entire cross-section of the first section 111 more evenly, providing a more stable flow pattern for the fluid subsequently entering the second section 112 and the transition cavity 13, thereby improving the fluid distribution uniformity and efficiency of the entire distributor 100.

[0067] In some embodiments, the first flow channel 11 includes a first segment 111 and a second segment 112 that are connected. The end of the first segment 111 away from the second segment 112 is formed as a first starting end 11a, and the end of the second segment 112 away from the first segment 111 is formed as a first ending end 11b. The cross-sectional area of ​​the first ending end 11b is larger than the cross-sectional area at the connection between the first segment 111 and the second segment 112. Specifically, the first segment 111 can be designed as a channel with a constant cross-sectional area, while the second segment 112 can be designed as a channel with a gradually changing cross-sectional area. The inlet end of the first segment 111 is the first starting end 11a of the first flow channel 11, which is responsible for receiving fluid from the inlet orifice 10c. This end can be designed as a flared shape that smoothly connects to the inlet orifice 10c to reduce inlet resistance, or it can be designed as a circular or rectangular cross-section that directly connects to the inlet orifice 10c. The outlet end of the second section 112 is the first termination end 11b of the first flow channel 11, responsible for guiding the fluid into the transition cavity 13. This end can be designed as a diffuser section that smoothly transitions into the transition cavity 13, or as a beveled surface with a specific angle to guide the fluid into the transition cavity 13. That is, after the fluid enters the second section 112 from the first section 111, it undergoes a process of gradually increasing cross-sectional area before reaching the first termination end 11b. This reduces the fluid velocity at the outlet, minimizes kinetic energy loss, and promotes a smoother diffusion of the fluid into the transition cavity 13.

[0068] As can be seen, this application effectively solves the problems of high local resistance, high pressure loss, and fluid turbulence that may occur when the fluid leaves the first flow channel 11 and enters the transition cavity 13 by making the cross-sectional area of ​​the first termination end of the second section of the first flow channel larger than the cross-sectional area of ​​the connection between the first and second sections. This design allows the fluid to decelerate and diffuse smoothly before entering the transition cavity 13, reducing fluid impact and energy loss, thereby improving the mixing uniformity of the fluid in the transition cavity 13, and providing more stable fluid conditions for the precise flow splitting of the subsequent first jet cavity 14, second jet cavity 15, and flow equalization cavity 16, ultimately improving the flow splitting efficiency and uniformity of the entire flow splitter 100.

[0069] In some embodiments, the inner wall of the second segment 112 is configured as an arcuate surface, and the side of the second segment 112 opposite to the axis of the cylinder 10 is the outer side of the arcuate surface.

[0070] The inner wall of the second segment 112 is constructed as an arcuate surface, meaning that the internal surface of the second segment 112 in the first flow channel 11 exhibits a curved shape, rather than a straight line or a cone. This arcuate design provides a smooth transition surface to guide fluid flow and reduce resistance that the fluid may encounter when the flow channel expands or changes direction. For example, the arcuate surface can be a continuously varying curved surface, thereby avoiding or reducing fluid separation and the generation of eddies.

[0071] The side of the second segment 112 away from the axis of the cylinder 10 is the outer side of the arc-shaped surface, meaning that the convex portion or outward convex side of this arc-shaped surface faces away from the central axis of the cylinder 10. This helps guide the fluid to the outer peripheral region of the first flow channel 11, promoting a uniform radial outward distribution of the fluid during expansion. For example, the arc-shaped surface can be designed with an outward convex shape, so that the fluid is gradually pushed towards the outer boundary of the first flow channel 11 as it passes through the second segment 112.

[0072] When the fluid passes through the first flow channel 11, it enters the second section 112 from the first section 111. Given that the inner wall of the second section 112 is constructed as an arcuate surface, and the outer side of this arcuate surface is opposite to the axis of the cylinder 10, the fluid can gradually expand along a smooth arcuate path within the second section 112. This arcuate design avoids sharp angles or abrupt changes that may be caused by sudden expansion of the flow channel cross-section, thereby reducing the tendency for flow separation in the expansion region. Because the fluid is smoothly guided outward and flows along a continuous curved surface, the formation of eddies is effectively suppressed, allowing the fluid to maintain a more stable flow pattern and a more uniform velocity distribution when passing through the second section 112.

[0073] In some embodiments, the cylindrical body 10 includes a shell portion 101 and a first inner portion 102. The shell portion 101 has an inlet end 10a and an outlet end 10b. The first inner portion 102 is disposed inside the shell portion 101. The first inner portion 102 extends from the inlet end 10a along the axial direction y of the cylindrical body 10 towards the outlet end 10b. The peripheral side surface of the first inner portion 102 is spaced from the inner sidewall of the shell portion 101 to form a first flow channel 11. The first inner portion 102 is provided with a second flow channel 12.

[0074] Specifically, the housing portion 101 is the main outer shell of the distributor 100, and its main function is to provide overall structural support and external interface, and to define the external boundary of the fluid. The housing portion 101 can be constructed into a cylindrical, square, or other geometry suitable for fluid passage. Its manufacturing methods can include various processes such as casting, forging, stamping, welding, or deep drawing. The inlet end 10a and the outlet end 10b are the interfaces for fluid to enter and leave the distributor 100, and are typically designed to reliably connect to an external piping system, such as through threaded connections, flange connections, or clamp connections.

[0075] The first embedded portion 102 is an internal component independent of the housing portion 101, and its main function is to assist in forming a partial flow channel structure inside the distributor 100. The first embedded portion 102 can be designed as a solid or hollow structure, and its specific shape and size will be determined according to the geometry of the required flow channel. The first embedded portion 102 can be manufactured by precision casting, injection molding, 3D printing, or high-precision machining, etc.

[0076] The solution of this application achieves modular design and manufacturing of the complex internal flow channel structure of the distributor 100 by including a shell portion 101 and a first embedded portion 102 in the cylinder 10. This allows the first flow channel 11 to be formed through the annular gap between the peripheral side surface of the first embedded portion 102 and the inner sidewall of the shell portion 101, while the second flow channel 12 is directly integrated into the interior of the first embedded portion 102. This separate design simplifies the manufacturing difficulty of internal flow channels with complex geometries (such as the first flow channel 11 and the second flow channel 12) and improves the machining accuracy of each component.

[0077] Understandably, the housing portion 101 can be a cylindrical component formed from a metallic material (such as stainless steel or aluminum alloy) through a stretching or spinning process. The first insert portion 102 can be manufactured from engineering plastic or ceramic material using high-precision injection molding or 3D printing technology. Its outer surface is designed with a specific contour so that, when assembled into the housing portion 101, it forms a first flow channel 11 with a predetermined cross-sectional area and shape together with the inner wall of the housing portion 101. The first insert portion 102 can be pressed into the housing portion 101 by an interference fit, or it can be engaged, positioned, and fixed by providing a positioning groove on the inner wall of the housing portion 101 and providing corresponding protrusions on the first insert portion 102.

[0078] Considering that if the size ratio of the starting part of the second flow channel 12 to the overall cavity of the cylinder 10 is not appropriate, it may cause the fluid to generate large local resistance or uneven velocity distribution when entering the second flow channel 12, affecting the diversion efficiency and overall performance.

[0079] Based on this, in some embodiments, such as Figure 2 and Figure 3 As shown, the radius of the second starting end 12a is R1, the radius of the cavity of the housing part 101 corresponding to the first inner part 102 is R2, and R1 / R2≥0.2, R1 / R2≤0.4.

[0080] Specifically, the radius R1 of the second starting end 12a refers to the radial dimension of the initial portion of the second flow channel 12 near the inlet hole 10c. This radius directly determines the initial cross-sectional area of ​​the fluid entering the second flow channel 12, thus affecting the initial flow velocity and pressure distribution of the fluid. R1 can be determined by adjusting the structural dimensions of the first embedded portion 102, for example, by changing the diameter of the central portion of the first embedded portion 102, or by designing a tapered or arc-shaped transition section at the starting end of the first embedded portion 102 to indirectly affect the effective radius. The radius R2 of the cavity of the housing portion 101 corresponding to the first embedded portion 102 refers to the radial dimension of the internal cavity of the housing portion 101 at the position corresponding to the first embedded portion 102. It represents the overall effective flow space of the distributor 100 in this region. R2 is a key parameter for measuring the overall size of the distributor 100. Together with R1, it determines the geometric conditions for the initial distribution of fluid between the first flow channel 11 and the second flow channel 12 after entering the distributor 100. R2 is usually determined by the inner diameter of the housing portion 101 and can be controlled by methods such as mold forming and machining. In some designs, the inner wall of the housing portion 101 may not be perfectly cylindrical, and R2 can be taken as the average radius or the maximum effective radius of that area.

[0081] The ratio R1 / R2≥0.2 and R1 / R2≤0.4 defines the relative size relationship between the initial radius R1 of the second flow channel 12 and the corresponding cavity radius R2 of the housing portion 101. This ratio range is designed to optimize the initial flow splitting effect of the fluid at the inlet of the splitter 100.

[0082] The solution in this application limits the ratio of the radius R1 of the second starting end 12a to the radius R2 of the cavity corresponding to the first embedded part 102 in the shell part 101 to between 0.2 and 0.4. This ensures that after the fluid enters the cylinder 10 from the inlet hole 10c, it can obtain a reasonable initial cross-sectional area distribution when simultaneously entering the annular first flow channel 11 and the second flow channel 12 inside the first embedded part 102. When this ratio is within this range, the fluid will not experience excessive local flow resistance and pressure loss due to an excessively narrow inlet when entering the second flow channel 12, nor will it experience uneven flow velocity or unnecessary turbulence due to an excessively wide inlet. This optimized inlet geometry allows the fluid to enter the second flow channel 12 more smoothly and uniformly, thereby improving the initial flow splitting effect of the fluid inside the distributor 100 and reducing energy loss at the inlet.

[0083] For example, the inner diameter of the housing portion 101 of the distributor 100 at the cavity corresponding to the first embedded portion 102 can be designed to be 20 mm, and its radius R2 is 10 mm. To satisfy the R1 / R2 ratio being in the range of 0.2 to 0.4, the radius R1 of the second starting end 12a can be designed to be 2.5 mm. In this case, the R1 / R2 ratio is 0.25, which is within the defined range. In this configuration, the central portion of the first embedded portion 102 can be designed as a cylindrical structure with a diameter of 5 mm, and the starting portion of the second flow channel 12 is formed inside it. An annular first flow channel 11 is formed between the inner wall of the housing portion 101 and the outer wall of the first embedded portion 102. This dimensional design allows the fluid to be distributed into the second flow channel 12 and the first flow channel 11 with a relatively balanced flow rate when entering the distributor 100, reducing fluid impact and pressure fluctuations.

[0084] It is understandable that R1 / R2 can be 0.2, 0.25, 0.3, 0.35, 0.4, etc.

[0085] In some embodiments, the radius of the cavity of the housing portion 101 corresponding to the first inner portion 102 is R2, the radius of the second termination end 12b is R3, and R3 / R2≥0.3, R3 / R2≤0.5.

[0086] The radius R2 of the cavity corresponding to the first inner portion 102 in the shell portion 101 refers to the inner diameter of the shell portion 101 of the cylinder 10 in the region where the first inner portion 102 is located. This radius R2 defines the maximum radial space available to the fluid in this region. The radius R3 of the second termination end 12b refers to the radial dimension of the second flow channel 12 at the outlet when the fluid leaves the flow channel. This radius R3 directly affects the flow velocity and pressure distribution of the fluid when it flows out of the second flow channel 12. The ratio range of R3 / R2 defines the relative size between the radius R3 of the second termination end 12b and the radius R2 of the cavity corresponding to the shell portion 101. The setting of this ratio range is intended to optimize the flow pattern of the fluid when it flows out of the second flow channel 12, ensuring that the fluid can smoothly and uniformly enter the subsequent transition cavity 13, avoiding excessive flow velocity and jet effect due to an excessively small outlet, or insufficient fluid diffusion due to an excessively large outlet.

[0087] This application ensures that the outlet size of the second flow channel 12 matches the overall internal space of the distributor 100 by limiting the proportional relationship between the radius R3 of the second termination end 12b and the corresponding cavity radius R2 of the housing portion 101, i.e., R3 / R2 is within the range of 0.3 to 0.5. When fluid flows out from the second termination end 12b of the second flow channel 12, this proportional range can effectively control the diffusion angle and velocity attenuation of the fluid, avoiding the formation of a high-speed jet due to an excessively small outlet, or insufficient fluid diffusion or poor mixing with the fluid in the first flow channel 11 due to an excessively large outlet. This precise dimensional matching allows the fluid to form a more uniform flow velocity distribution when entering the transition cavity 13, reducing the generation of local eddies and pressure losses.

[0088] For example, suppose the radius R2 of the cavity corresponding to the first embedded portion 102 in the housing portion 101 is 50 mm. According to the limitations of this application, the radius R3 of the second termination end 12b should satisfy R3 / R2≥0.3 and R3 / R2≤0.5. Therefore, the value of R3 should be between 15 mm and 25 mm. For example, the radius R3 of the second termination end 12b can be designed to be 20 mm. In this case, the structure of the first embedded portion 102 will form an outlet with a radius of 20 mm at the second termination end 12b, which forms a suitable transition area with the cavity with a radius of 50 mm inside the housing portion 101.

[0089] It is understandable that R3 / R2 can be 0.3, 0.35, 0.4, 0.45, 0.5, etc.

[0090] In some embodiments, a wide portion 102a is formed between the two ends of the first embedded portion 102, and the cross-sectional area of ​​the wide portion 102a is greater than the cross-sectional area of ​​the rest of the first embedded portion 102 excluding the wide portion 102a.

[0091] The wide portion 102a refers to a region with a large cross-sectional area formed between the two ends of the first inner portion 102 along its axial direction. The cross-sectional area of ​​the wide portion 102a is designed to be larger than the cross-sectional area of ​​the other parts of the first inner portion 102 excluding the wide portion 102a. This structure allows the fluid to experience a local expansion at the wide portion 102a when flowing through the first inner portion 102. For example, the wide portion 102a can be designed such that the inner wall of the first inner portion 102 protrudes outward, forming a drum-shaped or spindle-shaped internal space; or, the wall thickness of the first inner portion 102 can be thinned at the wide portion 102a, thereby increasing the cross-sectional area of ​​the internal flow channel.

[0092] By providing a wide portion 102a between the two ends of the first embedded portion 102, the fluid undergoes a local expansion at the wide portion 102a when flowing in the second flow channel 12. When the fluid enters this expansion region, its velocity decreases accordingly, and part of its kinetic energy is converted into static pressure energy, thereby helping to stabilize the fluid flow and reduce turbulence and eddies that may be generated when the fluid flows at high speeds. This design effectively avoids local high-speed jets or fluid separation phenomena inside the second flow channel 12, ensuring a more uniform velocity distribution and a more stable pressure state before the fluid enters the transition cavity 13.

[0093] For example, the first embedded portion 102 can be configured as a component with a variable cross-sectional shape. For instance, the outer contour of the first embedded portion 102 can be designed as a spindle shape that is thicker in the middle and thinner at both ends, or its internal flow channel can be designed to have an annular expansion section at the axial midpoint.

[0094] By forming a wide portion 102a between the two ends of the first embedded portion 102, and making its cross-sectional area larger than the cross-sectional area of ​​the rest of the first embedded portion 102 excluding the wide portion 102a, a local expansion region can be effectively formed inside the second flow channel 12. This expansion region can reduce the fluid velocity at that location, thereby helping to stabilize the fluid flow and reduce the generation of turbulence and eddies. This is crucial for the subsequent entry of fluid into the transition cavity 13 and further flow splitting processes, ensuring uniform distribution of fluid within the splitter 100 and improving splitting efficiency and accuracy. Furthermore, this design also helps to reduce local pressure loss of fluid in the second flow channel 12, optimizing overall hydrodynamic performance, thereby enabling the splitter 100 to operate more stably and efficiently.

[0095] Considering that if there is a lack of proportional relationship between the size of the width portion 102a and the size of the housing portion 101, the flow cross-sectional area of ​​the first flow channel 11 may be unreasonable, thereby affecting the flow velocity distribution, pressure drop and overall flow splitting efficiency of the fluid.

[0096] Based on this, in some embodiments, the radius of the cavity of the housing portion 101 corresponding to the first embedded portion 102 is R2, the radius of the wide portion 102a is R4, R4 / R2≥0.6, and R4 / R2≤0.8.

[0097] The radius R2 of the cavity corresponding to the first inner portion 102 in the housing portion 101 refers to the inner radial dimension of the housing portion 101 at the location of the first inner portion 102. This radius R2 is a basic dimensional parameter of the internal space of the distributor 100, which determines the overall radial layout of the first flow channel 11 and the second flow channel 12. R2 can be a constant value, for example, the interior of the housing portion 101 can be a cylindrical cavity, or it can vary along the axial direction y, for example, forming a conical or stepped cavity. The radius R4 of the width portion 102a refers to the maximum radial dimension of the width portion 102a on the first inner portion 102. The width portion 102a is a local expansion structure of the first inner portion 102, and its radius R4 directly affects the radial width of the first flow channel 11 at that location. R4 can be determined by the geometry of the first inner portion 102; for example, if the width portion 102a is an annular protrusion, then R4 is its outer diameter.

[0098] This application precisely defines the ratio between the radius R4 of the width 102a of the first embedded portion 102 and the corresponding cavity radius R2 of the housing portion 101, thereby effectively controlling the radial clearance of the first flow channel 11 at the width 102a. When fluid enters the distributor 100 and flows through the first flow channel 11, the presence of the width 102a changes the cross-sectional area of ​​the flow channel. By controlling the R4 / R2 ratio between 0.6 and 0.8, the flow area of ​​the first flow channel 11 at the width 102a can be ensured to be within a suitable range. This not only helps maintain a stable flow velocity of the fluid in the first flow channel 11, avoiding excessively high or low local flow velocities, but also effectively guides the fluid, reducing the generation of turbulence and eddies, thereby reducing energy loss when the fluid passes through. When this ratio is met, the first flow channel 11 can work more effectively with the second flow channel 12 to achieve uniform fluid distribution and provide more stable fluid conditions for subsequent jetting and flow equalization processes.

[0099] For example, the inner wall of the housing portion 101 can be configured as a cylindrical cavity with an inner diameter of R2. The wide portion 102a of the first embedded portion 102 can be designed as an annular protrusion with a maximum radius of R4. For example, when the cavity radius R2 of the housing portion 101 is 100 mm, the radius R4 of the wide portion 102a can be set to 70 mm. In this case, the ratio of R4 / R2 is 0.7, satisfying the defined range of 0.6 to 0.8. In this configuration, the radial clearance of the first flow channel 11 at the wide portion 102a is R2 minus R4, i.e., 30 mm. The surface of the wide portion 102a can be designed as a smooth arc or gentle slope to reduce fluid impact and pressure drop.

[0100] For example, R4 / R2 can be 0.6, 0.65, 0.7, 0.75, 0.8, etc.

[0101] In some embodiments, the second flow channel 12, the transition cavity 13, the second jet cavity 15, and the flow equalization cavity 16 are arranged sequentially from the inlet end 10a to the outlet end 10b along the axial direction y of the cylinder 10.

[0102] Specifically, the second flow channel 12 is one of the main fluid channels inside the distributor 100, and its main function is to guide the fluid entering from the inlet orifice 10c. This flow channel is typically designed with a specific cross-sectional area and shape to control the initial flow velocity and pressure of the fluid. The transition chamber 13 is an intermediate chamber connecting different fluid channels, and its function is to collect the fluid from the first flow channel 11 and the second flow channel 12 and provide space for subsequent fluid mixing. The second jet chamber 15 is a key chamber inside the distributor 100 for fluid mixing. It receives the fluid from the transition chamber 13 and communicates with the first jet chamber 14, promoting initial mixing of the fluid through jet action. The flow equalization chamber 16 is the final fluid distribution chamber of the distributor 100, and its main function is to further homogenize the fluid, ensuring that the fluid reaches a highly uniform state before entering the multiple distribution orifices 10d. The arrangement of fluid channels and chambers along the axial direction y of the cylinder 10 from the inlet end 10a to the outlet end 10b means that these fluid channels and chambers are arranged sequentially along the longitudinal axis of the distributor 100, from the fluid inlet to the fluid outlet. This arrangement can be achieved by setting a series of interconnected baffles, embedded structures, or integrally formed cavities inside the cylinder 10 to ensure that the fluid flows sequentially along a predetermined path.

[0103] In other words, by arranging the second flow channel 12, transition cavity 13, second jet cavity 15, and flow equalization cavity 16 sequentially along the axial direction y of the cylinder 10 from the inlet end 10a to the outlet end 10b, a clear and smooth fluid transport path is constructed. The fluid first enters the second flow channel 12 through the inlet hole 10c (while some fluid also enters the first flow channel 11), and the second flow channel 12 guides the fluid to the transition cavity 13. In the transition cavity 13, the fluids from the first flow channel 11 and the second flow channel 12 merge. Subsequently, the merged fluid smoothly enters the second jet cavity 15, where it undergoes preliminary jet mixing with the fluid in the first jet cavity 14. Finally, the mixed fluid enters the flow equalization cavity 16, where it is further homogenized before being uniformly discharged through multiple flow dividers 10d. This orderly axial arrangement ensures a clear flow direction for the fluid within the distributor 100, preventing unnecessary backflow, eddies, or turbulence between different chambers. This effectively reduces fluid flow resistance and energy loss. Simultaneously, this structural layout provides ample and continuous space for fluid mixing and homogenization at each stage, ensuring fluid uniformity before distribution.

[0104] In some embodiments, the cylindrical body 10 may include a shell portion 101, a first inner portion 102, and a second inner portion 103.

[0105] The housing 101 is the external main structure of the distributor 100, having an inlet end 10a and an outlet end 10b, used to house internal components and provide overall structural support and protection. The housing 101 can be manufactured from a metal material (e.g., stainless steel, aluminum alloy) using a one-piece molding process, or from a high-strength engineering plastic (e.g., polypropylene, polyvinyl chloride) using injection molding. In another implementation, the housing 101 can also be composed of multiple parts assembled by welding, threaded connections, or snap-fit ​​connections.

[0106] The first embedded portion 102 is a structural component provided inside the shell portion 101, which extends from the inlet end 10a along the axial direction y of the cylinder 10 to the outlet end 10b. The peripheral side surface of the first embedded portion 102 is spaced apart from the inner sidewall of the shell portion 101, thereby forming a first flow channel 11.

[0107] In addition, the first embedded part 102 is provided with a second flow channel 12, which can be integrally formed during the manufacturing process of the first embedded part 102, for example by casting, injection molding or drilling.

[0108] The second embedded portion 103 is another key structural component located inside the shell portion 101. It is spaced apart from the first embedded portion 102 along the axial direction y of the cylinder 10, thus forming a transition cavity 13. This spaced arrangement simplifies the formation process of the transition cavity 13 and ensures the connection accuracy between it and the first flow channel 11 and the second flow channel 12. The peripheral side surface of the second embedded portion 103 is spaced apart from the inner sidewall of the shell portion 101, thus forming a first jet cavity 14. The second embedded portion 103 can be manufactured using similar processes and materials as the first embedded portion 102. In addition, the second embedded portion 103 also has a second jet cavity 15, a first jet hole 14a, and a second jet hole 15a inside. These internal cavities and holes can be integrally formed during the manufacturing process of the second embedded portion 103. Along the axial direction y of the cylinder 10, the end of the second embedded portion 103 facing the outlet end 10b is spaced apart from the outlet end 10b, thus forming a flow equalization cavity 16. This structure allows the formation of the flow equalization cavity 16 to be achieved through the end design of the second inner part 103 and its cooperation with the housing part 101, which helps to achieve uniform distribution of fluid before diversion.

[0109] By including three main components—a housing portion 101, a first inner portion 102, and a second inner portion 103—the flow divider 100 achieves modular construction of the internal flow channels and cavities. Specifically, after the fluid enters the cylinder 10 from the inlet end 10a, a portion of the fluid flows through the annular first flow channel 11 formed by the peripheral side surface of the first inner portion 102 and the inner wall of the housing portion 101, while another portion flows through the second flow channel 12 inside the first inner portion 102. Subsequently, the fluid merges from the first termination end 11b of the first flow channel 11 and the second termination end 12b of the second flow channel 12 into the transition cavity 13 formed by the axial spacing between the first inner portion 102 and the second inner portion 103. In the transition cavity 13, the fluid undergoes preliminary mixing and buffering. Next, the fluid enters the annular first jet cavity 14 formed by the peripheral side surface of the second inner portion 103 and the inner wall of the housing portion 101, and the second jet cavity 15 inside the second inner portion 103. The second jet chamber 15 is connected to the first jet chamber 14 through the first jet hole 14a, allowing the fluid to be accelerated and mixed through precisely designed jet holes before entering the flow equalization chamber 16, thereby producing a jet effect. Finally, the fluid enters the flow equalization chamber 16 from the second jet chamber 15 through the second jet hole 15a, formed by the gap between the end of the second embedded part 103 and the outlet end 10b, where it is further homogenized before finally flowing out through multiple diversion holes 10d. This split structure improves the manufacturing precision of each flow channel and cavity, simplifies the overall assembly process, and ensures precise alignment and sealing between fluid paths, effectively solving the challenges of manufacturing and assembling complex internal structures.

[0110] In other words, the split design of the distributor in this application simplifies the overall assembly process, reduces the requirements for assembly technology, and reduces the risk of fluid leakage or uneven flow resistance caused by assembly errors.

[0111] In some embodiments, the radius of the second jet cavity 15 is R5, the radius of the flow equalization cavity 16 is R6, and the ratio of R5 to R6 satisfies R5 / R6≥0.6 and R5 / R6≤0.8.

[0112] The radius R5 of the second jet cavity 15 refers to the radial dimension of the second jet cavity 15. R5 can be a constant radius, such as when the second jet cavity 15 is cylindrical; or, R5 can be the effective radius or average radius for a non-cylindrical cavity. This radius can be determined based on the fluid properties, the expected flow rate, and the overall design requirements of the distributor 100. In another implementation, R5 can vary along the axial direction, for example, forming a conical or stepped cavity, in which case R5 can represent its maximum radius or the effective radius of a specific cross-section. The radius R6 of the flow equalization cavity 16 refers to the radial dimension of the flow equalization cavity 16. R6 can be a constant radius, such as when the flow equalization cavity 16 is cylindrical; or, R6 can be the effective radius or average radius for a non-cylindrical cavity. In another implementation, R6 can be defined by the outermost boundary of the flow equalization cavity 16, even if the boundary is not circular, R6 can represent the equivalent hydraulic radius or the maximum radial range.

[0113] By controlling R5 / R6 within the range of 0.6 to 0.8, an optimal balance is achieved during the fluid expansion process. For example, if R5 is too small relative to R6, the sudden expansion of the fluid may lead to significant pressure loss and turbulence; while if R5 is too large relative to R6, the flow equalization cavity 16 may not provide enough space for the fluid to stabilize and achieve a uniform distribution.

[0114] As can be seen, by controlling the ratio of the radius R5 of the second jet cavity 15 to the radius R6 of the flow equalization cavity 16 within the range of 0.6 to 0.8, this application can effectively optimize the flow state of the fluid entering the flow equalization cavity 16 from the second jet cavity 15. After passing through the first flow channel 11 and the second flow channel 12 and converging in the transition cavity 13, the fluid enters the first jet cavity 14 and the second jet cavity 15. Subsequently, the fluid enters the flow equalization cavity 16 from the second jet cavity 15. This specific R5 / R6 ratio ensures the smoothness of the fluid expansion from the second jet cavity 15 to the flow equalization cavity 16. It helps to avoid excessive turbulence and separation during the expansion process, thereby significantly reducing the pressure loss of the fluid when passing through the distributor 100. At the same time, it ensures that the fluid can form a more uniform velocity and pressure distribution in the flow equalization cavity 16, greatly improving the uniformity of fluid distribution at the multiple distribution holes 10d.

[0115] It is understandable that R5 / R6 can be 0.6, 0.65, 0.7, 0.8, etc.

[0116] In some embodiments, along the axial direction y of the cylinder 10, the height of the flow equalization cavity 16 is h1, the height of the first jet cavity 14 is h2, and the ratio of h1 to h2 satisfies h1 / (h1+h2)≥0.2 and h1 / (h1+h2)≤0.4.

[0117] The height h1 of the flow equalization chamber 16 refers to its dimension along the axial direction y of the cylinder 10. The main function of the flow equalization chamber 16 is to further mix and stabilize the fluid ejected from the second jet chamber 15, ensuring the fluid has the most uniform pressure and velocity distribution possible before entering the multiple flow dividers 10d. The size of its height h1 directly affects the residence time, mixing degree, and pressure recovery effect of the fluid within the flow equalization chamber 16. For example, h1 can refer to the axial length of the flow equalization chamber 16, or the maximum effective flow height of the flow equalization chamber 16 in the axial direction y. The height h2 of the first jet chamber 14 refers to its dimension along the axial direction y of the cylinder 10. The first jet chamber 14 receives fluid from the transition chamber 13 and communicates with the second jet chamber 15 through the first jet hole 14a, together forming a jet structure. The size of its height h2 affects the flow path, jet effect, and interaction with the second jet chamber 15 within the first jet chamber 14. For example, h2 can refer to the axial length of the first jet cavity 14, or the maximum effective flow height of the first jet cavity 14 in the axial direction y.

[0118] The ratio h1 / (h1+h2)≥0.2 and h1 / (h1+h2)≤0.4 defines the relative dimensions of the flow equalization cavity 16 and the first jet cavity 14 in the axial direction y. This ratio is set to optimize energy conversion and pressure distribution of the fluid during the jetting and flow equalization processes. For example, when h1 / (h1+h2) is 0.2, it means the height of the flow equalization cavity 16 is approximately one-quarter of the height of the first jet cavity 14; when h1 / (h1+h2) is 0.4, it means the height of the flow equalization cavity 16 is approximately two-thirds of the height of the first jet cavity 14. This range of ratios ensures that after the fluid is accelerated by the jet, there is sufficient space and time for thorough mixing and pressure recovery within the flow equalization cavity 16, while avoiding excessive volume redundancy or pressure loss due to an overly large flow equalization cavity 16, and also avoiding poor flow equalization due to an overly small flow equalization cavity 16.

[0119] That is, by limiting the proportional relationship between the height h1 of the flow equalization chamber 16 and the height h2 of the first jet chamber 14, i.e., h1 / (h1+h2) is between 0.2 and 0.4, this application ensures that the fluid, after passing through the jetting action of the first jet chamber 14 and the second jet chamber 15, can be fully mixed and pressure restored within a flow equalization chamber 16 of appropriate size. After entering the distributor 100 through the inlet orifice 10c, the fluid simultaneously flows through the first flow channel 11 and the second flow channel 12, and converges in the transition chamber 13. Subsequently, the fluid enters the first jet chamber 14 and the second jet chamber 15, wherein the second jet chamber 15 is connected to the first jet chamber 14 through the first jet orifice 14a, generating a jetting effect that allows the fluid to gain a certain kinetic energy before entering the flow equalization chamber 16. The flow equalization chamber 16 receives the fluid from the second jet chamber 15 and further homogenizes it, finally outputting it through multiple diversion orifices 10d. If the height h1 of the flow equalization cavity 16 is too small relative to the height h2 of the first jet cavity 14, the fluid will not stay in the flow equalization cavity 16 for long enough, resulting in insufficient mixing and potentially uneven distribution of the fluid at the diversion orifice 10d. If the height h1 of the flow equalization cavity 16 is too large, the fluid may have an excessively long flow path in the flow equalization cavity 16, increasing flow resistance, causing unnecessary pressure loss, and potentially increasing the overall size of the diverter 100.

[0120] For example, the cylinder 10 of the flow divider 100 can be cylindrical. Along the axial direction y of the cylinder 10, the flow equalization cavity 16 can be designed as an annular cavity with a certain axial length, its height h1 referring to the axial length of this annular cavity. The first jet cavity 14 can also be designed as an annular cavity, its height h2 referring to the axial length of this annular cavity. In actual manufacturing, h1 and h2 can be precisely controlled by adjusting the axial dimensions of the internal structural components constituting the flow equalization cavity 16 and the first jet cavity 14, or the axial distance between them. For example, the axial height h1 of the flow equalization cavity 16 can be set to 10 mm, and the axial height h2 of the first jet cavity 14 to 30 mm. In this case, h1 / (h1+h2) = 10 / (10+30) = 10 / 40 = 0.25, a value falling within the range of 0.2 to 0.4. Alternatively, h1 can be set to 15mm and h2 to 25mm. In this case, h1 / (h1+h2) = 15 / (15+25) = 15 / 40 = 0.375, which also falls within this range.

[0121] It is understandable that h1 / (h1+h2) can be 0.2, 0.25, 0.3, 0.4, etc.

[0122] In some embodiments, the number of diversion holes 10d is N1, the number of first jet holes 14a is N2, N2≥2N1, and N2≤4N1.

[0123] The number N1 of the diversion orifices 10d refers to the number of holes on the outlet end 10b of the distributor 100 used to ultimately divert the fluid to an external system. These diversion orifices 10d are the final outlets for the fluid leaving the distributor 100, and their number depends on the specific application's requirement for the number of diversion paths. For example, in some applications, it may be necessary to divide the fluid into 2, 3, or 4 paths, in which case N1 can be 2, 3, or 4, respectively.

[0124] The number N2 of the first jet holes 14a refers to the number of holes connecting the second jet cavity 15 and the first jet cavity 14. For example, four, six or eight first jet holes 14a can be provided to achieve different fluid injection effects.

[0125] The ratio N2 ≥ 2N1 and N2 ≤ 4N1 defines the proportional relationship between the number N2 of the first jet orifice 14a and the number N1 of the diversion orifice 10d. This means that the number of the first jet orifice 14a is at least twice the number of the diversion orifice 10d, but no more than four times it. For example, if the number N1 of the diversion orifice 10d is 2, then the number N2 of the first jet orifice 14a can be selected between 4 and 8. If N1 is 3, then N2 can be selected between 6 and 12.

[0126] This application sets the number N2 of the first jet orifices 14a to be 2 to 4 times the number N1 of the diverting orifices 10d, allowing fluid entering the first jet cavity 14 from the second jet cavity 15 to be injected through more channels. In the structure of the diverter 100 described above, the fluid passes through the first flow channel 11 and the second flow channel 12, converges in the transition cavity 13, and then enters the first jet cavity 14 and the second jet cavity 15. The increased number of first jet orifices 14a, which serve as channels connecting the second jet cavity 15 and the first jet cavity 14, means that when fluid enters the first jet cavity 14, it can be injected from more points and in a more dispersed manner. This multi-point injection method helps to form a more uniform flow field within the first jet cavity 14, reducing local velocity differences and pressure fluctuations. When the fluid further enters the flow equalization chamber 16 from the first jet chamber 14 and finally flows out through the diversion orifice 10d, it has already been sufficiently mixed and homogenized in the early stage, thus ensuring that the flow rate and pressure of the fluid obtained by each diversion orifice 10d tend to be consistent. This design effectively solves the technical problem of uneven fluid distribution in multi-channel diversion scenarios and improves the overall performance of the diverter 100.

[0127] For example, suppose the distributor 100 needs to uniformly distribute fluid to four independent outlets, i.e., the number N1 of the diversion orifices 10d is 4. According to the above technical solution, the number N2 of the first jet orifices 14a should satisfy the condition N2≥2N1 and N2≤4N1, i.e., N2 should be between 8 and 16. In this case, the number N2 of the first jet orifices 14a can be set to 12. These 12 first jet orifices 14a can be evenly distributed around the periphery of the second jet cavity 15 and communicate with the first jet cavity 14. When the fluid enters the first jet cavity 14 from the second jet cavity 15 through these 12 first jet orifices 14a, the fluid is more finely dispersed and guided, thereby forming a more stable and uniform fluid layer in the first jet cavity 14. Subsequently, this uniform fluid layer enters the flow equalization cavity 16 and finally flows out through the four diversion orifices 10d.

[0128] In some embodiments, the orientation direction of the first termination end 11b is the same as the axial direction y of the cylinder 10, and the orientation direction of the first jet hole 14a forms an angle θ with the orientation direction of the first termination end 11b, where θ ≥ 30° and θ ≤ 60°.

[0129] Specifically, the orientation of the first termination end 11b is aligned with the axial direction y of the cylinder 10. This ensures that the initial momentum direction of the fluid flowing out of the first flow channel 11 is consistent with the axial direction y of the cylinder 10 when it enters the transition cavity 13. This helps to form a stable axial flow field, providing a basis for subsequent fluid mixing and splitting. This arrangement can be achieved by designing the outlet of the first termination end 11b to be parallel to the axis y of the cylinder 10, or by making its outlet cross-section perpendicular to the axis y of the cylinder 10.

[0130] The angle θ formed between the orientation direction of the first jet orifice 14a and the orientation direction of the first termination end 11b is introduced to ensure a predetermined relative angle between the fluid ejected from the first jet orifice 14a and the fluid flowing out from the first termination end 11b (whose direction is the same as the axial direction y of the cylinder 10). This angle can be achieved by tilting the central axis of the first jet orifice 14a relative to the axial direction y of the cylinder 10. For example, the first jet orifice 14a can be designed as an oblique opening, or the angle can be formed by providing an oblique flow guiding structure between the second jet cavity 15 and the first jet cavity 14a.

[0131] This application limits the included angle θ to between 30° and 60° to achieve a balance between fluid mixing efficiency and pressure loss. A smaller included angle may lead to insufficient mixing, while an excessively large included angle may cause excessive local pressure loss and unnecessary turbulence, which is detrimental to uniform flow distribution. An angle within this range ensures that the fluid, upon entering the first jet cavity 14, generates sufficient shear and disturbance to promote mixing, while avoiding excessive energy dissipation.

[0132] For example, the cylinder 10 can be a cylindrical shell with its central axis in the axial direction y. The first termination end 11b of the first flow channel 11 can be designed as a circular outlet parallel to the axial direction y of the cylinder 10, allowing fluid to enter the transition cavity 13 along the axial direction y. The first jet orifice 14a can specifically be a plurality of inclined holes opened in the partition wall between the second jet cavity 15 and the first jet cavity 14. For example, the central axis of these inclined holes can be inclined at 45° relative to the axial direction y of the cylinder 10. When fluid is injected into the first jet cavity 14 from these inclined first jet orifices 14a, a spiral or vortex-like flow pattern is formed, generating strong shearing and mixing with the fluid entering axially from the first termination end 11b. This design can effectively promote thorough mixing of the fluid in the first jet cavity 14, laying the foundation for subsequent uniform flow distribution.

[0133] It is understandable that, such as Figure 4 As shown, the first jet orifice 14a can be a continuous slit opened on the partition wall between the second jet cavity 15 and the first jet cavity 14, or it can be a plurality of arrayed micropores. Figure 5 As shown, the plurality of first jet holes 14a can be evenly arranged circumferentially around the second jet cavity 15. Of course, as... Figure 6 As shown, the multiple first jet holes 14a can also be arranged in a spiral pattern along the axial direction of the second jet cavity 15.

[0134] It is understandable that, such as Figure 7 As shown, the second embedded portion 103 can be a cylindrical structure, or it can be a frustum-shaped structure. Figure 8 As shown, in the direction from the inlet orifice 10c to the flow equalization cavity 16, the second embedded portion 103 may be oriented to contract near the flow equalization cavity 16, or, as... Figure 9 As shown, it can also be presented as expanding towards the flow equalization cavity 16. This embodiment does not specifically limit this.

[0135] Secondly, such as Figure 10 As shown, this application proposes an air conditioner 200, including a distributor 100 as described above. By integrating the aforementioned distributor 100, the air conditioner 200 effectively addresses the problem of uneven distribution of the gas-liquid two-phase refrigerant caused by stratified flow or asymmetric annular flow during the distribution process.

[0136] Taking a practical application scenario as an example, when the air conditioner 200 is in cooling mode, the gas-liquid two-phase refrigerant from the compressor enters the distributor 100 through the inlet orifice 10c. Due to the synergistic flow-dividing effect of the first flow channel 11 and the second flow channel 12, and the gradually expanding cross-sectional area of ​​the termination end of the second flow channel 12, the fluid has completed preliminary gas-liquid recombination before entering the transition cavity 13. Subsequently, the oblique jet generated by the first jet orifice 14a forms a vortex disturbance in the first jet cavity 14, enabling the gas-liquid two phases to quickly achieve molecular-level mixing; the flow equalization cavity 16 further equalizes the pressure distribution. Through the above technical solution, the heat exchanger of the air conditioner 200 can maintain a balanced distribution of heat load in each branch, avoiding local frost or overheating, thereby helping to extend the service life of the equipment and reduce energy consumption.

[0137] The above provides a detailed description of a splitter and air conditioner disclosed in this application. This document uses specific examples to illustrate the principles and implementation methods of this application. The description of the above embodiments is only for the purpose of helping to understand the splitter and air conditioner and their core ideas in this application. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the ideas of this application. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A shunt (100), characterized in that, include: The cylindrical body (10) has an inlet end (10a) and an outlet end (10b). The inlet end (10a) is provided with an inlet hole (10c), and the outlet end (10b) is provided with a plurality of diversion holes (10d). The first flow channel (11) is formed inside the cylinder (10). The two ends of the first flow channel (11) are a first starting end (11a) and a first ending end (11b), respectively. The first starting end (11a) is connected to the inlet hole (10c). The second flow channel (12) is formed inside the cylinder (10) along the radial direction (x) of the cylinder (10). The first flow channel (11) is distributed around the outer periphery of the second flow channel (12). The two ends of the second flow channel (12) are a second starting end (12a) and a second ending end (12b), respectively. The second starting end (12a) is connected to the inlet hole (10c). The cross-sectional area of ​​the second ending end (12b) is larger than the cross-sectional area of ​​the second starting end (12a). A transition cavity (13) is formed inside the cylinder (10) and the transition cavity (13) is connected to the first termination end (11b) and the second termination end (12b). A first jet cavity (14) is formed inside the cylinder (10) and is connected to the transition cavity (13); A second jet cavity (15) is formed inside the cylinder (10) along the radial direction (x) of the cylinder (10). A first jet cavity (14) surrounds the outer periphery of the second jet cavity (15). The second jet cavity (15) communicates with the transition cavity (13) and is connected to the first jet cavity (14) through a first jet hole (14a). The cross-sectional area of ​​the first jet hole (14a) is smaller than the cross-sectional area of ​​the first termination end (11b), and the orientation direction of the first jet hole (14a) forms an angle with the orientation direction of the first termination end (11b). A flow equalization cavity (16) is formed inside the cylinder (10). The flow equalization cavity (16) is connected to a plurality of flow splitting holes (10d), and the flow equalization cavity (16) is connected to the second flow splitting cavity (15) through a second flow splitting hole (15a).

2. The shunt (100) according to claim 1, characterized in that, The inner wall of the second flow channel (12) is inclined relative to the axial direction (y) of the cylinder (10), and extends from the second starting end (12a) to the second ending end (12b) away from the axis of the cylinder (10); And / or, the first flow channel (11) is formed with a narrow portion (11c) located between the first starting end (11a) and the first ending end (11b), the cross-sectional area of ​​the narrow portion (11c) being smaller than the cross-sectional area of ​​the rest of the first flow channel (11) excluding the narrow portion (11c).

3. The shunt (100) according to claim 1, characterized in that, The first flow channel (11) includes a first segment (111) and a second segment (112) that are connected. The end of the first segment (111) away from the second segment (112) is formed as the first starting end (11a), and the end of the second segment (112) away from the first segment (111) is formed as the first ending end (11b). The cross-sectional area of ​​the first starting end (11a) is greater than the cross-sectional area of ​​the connection between the first segment (111) and the second segment (112).

4. The shunt (100) according to claim 1, characterized in that, The first flow channel (11) includes a first segment (111) and a second segment (112) that are connected. The end of the first segment (111) away from the second segment (112) is formed as the first starting end (11a), and the end of the second segment (112) away from the first segment (111) is formed as the first ending end (11b). The cross-sectional area of ​​the first ending end (11b) is greater than the cross-sectional area at the connection between the first segment (111) and the second segment (112).

5. The shunt (100) according to claim 4, characterized in that, The inner wall of the second segment (112) is constructed as an arcuate surface, and the side of the second segment (112) opposite to the axis of the cylinder (10) is the outer side of the arcuate surface.

6. The shunt (100) according to any one of claims 1 to 5, characterized in that, The cylindrical body (10) includes a shell portion (101) and a first inner portion (102). The shell portion (101) has the inlet end (10a) and the outlet end (10b). The first inner portion (102) is disposed inside the shell portion (101). The first embedded portion (102) extends from the inlet end (10a) along the axial direction (y) of the cylinder (10) toward the outlet end (10b). The peripheral side surface of the first embedded portion (102) is spaced apart from the inner side wall of the shell portion (101) to form the first flow channel (11). The first embedded portion (102) is provided with a second flow channel (12).

7. The shunt (100) according to claim 6, characterized in that, The radius of the second starting end (12a) is R1, and the radius of the cavity of the housing part (101) corresponding to the first inner part (102) is R2, R1 / R2≥0.2, R1 / R2≤0.4; And / or, the radius of the cavity of the housing portion (101) corresponding to the first embedded portion (102) is R2, the radius of the second termination end (12b) is R3, R3 / R2≥0.3, and R3 / R2≤0.

5.

8. The shunt (100) according to claim 6, characterized in that, A wide portion (102a) is formed between the two ends of the first embedded portion (102), and the cross-sectional area of ​​the wide portion (102a) is greater than the cross-sectional area of ​​the rest of the first embedded portion (102) excluding the wide portion (102a).

9. The shunt (100) according to claim 8, characterized in that, The radius of the cavity in the housing portion (101) corresponding to the first embedded portion (102) is R2, and the radius of the wide portion (102a) is R4, where R4 / R2≥0.6 and R4 / R2≤0.

8.

10. An air conditioner (200), characterized in that, Includes the shunt (100) as described in any one of claims 1 to 9.

Images