Refrigerant distributor, heat exchanger assembly and refrigeration apparatus

Abstract

The utility model provides a kind of refrigerant distributor, heat exchanger assembly and refrigeration equipment.The refrigerant distributor includes distribution body and multiple branch pipes.The distribution body includes liquid inlet end, main part and liquid outlet end, and the main part is hollow structure, and assembly part for assembling liquid inlet pipe is formed on the liquid inlet end, and multiple branch pipe holes distributed around the main part axis are formed on the liquid outlet end.The multiple branch pipes are respectively welded in the multiple branch pipe holes.The flow-through diameter Din of the assembly part is less than or equal to the diameter Φ1 of distribution circle passing through the center of the multiple branch pipe holes, and the vertical distance H1 between the plane where the downstream end of the assembly part is located and the inner surface of the liquid outlet end where the branch pipe hole is located satisfies: 0.25D0≤H1≤2.15D0, wherein D0 is the maximum outer diameter of the main part.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration accessories, and in particular to a refrigerant distributor, heat exchanger assembly and refrigeration equipment. Background Technology

[0002] In refrigeration systems, the refrigerant distributor is located between the outlet of the thermostatic expansion valve and the multi-branch evaporator. Its function is to evenly distribute the throttled refrigerant to each branch of the evaporator. Traditional distributors mainly include Venturi type, pressure drop type, and socket type structures. Among them, the socket type distributor is widely used due to its simple structure and low cost. However, this type of distributor has poor distribution uniformity, and its distribution performance is easily affected by the installation angle and refrigerant mass flow rate. With the continuous improvement of refrigeration product performance, the socket type distributor not only fails to meet the requirements for liquid distribution uniformity, but its strict installation angle requirements are also difficult to adapt to compact products.

[0003] To improve the performance of plug-in refrigerant distributors, existing research has proposed solutions such as adjusting the tilt angle of the outlet branch pipe or changing the insertion depth of the inlet pipe. While these methods improve the uniformity of liquid distribution to some extent, they still cannot meet the performance requirements of current refrigeration products. Therefore, most current refrigeration products still use high-performance but expensive integrated brass Venturi distributors. This choice not only brings high cost pressure, but also, as copper resources increasingly become strategic resources, the application of Venturi distributors will be constrained. Therefore, developing a new type of refrigerant distributor that combines excellent refrigerant distribution performance with low cost has become an urgent need for the industry. Utility Model Content

[0004] In order to overcome the shortcomings of the prior art, this utility model provides a refrigerant distributor, a heat exchanger assembly, and a refrigeration device.

[0005] To achieve the above objectives, the first aspect of this utility model provides a refrigerant distributor, comprising a distribution body and multiple branch pipes. The distribution body includes an inlet end, a main body, and an outlet end. The main body has a hollow structure. The inlet end has an assembly part for assembling an inlet pipe, and the outlet end has multiple branch pipe holes distributed around the axis of the main body. The multiple branch pipes are welded to the multiple branch pipe holes respectively. The flow diameter Din of the assembly part is less than or equal to the diameter Φ1 of the distribution circle passing through the center of the multiple branch pipe holes, and the vertical distance H1 between the plane of the downstream end of the assembly part and the inner surface of the outlet end where the branch pipe holes are located satisfies: 0.25D0≤H1≤2.15D0, where D0 is the maximum outer diameter of the main body.

[0006] According to an embodiment of the first aspect of the present invention, the flow diameter Din of the assembly part satisfies: Din≤Φ2+0.3Dout, where Φ2 is the inscribed circle diameter of the plurality of branch pipe holes, and Dout is the hole diameter at the branch pipe hole that is assembled with the branch pipe.

[0007] According to an embodiment of the first aspect of the present invention, the refrigerant distributor further includes an inlet pipe, a connecting pipe section of which is inserted into the assembly part, and the flow diameter Din of the assembly part is the flow diameter of the connecting pipe section at its downstream end.

[0008] According to an embodiment of the first aspect of the present invention, the inlet pipe further includes a main pipe section located upstream of the connecting pipe section, wherein the flow diameter Din at the downstream end of the connecting pipe section and the inner diameter D1 of the main pipe section satisfy the following condition: 0.4D1≤Din≤1.15D1.

[0009] According to an embodiment of the first aspect of the present invention, the connecting pipe section is narrowed relative to the main pipe section or a bushing is provided inside the connecting pipe section, so that the flow diameter Din at the downstream end of the connecting pipe section is smaller than the inner diameter D1 of the main pipe section. Alternatively, the inlet pipe can be a pipe with a basically uniform inner diameter.

[0010] According to an embodiment of the first aspect of the present invention, the inner wall of the inlet end extends obliquely towards the outlet end, and its inner wall generatrix is ​​an arc or an oblique straight line. The line connecting the projection position K of the outer edge of the branch hole along the axial direction of the main body on the inner wall of the inlet end and the center O of the downstream end of the assembly part forms an angle α with respect to the radial direction of the main body, and 8°≤α≤17°. The axial distance H2 from the inner surface of the outlet end where the branch hole is located to the projection position K satisfies: H2≤H1 and 3mm≤H2≤12mm. The outer edge of the branch hole is the branch hole edge furthest from the axis of the main body.

[0011] According to an embodiment of the first aspect of the present invention, the inner surface of the liquid outlet is a plane; or, a reflective recess is formed on the inner surface of the liquid outlet, and a plurality of branch pipe holes are disposed on the outer periphery of the reflective recess and distributed around the reflective recess.

[0012] According to an embodiment of the first aspect of the present invention, the branch pipe is inserted into the corresponding branch pipe hole, and the insertion end of the branch pipe does not extend into the inner cavity of the main body. Alternatively, the insertion end of the branch pipe extends into the inner cavity of the main body, and the vertical distance H3 between the end face of the insertion end of the branch pipe and the inner surface of the outlet end where the branch pipe hole is located satisfies: H3≤4mm.

[0013] According to an embodiment of the first aspect of the present invention, the dispensing body includes an end cap and an end plate, the small-diameter end of the end cap forming a liquid inlet end, and the end plate being welded to the large-diameter end of the end cap to serve as a liquid outlet end. Alternatively, the dispensing body includes an end cap, a tube body, and an end plate. The small-diameter end of the end cap serves as the liquid inlet, the large-diameter end of the end cap is connected to one end of the tube body, and the end plate is welded to the other end of the tube body as the liquid outlet.

[0014] A second aspect of this utility model also provides a heat exchanger assembly, which includes the aforementioned refrigerant distributor.

[0015] The second aspect of this utility model also provides a heat exchanger refrigeration device, which includes the above-mentioned heat exchanger assembly.

[0016] In summary, the refrigerant distributor provided by this utility model features a hollow structure in its main body, providing ample space for the mixing of the gas-liquid two-phase refrigerant. By limiting the vertical distance H1 from the plane of the downstream end of the assembly section to the inner surface of the liquid outlet end of the branch pipe, the internal volume of the main body can be precisely controlled. This design ensures thorough mixing of the refrigerant while effectively preventing uneven phenomena such as increased segregation of the two-phase refrigerant, reduced flow rate, and liquid refrigerant backflow caused by excessive volume. Furthermore, volume control based on the vertical distance H1 helps regulate the overall pressure drop of the refrigerant distributor, preventing excessive pressure drop from affecting the system's refrigeration efficiency. Further, by limiting the flow diameter Din of the assembly section to be less than or equal to the diameter Φ1 of the distribution circle formed by the centers of multiple branch pipes, the maximum radial penetration area of ​​the refrigerant in the distribution body is geometrically controlled. This design forces the two-phase refrigerant to be fully diffused and mixed within the main body before entering the branch pipes, and then evenly distributed to each branch pipe. This effectively avoids the problem of uneven distribution where the input refrigerant "short-circuits" to the outlet branch pipe before it is fully mixed.

[0017] To make the above and other objects, features and advantages of this utility model more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0018] Figure 1 The diagram shown is a structural schematic of the refrigerant distributor provided in Embodiment 1 of this utility model.

[0019] Figure 2 As shown Figure 1 A schematic diagram of the projection of the flow surface at the middle assembly end onto the inner surface of the liquid outlet end.

[0020] Figure 3 As shown Figure 1 A schematic diagram of the structure after the inlet tube is removed.

[0021] Figure 4 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model.

[0022] Figure 5 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model.

[0023] Figure 6 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model.

[0024] Figure 7 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model.

[0025] Figure 8 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model.

[0026] Figure 9 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model.

[0027] Figure 10 The diagram shown is a structural schematic of a refrigerant distributor provided in another embodiment of this utility model. Detailed Implementation

[0028] Although plug-in distributors have the advantages of simple structure and low cost, their distribution uniformity and stability are poor, making it difficult to meet the requirements of high-performance refrigeration systems. To improve their performance, the inventors conducted in-depth research and discovered that: the plug-in distributor has a large internal cavity, and the flow rate of the two-phase refrigerant decreases due to expansion after entering; the denser liquid refrigerant gradually separates from the gas phase due to insufficient inertial force to overcome gravity, resulting in decreased liquid-liquid uniformity. Increasing the refrigerant flow rate leads to the problem of the two-phase refrigerant flowing directly to the liquid outlet without sufficient mixing, and the uniformity still cannot be improved.

[0029] In view of this, this embodiment provides a high-performance refrigerant distributor. For example... Figure 1 , Figure 2 as well as Figure 3 As shown, the refrigerant distributor 100 includes a distribution body 1 and multiple branch pipes 2. The distribution body 1 includes an inlet end 11, a main body 12, and an outlet end 13. The main body 12 has a hollow structure. The inlet end 11 has an assembly part 111 for assembling the inlet pipe, and the outlet end 13 has multiple branch pipe holes 131 distributed around the axis of the main body 12. The multiple branch pipes 2 are respectively welded to the multiple branch pipe holes 131. The flow diameter Din of the assembly part 111 is less than or equal to the diameter Φ1 of the distribution circle C1 passing through the center of the multiple branch pipe holes 131, and the vertical distance H1 between the plane where the downstream end of the assembly part 111 is located and the inner surface of the outlet end 13 where the branch pipe hole 131 is located satisfies: 0.25D0≤H1≤2.15D0, where D0 is the maximum outer diameter of the main body 12.

[0030] In this embodiment, the distinction between upstream and downstream is based on the refrigerant flow direction. Generally, the refrigerant flows from upstream to downstream, and the downstream area receives refrigerant from upstream. In refrigeration equipment, distributors are generally installed vertically or at an angle. The liquid inlet of the distributor is located below the liquid outlet along the direction of gravity. The inertial force of the refrigerant in the distributor overcomes gravity and flows in the opposite direction of gravity; in this case, upstream and downstream are still distinguished according to the refrigerant flow direction.

[0031] In this embodiment, the assembly part 111 has an assembly hole with a certain straight section on the liquid inlet end 11. The refrigerant distributor also includes a liquid inlet pipe 3, and a connecting pipe section 31 of the liquid inlet pipe 3 is inserted into the assembly part 111. The flow diameter Din of the assembly part 11 is the flow diameter of the connecting pipe section 31 at its downstream end. However, this utility model does not impose any limitations on this. In other embodiments, the connecting pipe section 31 of the liquid inlet pipe may also be sleeved on the assembly 111; in this case, the flow diameter Din of the assembly part is the inner diameter of the assembly part 111 itself.

[0032] In this embodiment, the inlet pipe 3 also includes a main pipe section 32 located upstream of the connecting pipe section 31. The two-phase refrigerant after being throttled by the throttle valve enters the main pipe section 32 and is then input into the distribution body 1 via the connecting pipe section 31. The inner diameter of the main pipe section 32 is D1.

[0033] In the refrigerant distributor 100 provided in this embodiment, the hollow structure of the main body 12 provides a mixing space for the two-phase refrigerant. Based on this, by rationally setting two key parameters—the vertical distance H1 and the flow diameter Din of the assembly section—the contradiction between the refrigerant's deceleration due to expansion and its high-speed direct flow is effectively balanced. The vertical distance H1, as an axial structural parameter, precisely controls the internal volume of the main body 12 while also limiting the axial flow path of the refrigerant within it, avoiding the problem of insufficient mixing due to an excessively short axial flow path. Specifically, the lower limit setting of H1 not only ensures sufficient space for uniform mixing of the two-phase refrigerant but also limits the minimum axial dimension of the main body 12, allowing the two-phase refrigerant to fully diffuse and mix radially after entering, promoting droplet breakage and atomization to enhance the gas-liquid mixing effect. Furthermore, this lower limit setting also considers the overall pressure drop of the refrigerant distributor, preventing increased system flow resistance due to an excessively small internal cavity, which would affect heat exchange efficiency. The upper limit control of the vertical distance H1 effectively avoids excessive expansion and deceleration of the refrigerant caused by the excessive volume of the main body 12, ensuring that the mixed two-phase refrigerant has sufficient inertial force to suppress the separation of the gas and liquid phases caused by gravity.

[0034] On the other hand, the flow diameter Din of the assembly section 111 geometrically limits the maximum radial penetration area of ​​the refrigerant in the distribution body 1, creating an "axial flow restriction-radial flow guidance" flow pattern to force the refrigerant to change direction and diffuse within the inner cavity of the main body 12. Upon encountering this area restriction, the incoming refrigerant cannot directly and massively impact the branch pipe 2 at the outlet end 13, but is forced to diffuse within the inner cavity of the main body 12 and fully mix with the refrigerant inside. This design effectively cuts off the "short-circuit" path of the refrigerant, solving the problem of uneven distribution caused by insufficiently mixed refrigerant flowing directly into the branch pipe. Only refrigerant that has been fully mixed within the inner cavity of the main body 12 can be evenly distributed to each branch pipe 2 under pressure, thereby ensuring a consistent refrigerant supply to each branch of the downstream heat exchanger.

[0035] To verify the impact of vertical distance H1 and through area on the performance of the refrigerant distributor, the inventors conducted a large number of simulation analysis experiments.

[0036] 【1】Analyze the impact of vertical distance H1 on distribution performance.

[0037] by Figure 1 The refrigerant distributor structure shown is used as a sample structure to prepare multiple test samples. Multiple test samples within the same test group are identical in all parameters except for the vertical distance H1. To better study the effect of the vertical distance H1 on the dispensing performance, this experiment sets the flow diameter Din of the assembly part 111 to be less than Φ2, where Φ2 is the diameter of the inscribed circle C2 of the multiple branch pipe holes 131. In this case, the flow surface of the assembly part 111 does not penetrate the branch pipe holes; penetration means that when projected along the axial direction of the dispensing body, the flow surface at the assembly part overlaps with the branch pipe hole. Figure 1 In the middle, the branch pipe 2 is inserted and welded into the branch pipe hole 131. The diameter Dout of the branch pipe hole where it is assembled with the branch pipe is the outer diameter of the insertion end of the branch pipe 2.

[0038] Under the same boundary conditions, CFD (Computational Fluid Dynamics) simulation analysis was performed on the above-mentioned test samples. The software used for the CFD simulation analysis was ANSYS, and the conditions were set as follows: Turbulence model: Realizable k-ε model; Mesh parameters: Tetrahedral unstructured mesh is used; Operating conditions: The working fluid is R32 refrigerant, and the wall boundary is an adiabatic boundary.

[0039] Boundary conditions: turbulence intensity 5%, inlet gas phase velocity 5.6434 m / s, inlet liquid phase velocity 0.3822 m / s, liquid volume fraction 0.0933, dryness fraction 0.22, hydraulic diameter 5.0 mm. Other boundary conditions are detailed in the data table.

[0040] Evaluation parameters: STD and K. STD refers to the standard deviation of the refrigerant mass flow rate at each branch outlet, and K refers to the ratio of the standard deviation STD to the set mass flow rate allocated to each branch. M out The percentage.

[0041] The specific formulas for calculating STD and K are as follows: ; ; in, This represents the average refrigerant mass flow rate at all branch outlets. m j For the first j The refrigerant mass flow rate at the outlet of each branch pipe, n For the number of branches, M out To set the mass flow rate allocated to each branch pipe.

[0042] Sample selection: First test group: Maximum outer diameter of the main body D0 = 15.7 mm, orifice diameter of the branch pipe hole to which it is assembled Dout = 3.4 mm, inner diameter of the main body section of the inlet pipe D1 = 5.0 mm, flow diameter Din = 3.6 mm, number of branch pipes n = 3, set input total mass flow rate M in =53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =17.9Kg / h. Within this test group, 15 test samples were formed based on different vertical distances H1.

[0043] Second test group: Maximum outer diameter of the main body D0 = 17.2 mm, orifice diameter of the branch pipe hole to which it is assembled Dout = 3.8 mm, inner diameter of the main body section of the inlet pipe D1 = 5.0 mm, flow diameter Din = 3.6 mm, number of branch pipes n = 3, set input total mass flow rate M in =53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =17.9Kg / h. Within this test group, 15 test samples were formed based on different vertical distances H1.

[0044] Third test group: Maximum outer diameter of the main body D0 = 15.7 mm, orifice diameter of the branch pipe hole to which it is assembled Dout = 3.4 mm, inner diameter of the main body section of the inlet pipe D1 = 5.0 mm, flow diameter Din = 3.6 mm, number of branch pipes n = 2, set input total mass flow rate M in =53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =26.86Kg / h. Within this test group, 15 test samples were formed based on different vertical distances H1.

[0045] Table 1 summarizes the data from the three test groups. Analysis reveals that in each test group, the STD value, characterizing refrigerant distribution uniformity, initially decreases gradually with decreasing vertical distance H1; however, when H1 decreases to a certain critical value, the STD value begins to increase, and simultaneously, the pressure drop ΔP value, characterizing the pressure drop of the refrigerant distributor, also increases sharply. This simulation result effectively verifies the design principle of the refrigerant distributor provided in this embodiment: reducing the vertical distance H1 decreases the internal volume of the main body 12, effectively curbing excessive refrigerant expansion and improving distribution performance. However, as the vertical distance H1 continuously decreases, the axial flow path of the refrigerant from the inlet end 11 to the outlet end 13 becomes shorter and shorter. An excessively short axial flow path leads to insufficient mixing of the refrigerant before distribution, resulting in deteriorated distribution uniformity. Furthermore, as the vertical distance H1 gradually decreases, the overall pressure drop ΔP of the refrigerant distributor also gradually increases.

[0046] Further analysis revealed that although the critical vertical distance H1 at which STD began to deteriorate varied across different experimental groups, analysis of the relationship between H1 and D0 showed that in each experimental group, the distribution performance began to deteriorate after H1 < 0.25D0. When H1 > 2.15D0, although the absolute increase in STD value was not significant, the K value (i.e., STD / Mout), which characterizes its relative magnitude, exceeded 3%. Therefore, the range 0.25D0 ≤ H1 ≤ 2.15D0 was set.

[0047] [2] Based on the determined vertical distance H1, the influence of the connection between the assembly part and the branch pipe hole on the distribution uniformity and pressure drop is analyzed by simulation. The connection area is adjusted by changing the flow diameter Din of the assembly part.

[0048] by Figure 1 The refrigerant distributor structure shown is used as a sample structure to prepare multiple test samples. The multiple test samples within the same test group are identical in all parameters except for the flow diameter Din of the assembly part 111. For the vertical distance H1, based on the data analysis in Table 1, H1 = 0.486D0 is set; however, this invention does not impose any limitations on this.

[0049] The CFD simulation analysis used ANSYS software. The turbulence model, mesh parameters, operating conditions, and evaluation parameters were the same as those in the simulation analysis of the vertical distance H1 described above, but the boundary conditions were different. The specific boundary conditions were: inlet gas phase velocity 3.5771 m / s, inlet liquid phase velocity 0.4154 m / s, liquid volume fraction 0.0933, dryness fraction 0.22, hydraulic diameter 8.5 mm, and other boundary conditions are detailed in the data table.

[0050] Sample selection: First test group: Maximum outer diameter of the main body D0 = 20.6 mm, orifice diameter of the branch pipe hole to which it is assembled Dout = 3.4 mm, inner diameter of the main body section of the inlet pipe D1 = 8.5 mm, number of branch pipes n = 3, set input total mass flow rate M in =53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =17.9Kg / h.

[0051] Second test group: The maximum outer diameter of the main body D0 = 20.6 mm, the diameter of the branch pipe hole where it is assembled with the branch pipe Dout = 3.4 mm, the inner diameter of the main body section of the inlet pipe D1 = 8.5 mm, the number of branch pipes n = 2, and the total mass flow rate M is set to be input. in =53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =26.86Kg / h.

[0052] Each test group consisted of 17 test samples based on different flow diameters (Din). Three of these samples had Din ≤ Φ2, meaning the assembly part 111 and the branch pipe hole 131 were not connected. The remaining 14 samples had the assembly part 111 connected to the branch pipe hole (Din > Φ2), but with different connection areas. The connection area refers to the area of ​​the overlapping region between the flow surface at the assembly part and the branch pipe hole when projected along the axial direction of the distribution body.

[0053] Table 2 is a summary of the data from the test samples in the two test groups.

[0054] Analysis of the data in Table 2 shows that: First, for the test samples where the assembly part 111 and the branch pipe hole 131 are not connected, not only is the STD excellent but the K value is also very small, indicating that its distribution uniformity is excellent and stable. Second, for the test samples where the connection is complete, when the connection area is small (i.e., Din is approximately Φ2), the influence of the connection area on the STD and K value is relatively small, and the refrigerant distributor still has extremely excellent distribution performance. Furthermore, as Din gradually increases, the connection area gradually increases, and both the STD and K values ​​gradually increase, indicating that the distribution performance gradually decreases; when Din is equal to the diameter Φ1 of the distribution circle C1 passing through the center of multiple branch pipe holes 131, the K value, which represents the relative amplitude of STD, is close to 3%, and the distribution performance decreases. Therefore, in this embodiment, the flow diameter Din of the assembly part 111 is set to be less than or equal to the diameter Φ1 of the distribution circle C1 passing through the center of multiple branch pipe holes 131.

[0055] Further analysis of the data in Table 2 reveals that for test samples with Din ≤ 5.3 mm (Φ2 + 0.3Dout), their distribution performance is extremely excellent, with a K value less than 2.2%. Therefore, preferably, the flow diameter Din of the assembly part 111 is set to satisfy: Din ≤ Φ2 + 0.3Dout. Wherein, Φ2 is the diameter of the inscribed circle C2 of the multiple branch pipe holes 131, and Dout is the hole diameter at the branch pipe hole 131 that is assembled with the branch pipe 2; in this embodiment, it is the outer diameter of the insertion end of the branch pipe 2. Figure 2 In the diagram, the red dashed line represents the distribution circle C1 passing through the center of the multiple branch pipe holes 131, and the blue dashed line represents the inscribed circle C2 of the multiple branch pipe holes 131. These two circles are only for the convenience of illustrating the flow diameter Din of the assembly part 111 and the continuity of the branch pipe holes 131. In the actual refrigerant distributor product, the distribution circle C1 and the inscribed circle C2 do not exist.

[0056] In this embodiment, as Figure 1 and Figure 3 As shown, the inner wall of the inlet end 11 extends obliquely towards the outlet end 13, and its inner wall generatrix is ​​an arc or an oblique straight line. The projection position K of the outer edge of the branch pipe hole 131 along the axial direction of the main body 12 on the inner wall of the inlet end 11 and the line connecting the center O of the downstream end of the assembly part 111 form an angle α with respect to the radial direction of the main body 12, and 8°≤α≤17°. The axial distance H2 from the inner surface of the outlet end 13 where the branch pipe hole 131 is located to the projection position K satisfies: H2≤H1 and 3mm≤H2≤12mm. The outer edge of the branch pipe hole 131 is the edge of the branch pipe hole 131 that is furthest from the axis of the main body 12. This setting further refines the internal cavity volume of the main body 12 based on the vertical distance H1, suppressing the degree of refrigerant expansion while taking into account the axial flow path of the refrigerant to ensure sufficient mixing of the refrigerant. Furthermore, the inclined inner wall of the inlet end 11 forms a secondary reflective surface. The refrigerant with greater kinetic energy input from the inlet end 11 is reflected back into the inner cavity of the main body 12 via the inner surface of the outlet end 13. The reflected refrigerant is then reflected a second time upon reaching the inner wall of the inlet end 11. This multiple reflection not only greatly enhances the turbulence of the refrigerant, but also the continuous change in the refrigerant flow direction during reflection greatly promotes the thorough collision and mixing of refrigerant in different areas within the main body 12.

[0057] Among the positional parameters related to the projection position K of the outer edge of the branch pipe hole 131 on the inner wall of the liquid inlet 11, the included angle α determines the extension slope of the inner wall of the liquid inlet 11 and the secondary reflection distance (i.e., axial distance H2) from the inner surface of the liquid outlet 13 to the inner wall of the liquid inlet 11. Specifically, when the maximum outer diameter D0 of the main body 12 and the position of the branch pipe hole 131 are determined, the larger the included angle α, the larger the tangent slope at the generatrix of the inner wall of the liquid inlet 11 will be, and the longer the axial length of the liquid inlet 11 will be; correspondingly, the secondary reflection distance from the inner surface of the liquid outlet 13 to the inner wall of the liquid inlet 11 will also be larger. In order to make the inner wall of the liquid inlet 11 a secondary reflection surface to enhance the mixing effect, the included angle α needs to be controlled to avoid it being too large; while if the included angle α is too small, the axial distance H2 will be too short, compressing the internal cavity volume of the main body 12, resulting in insufficient mixing space for the refrigerant, and also increasing the pressure drop of the refrigerant distributor.

[0058] Similarly, simulation analysis was used to analyze the influence of the axial spacing H2 and the associated included angle α on the performance of the refrigerant distributor. Under the condition that the maximum outer diameter D0 of the main body 12 and the position of the branch pipe hole 131 are fixed, α varies with H2, so this simulation experiment focuses on examining the influence of H2.

[0059] by Figure 1 The refrigerant distributor structure shown is used as a sample structure. Multiple test samples were fabricated. All test samples were identical except for the axial spacing H2 and the associated included angle α. The CFD simulation analysis used ANSYS software. The turbulence model, mesh parameters, operating conditions, and evaluation parameters were the same as those in the simulation analysis of the vertical distance H1 described above, but the boundary conditions differed. Specifically, the boundary conditions were: inlet gas phase velocity 5.6434 m / s, inlet liquid phase velocity 0.3882 m / s, liquid volume fraction 0.0933, dryness fraction 0.22, hydraulic diameter 5.0 mm. Other boundary conditions are detailed in the data table.

[0060] Sample selection: Maximum outer diameter of the main body D0 = 15.7 mm, orifice diameter of the branch pipe hole for assembly with the branch pipe Dout = 3.4 mm, inner diameter of the main body section of the inlet pipe D1 = 5.0 mm, flow diameter Din = 3.6 mm, number of branch pipes n = 3, set input total mass flow rate M in =53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =17.9Kg / h, and based on the analysis of the data in Tables 1 and 2, the vertical distance H1 was set to 15.7mm (H1=D0), and the assembly end 111 and the branch hole were not connected (Din<Φ2). Based on the different axial spacing H2, 22 test samples were formed.

[0061] Table 3 summarizes the above 22 test samples.

[0062] Analysis of the data in Table 3 shows that: First, the K value of all test samples is less than 3%, indicating excellent distribution performance. This is because H1 satisfies 0.25D0≤H1≤2.15D0 and the assembly end 111 and the branch pipe hole are not connected. Second, as the axial spacing H2 decreases, the STD value and K value, which characterize the uniformity of distribution, first decrease, then increase after reaching a critical value; and as H2 continues to shrink, the pressure drop ΔP increases dramatically, exceeding 0.05 MPa when H3 is less than 3 mm. Furthermore, for test samples with H2 greater than 12 mm, their K values ​​are relatively large and all exceed 2.2%. Therefore, preferably, 3 mm ≤ H2 ≤ 12 mm is set, and the included angle α of the relevant connections is between 8° and 17°. However, this utility model does not impose any limitations on this.

[0063] Considering the influence of local resistance and friction resistance on the refrigerant flow rate in the inlet pipe 3, in order to ensure that the refrigerant can be input into the distribution body 1 with greater kinetic energy to improve the distribution uniformity, the inventors also studied the relationship between the flow diameter Din at the downstream end of the connecting pipe section 31 and the inner diameter D1 of the main pipe section 32.

[0064] by Figure 1 The refrigerant distributor structure shown is used as a sample structure. Multiple test samples were fabricated. The only difference between the multiple test samples was the flow diameter (Din) at the downstream end of the connecting pipe section 31; all other parameters were identical. The CFD simulation analysis used ANSYS software. The turbulence model, mesh parameters, operating conditions, and evaluation parameters were the same as those in the simulation analysis of the vertical distance H1 described above, but the boundary conditions differed. Specifically, the boundary conditions were: inlet gas phase velocity 3.5771 m / s, inlet liquid phase velocity 0.4154 m / s, liquid volume fraction 0.0933, dryness fraction 0.22, hydraulic diameter 8.5 mm. Other boundary conditions are detailed in the data table.

[0065] Sample selection: Maximum outer diameter of the main body D0 = 24 mm, orifice diameter of the branch pipe hole for assembly with the branch pipe Dout = 3.8 mm, inner diameter of the main body section of the inlet pipe D1 = 8.5 mm, number of branch pipes n = 5, set input total mass flow rate M in =71.03Kg / h, set the mass flow rate M distributed to each branch pipe out =14.21Kg / h, and based on the analysis of data from Tables 1, 2, and 3, the vertical distance H1=15.7 (H1=0.654D0), the axial spacing H2=6.5mm, and the assembly end 111 and the branch pipe hole are not connected. Based on the different flow diameters (i.e., Din) at the downstream end of the connecting pipe section 31, 22 test samples were formed.

[0066] Table 4 summarizes the data from the 22 test samples. Analysis of the data in Table 4 shows that: First, the K value of all test samples is less than 3%, indicating excellent distribution performance. This is because H1 satisfies 0.25D0≤H1≤2.15D0 and there is no connection between the assembly end 111 and the branch pipe hole. Second, when Din is between 3.4mm (Din / D1=0.4) and 9.8mm (Din / D1=1.15), the STD value and K value, which characterize the uniformity of distribution, are both extremely excellent (K value less than or equal to 2.2%), and the overall pressure drop ΔP of the refrigerant distributor is also less than 0.05Mpa. Therefore, preferably, the flow diameter Din at the downstream end of the connecting pipe section 31 and the inner diameter D1 of the main pipe section 32 should satisfy: 0.4D1≤Din≤1.15D1. When Din < D1, the input refrigerant is depressurized and accelerated in the connecting pipe section 31 before being input into the distribution body 1; while when Din ≥ D1, the expansion degree of the input refrigerant in the connecting pipe section 31 is limited to avoid the flow rate of the refrigerant decreasing due to excessive expansion.

[0067] For refrigerant distributors, due to space constraints within the refrigeration equipment, the main body section 32 of the inlet pipe 3 typically needs to be bent into an L-shape. When the refrigerant passes through the bend, the liquid phase fluid has a higher density and viscosity, resulting in a greater centrifugal force than the gaseous phase refrigerant. This causes the liquid phase refrigerant to accumulate on the outside of the bend, while the gaseous phase refrigerant accumulates on the inside. This separation of the liquid and gas phases leads to an asymmetrical refrigerant flow pattern entering the connecting pipe section 31, affecting distribution performance. To improve distribution performance, preferably, a value of 0.4D1≤Din<D1 is set. This setting can both reduce the pressure and increase the speed of the refrigerant to improve the refrigerant flow pattern at the inlet of the distribution body 1 and increase the kinetic energy of the refrigerant entering the distribution body 1, thereby improving its mixing and collision effect.

[0068] In this embodiment, the connecting pipe section 31 and the main pipe section 32 are pipe sections with basically the same wall thickness. The connecting pipe section 31 is narrowed relative to the main pipe section 32 so that its downstream flow diameter (i.e., Din) is smaller than the inner diameter D1 of the main pipe section 32. However, this utility model does not impose any limitations on this. In other embodiments, such as Figure 4 As shown, a bushing 4 can also be installed inside the connecting pipe section 31 so that the flow diameter Din at the downstream end of the connecting pipe section 31 is smaller than the inner diameter D1 of the main pipe section 32; or, as shown... Figure 5 As shown, a bushing 4 is added to reduce the flow diameter Din while narrowing the opening. In addition, in other embodiments, if Din is approximately close to D1, the inlet pipe is a pipe with a similar inner diameter; or, the connecting pipe section is appropriately widened relative to the main pipe section so that D1 < Din ≤ 1.15D1.

[0069] Although in this embodiment, the connecting pipe segment 31 and the main pipe segment 32 are integrally formed, this utility model does not impose any limitations on this. In other embodiments, such as Figure 6 As shown, the connecting pipe section 31 and the main pipe section 32 can also be welded separately.

[0070] In this embodiment, as Figure 1 As shown, the inner surface of the liquid outlet 13 is a plane. However, this invention does not limit this aspect. In other embodiments, such as Figure 7 As shown, a reflective recess 132 can also be formed on the inner surface of the liquid outlet 13, and multiple branch pipe holes 131 are disposed on the outer periphery of the reflective recess 132 and distributed around the reflective recess 132. The input refrigerant is reflected, collided and mixed at the reflective recess 132 to further improve the distribution performance.

[0071] In this embodiment, as Figure 1 As shown, the dispensing body 1 includes an end cap 101 and an end plate 103. The small-diameter end of the end cap 101 forms a liquid inlet 11, and the straight section of the end cap 101 forms a main body 12. The end plate 103 is welded to the large-diameter end of the end cap 101 to serve as a liquid outlet 13; specifically, the end plate 103 is embedded in the open end of the end cap 101. However, this utility model does not limit this in any way. In other embodiments, such as Figure 8 As shown, the end plate 103 can also be fitted over the open end of the end cover 101.

[0072] This utility model does not limit the specific structure of the distributing body 1. In other embodiments, such as Figure 9 As shown, the dispensing body can also be provided with an end cap 101, a tube body 102 and an end plate 103. The small diameter end of the end cap 101 serves as the liquid inlet 11, the large diameter end of the end cap 101 is connected to one end of the tube body 102, and the end plate 103 is welded to the other end of the tube body 102 to serve as the liquid outlet 13. The tube body 102 forms the main body 12.

[0073] like Figure 1 As shown, in this embodiment, the branch pipe hole 131 is a through hole formed based on the thickness of the end plate 13. However, this utility model does not impose any limitations on this. In other embodiments, the branch pipe hole 131 may also be a flanged hole, with the branch pipe inserted into the flanged hole (e.g., Figure 8 (As shown) or the outer layer is applied to the folded edge.

[0074] For branch pipe 2, in this embodiment, it is inserted into the corresponding branch pipe hole 131, and the inserted end of branch pipe 2 does not extend into the inner cavity of the main body 12, that is, the end face of the inserted end of branch pipe 2 is located inside the branch pipe hole 131 or is substantially flush with the inner surface of the outlet end 13. However, this utility model does not impose any limitation on this. In other embodiments, such as Figure 10As shown, the insertion end face of the branch pipe 2 can also be set to extend beyond the inner surface of the outlet end 13 to enter the inner cavity of the main body 12. In this case, in order to avoid affecting the axial flow path of the refrigerant in the distribution body 1 due to the branch pipe 2 being inserted too deeply, the vertical distance H3 between the insertion end face of the branch pipe 2 and the inner surface of the outlet end 13 where the branch pipe hole 131 is located is set to satisfy: H3≤4mm.

[0075] Correspondingly, this embodiment also provides a heat exchanger assembly, which includes a heat exchanger and the aforementioned refrigerant distributor. The refrigerant distributor is disposed between the throttling valve and the heat exchanger, and distributes the throttled two-phase refrigerant as evenly as possible into the branches of the heat exchanger to improve the heat exchange performance of the refrigeration equipment.

[0076] Correspondingly, this embodiment also provides a heat exchange device including the above-mentioned heat exchanger assembly, such as an air conditioner.

[0077] In summary, the refrigerant distributor provided by this utility model features a hollow structure in its main body, providing ample space for the mixing of the gas-liquid two-phase refrigerant. By limiting the vertical distance H1 from the plane of the downstream end of the assembly section to the inner surface of the liquid outlet end of the branch pipe, the internal volume of the main body can be precisely controlled. This design ensures thorough mixing of the refrigerant while effectively preventing uneven phenomena such as increased segregation of the two-phase refrigerant, reduced flow rate, and liquid refrigerant backflow caused by excessive volume. Furthermore, volume control based on the vertical distance H1 helps regulate the overall pressure drop of the refrigerant distributor, preventing excessive pressure drop from affecting the system's refrigeration efficiency. Further, by limiting the flow diameter Din of the assembly section to be less than or equal to the diameter Φ1 of the distribution circle formed by the centers of multiple branch pipes, the maximum radial penetration area of ​​the refrigerant in the distribution body is geometrically controlled. This design forces the two-phase refrigerant to be fully diffused and mixed within the main body before entering the branch pipes, and then evenly distributed to each branch pipe. This effectively avoids the problem of uneven distribution where the input refrigerant "short-circuits" to the outlet branch pipe before it is fully mixed.

[0078] Although the present invention has been disclosed above by way of preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art may make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope of protection claimed in the claims.

[0079] Table 1 Table 2 Table 3 Table 4

Claims

1. A refrigerant distributor, characterized in that, include: The dispensing body includes an inlet end, a main body, and an outlet end. The main body has a hollow structure. The inlet end has an assembly part for assembling an inlet pipe. The outlet end has multiple branch pipe holes distributed around the axis of the main body. Multiple branch pipes are welded to the multiple branch pipe holes respectively; Wherein, the flow diameter Din of the assembly part is less than or equal to the diameter Φ1 of the distribution circle passing through the center of the plurality of branch pipe holes, and the vertical distance H1 between the plane where the downstream end of the assembly part is located and the inner surface of the liquid outlet end where the branch pipe hole is located satisfies: 0.25D0≤H1≤2.15D0, where D0 is the maximum outer diameter of the main body part.

2. The refrigerant distributor according to claim 1, characterized in that, The flow diameter Din of the assembly part satisfies: Din≤Φ2+0.3Dout, where Φ2 is the inscribed circle diameter of the multiple branch pipe holes, and Dout is the hole diameter at the branch pipe hole that is assembled with the branch pipe.

3. The refrigerant distributor according to claim 1, characterized in that, The refrigerant distributor also includes an inlet pipe, and the connecting pipe section of the inlet pipe is inserted into the assembly part. The flow diameter Din of the assembly part is the flow diameter of the connecting pipe section at its downstream end.

4. The refrigerant distributor according to claim 1 or 3, characterized in that, The inlet pipe also includes a main pipe section located upstream of the connecting pipe section. The flow diameter Din at the downstream end of the connecting pipe section and the inner diameter D1 of the main pipe section satisfy the following condition: 0.4D1≤Din≤1.15D1.

5. The refrigerant distributor according to claim 4, characterized in that, The connecting pipe section is narrowed relative to the main pipe section or a bushing is provided inside the connecting pipe section, so that the flow diameter Din at the downstream end of the connecting pipe section is smaller than the inner diameter D1 of the main pipe section. Alternatively, the inlet pipe may be a pipe with a basically uniform inner diameter.

6. The refrigerant distributor according to claim 1, characterized in that, The inner wall of the inlet end extends obliquely towards the outlet end, and its inner wall generatrix is ​​an arc or an oblique straight line. The line connecting the projection position K of the outer edge of the branch hole along the axial direction of the main body on the inner wall of the inlet end and the center O of the downstream end of the assembly part forms an angle α with respect to the radial direction of the main body, and 8°≤α≤17°. The axial distance H2 from the inner surface of the outlet end where the branch hole is located to the projection position K satisfies: H2≤H1 and 3mm≤H2≤12mm. The outer edge of the branch hole is the branch hole edge that is furthest from the axis of the main body.

7. The refrigerant distributor according to claim 1, characterized in that, The inner surface of the liquid outlet is a plane; or, a reflective recess is formed on the inner surface of the liquid outlet, and multiple branch pipe holes are arranged on the outer periphery of the reflective recess and distributed around the reflective recess.

8. The refrigerant distributor according to claim 1, characterized in that, The branch pipe is inserted into the corresponding branch pipe hole, and the inserted end of the branch pipe does not extend into the inner cavity of the main body. Alternatively, the insertion end of the branch pipe extends into the inner cavity of the main body, and the vertical distance H3 between the end face of the insertion end of the branch pipe and the inner surface of the outlet end where the branch pipe hole is located satisfies: H3≤4mm.

9. The refrigerant distributor according to claim 1, characterized in that, The dispensing body includes an end cap and an end plate. The small-diameter end of the end cap forms the liquid inlet, and the end plate is welded to the large-diameter end of the end cap to serve as the liquid outlet. Alternatively, the dispensing body includes an end cap, a tube body, and an end plate, with the small-diameter end of the end cap serving as the liquid inlet, the large-diameter end of the end cap connected to one end of the tube body, and the end plate welded to the other end of the tube body as the liquid outlet.

10. A heat exchanger assembly, characterized in that, Includes the refrigerant distributor as described in claim 1.

11. A refrigeration device, characterized in that, Includes the heat exchanger assembly as described in claim 10.

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