Multi-stage hybrid liquid equalization assembly, liquid distributor, and refrigeration system

Abstract

The application provides a multi-stage mixed liquid equalizing assembly, a distributor and a refrigeration system. The multi-stage mixed liquid equalizing assembly comprises a mixing cavity and a pair of jet mixing members. The mixing cavity has a mixing cavity. The pair of jet mixing members comprises a plurality of liquid equalizing plates arranged along an axis direction in sequence on the outer peripheral wall of the mixing cavity. Each liquid equalizing plate comprises a plurality of refrigerant ports distributed in a circumferential direction around the mixing cavity and a solid part between adjacent refrigerant ports. In the axial direction of the distributor, each solid part of the upper liquid equalizing plate of the adjacent two liquid equalizing plates covers the corresponding refrigerant port of the lower liquid equalizing plate, and the projections of the solid parts on both sides of the corresponding refrigerant port of the lower liquid equalizing plate overlap, so as to form a group of jet flow channels in which the refrigerant flows in opposite directions. The mixed refrigerant enters the plurality of groups of jet flow channels in the pair of jet mixing members through the mixing cavity, and the refrigerant is mixed in opposite directions in each group of jet flow channels.

Description

[0001] The priority information of the present application is as follows:

[0002] Application No.: 2025110932528, Application Date: August 5, 2025, Invention Name: Multistage Mixed Liquid Equalization Assembly, Liquid Distributor and Refrigeration System. TECHNICAL FIELD

[0003] The present application relates to the field of refrigeration accessories, and particularly relates to a multistage mixed liquid equalization assembly, a liquid distributor and a refrigeration system. BACKGROUND

[0004] In a compression refrigeration system, the liquid distributor is a flow distribution element connected between the expansion valve and the heat exchanger assembly. After being throttled by the expansion valve, the two-phase refrigerant flows into the liquid distributor, mixes in the liquid distributor, and is then distributed to each branch of the heat exchanger through multiple branch pipes. Due to the structure of the liquid distributor sample, the existing liquid distributors generally have poor liquid distribution uniformity.

[0005] Therefore, the inventors proposed a refrigeration liquid distributor with a mixing chamber in Chinese Patent CN216204506U. The refrigerant reflects and collides in the mixing chamber to promote gas-liquid phase mixing, thereby improving the liquid distribution uniformity. This structure of the liquid distributor has excellent liquid distribution performance in scenarios with large refrigerant dryness and large refrigerant mass flow rate, but it is still difficult to effectively improve the liquid distribution performance in scenarios with low dryness (such as dryness less than 0.15) or low mass flow rate (branch pipe mass flow rate less than or equal to 40 Kg / h). The main performance is poor liquid distribution uniformity or poor stability under different working conditions. The reason is that in the low dryness or low mass flow rate scenario, the refrigerant input into the liquid distributor is close to a laminar flow, and even after reflection in the mixing chamber, the two-phase refrigerant is still difficult to reach a fully mixed dispersed flow pattern, so it is difficult to stably achieve uniform distribution of the two-phase refrigerant.

[0006] To enhance the mixing effect, some people have proposed a cyclone vane type or impeller type liquid distributor. Although the cyclone vane type has strong turbulence effect, its vane not only has high processing difficulty but also is difficult to apply to a relatively small volume liquid distributor body. The impeller type liquid distributor (such as Chinese Patent CN217464979U and Chinese Patent

[0007] In the Chinese patent CN114963483A, the refrigerant is always output along the surface of the blade in the axial direction, and the mixing effect of the refrigerant during transmission is extremely limited. Even in the Chinese patent CN114963483A, the refrigerant will generate a reflected vortex when impacting each arc-shaped blade, but for the refrigerant close to a laminar flow, the vortex generated by the reflection is still difficult to make the refrigerant enter a uniform mixed dispersed flow type. Therefore, the problem of poor refrigerant distribution uniformity in the low dryness and low flow rate scene cannot be solved, and the blade processing difficulty, high processing cost and assembly difficulty of the impeller structure also exist. SUMMARY

[0008] In order to overcome the shortcomings of the prior art, the present application provides a multi-stage mixed liquid distribution assembly, a liquid distributor and a refrigeration system.

[0009] In order to achieve the above-mentioned purpose, the first aspect of the present application provides a multi-stage mixed liquid distribution assembly, which comprises a mixing cavity and a pair of mixing element. The mixing cavity has a mixing cavity. The pair of mixing element comprises a plurality of liquid distribution plates arranged in sequence along the axial direction of the mixing cavity. Each liquid distribution plate comprises a plurality of refrigerant ports distributed circumferentially around the mixing cavity and a solid portion located between adjacent refrigerant ports. Along the axial direction of the liquid distributor, each solid portion of the upper liquid distribution plate covers the corresponding refrigerant port of the lower liquid distribution plate and overlaps with the projection of the solid portion on both sides of the corresponding refrigerant port of the lower liquid distribution plate to form a pair of jet flow channels in which the refrigerant flows in opposite directions. The mixed refrigerant enters a plurality of pairs of jet flow channels in the pair of mixing element through the mixing cavity, and the refrigerant is mixed in each pair of jet flow channels.

[0010] According to an embodiment of the first aspect of the present application, the minimum width L0 of each overlapping area formed by the overlapping of the solid portion of the upper liquid distribution plate and the solid portion on both sides of the corresponding refrigerant port of the lower liquid distribution plate satisfies: 0.5mm≤L0≤3.5mm.

[0011] According to an embodiment of the first aspect of the present application, the axial spacing H0 between the solid portions of the adjacent two liquid distribution plates satisfies: 0<H0≤3mm.

[0012] According to an embodiment of the first aspect of the present application, the plurality of liquid distribution plates are locally in contact in sequence, and the solid portions of the adjacent two liquid distribution plates have a flow channel gap therebetween.

[0013] Alternatively, the plurality of liquid distribution plates are spaced apart along the axial direction of the mixing cavity to form a flow channel gap between the solid portions of the adjacent two liquid distribution plates.

[0014] According to an embodiment of the first aspect of the present application, the pair of mixing element further comprises a limiting sleeve sleeved on the outer peripheral wall of the mixing cavity, and the adjacent two liquid distribution plates abut the two ends of the limiting sleeve to be spaced apart.

[0015] According to an embodiment of the first aspect of the present application, the liquid equalizing plate is of a monolithic structure, and a connecting hole is formed in the middle of the liquid equalizing plate and is sleeved on the peripheral wall of the mixing cavity.

[0016] Alternatively, the liquid equalizing plate comprises a plurality of independent physical parts, and the plurality of physical parts are spaced apart along the circumference of the mixing cavity and are fixed to the peripheral wall of the mixing cavity.

[0017] According to an embodiment of the first aspect of the present application, among the plurality of liquid equalizing plates, the most upstream liquid equalizing plate is integrally formed with the mixing cavity, and the other liquid equalizing plates are connected to the peripheral wall of the mixing cavity or are sequentially connected to the most upstream liquid equalizing plate.

[0018] According to an embodiment of the first aspect of the present application, the refrigerant port is a notch groove continuously extending along the radial direction of the liquid equalizing plate to the edge of the liquid equalizing plate, and the notch groove is of a fan shape, a rectangular shape or a special shape with a curved groove wall.

[0019] According to an embodiment of the first aspect of the present application, the refrigerant port is one or a combination of a through hole, a flange hole or an arc bubble hole.

[0020] According to an embodiment of the first aspect of the present application, the counterflow mixing element comprises three or more liquid equalizing plates, and a plurality of groups of counterflow flow channels are formed between adjacent two liquid equalizing plates, and the refrigerant is subjected to two-stage or more counterflow mixing in the counterflow mixing element.

[0021] According to an embodiment of the first aspect of the present application, the counterflow mixing element comprises a plurality of liquid equalizing units, each of which comprises at least two liquid equalizing plates and a plurality of groups of counterflow flow channels are formed between adjacent two liquid equalizing plates; and no counterflow flow channel is formed between adjacent liquid equalizing units.

[0022] The second aspect of the present application further provides a distributor comprising a distributor body and the above-mentioned multi-stage mixed liquid equalizing assembly. The multi-stage mixed liquid equalizing assembly is arranged in the distributor body, the mixing cavity of the multi-stage mixed liquid equalizing assembly is substantially coaxial with the distributor body, and the edge of each liquid equalizing plate substantially abuts the inner peripheral wall of the distributor body.

[0023] The second aspect of the present application further provides a refrigeration system comprising the above-mentioned multi-stage mixed liquid equalizing assembly or the above-mentioned distributor.

[0024] In summary, the multi-stage mixing and homogenizing assembly provided by this invention achieves multi-stage mixing of refrigerant through a mixing chamber and a through-jet mixer. The mixing chamber reflects the input laminar refrigerant, breaking the liquid film into droplets to promote gas-liquid two-phase mixing, thereby causing the refrigerant to develop into a diffuse mist flow. The reflected and mixed refrigerant enters the through-jet mixer, where at least one stage of through-jet mixing occurs between its multiple homogenizing plates. Adjacent homogenizing plates in the through-jet mixer are configured such that each solid portion of the upper homogenizing plate not only covers the corresponding refrigerant port on the lower homogenizing plate but also overlaps with the projected solid portions on both sides of the refrigerant port, thus forming a set of through-jet channels with opposite refrigerant flow directions in the two overlapping areas. The reflected and mixed refrigerant, after being throttled and accelerated through the refrigerant ports, enters the multiple sets of through-jet channels between adjacent homogenizing plates. Within each set of through-jet channels, the high-speed refrigerant flowing in opposite directions collides and forms turbulence, enhancing the turbulence of the two-phase flow and causing it to develop into a stable diffuse mist flow, thereby significantly improving the uniformity and stability of the two-phase refrigerant distribution.

[0025] Furthermore, by controlling the axial spacing between the solid parts of adjacent liquid equalization plates, the refrigerant is provided with collision and mixing space in the jet channel while avoiding refrigerant expansion due to excessive channel size, ensuring continuous high-speed convection of the refrigerant and improving the jet mixing effect.

[0026] To make the above and other objects, features and advantages of the present invention more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0027] Figure 1 The diagram shown is a structural schematic of a multi-stage mixing and homogenizing component provided in Embodiment 1 of the present invention.

[0028] Figure 2 As shown Figure 1 A structural diagram from another perspective.

[0029] Figure 3 As shown Figure 1 A projection diagram.

[0030] Figure 4 As shown Figure 1 A projection diagram from another perspective.

[0031] Figure 5 As shown Figure 4 A cross-sectional view along line AA.

[0032] Figure 6 The image shows the refrigerant in... Figure 4 A schematic diagram of the flow.

[0033] Figure 7 The figure shows the refrigerant in the CFD simulation analysis. Figure 1A schematic diagram of the flow in the jet channel in the multi-stage hybrid liquid homogenizing assembly shown.

[0034] Figure 8 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application.

[0035] Figure 9 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 8

[0036] Figure 10 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application.

[0037] Figure 11 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application.

[0038] Figure 12 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application.

[0039] Figure 13 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 12

[0040] A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 14

[0041] A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 15

[0042] A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 16

[0043] A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 17 Figure 16 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application.

[0044] Figure 18 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 17

[0045] A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 19 Figure 1 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application.

[0046] Figure 20 A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 19

[0047] A schematic diagram of the structure of a multi-stage hybrid liquid homogenizing assembly provided by another embodiment of the present application. Figure 21 Figure 1 ​​​​A second sample structure of the multi-stage mixed liquid uniform assembly is shown in the structure diagram of the distributor.

[0048] Figure 22 A structure diagram of the control sample corresponding to the sample structure is shown. Figure 21 A structure diagram of the control sample corresponding to the sample structure is shown.

[0049] Figure 23 A structure diagram of the control sample corresponding to the sample structure is shown.

[0050] Figure 24 A structure diagram of the control sample corresponding to the sample structure is shown.

[0051] Figure 25 A structure diagram of the control sample corresponding to the sample structure is shown.

[0052] Figure 26 A structure diagram of the control sample corresponding to the sample structure is shown.

[0053] Figure 27 A structure diagram of the control sample corresponding to the sample structure is shown. Figure 26 A projection diagram of the control sample is shown.

[0054] Figure 28 A structure diagram of the control sample corresponding to the sample structure is shown. Figure 27 A cross-sectional diagram of the control sample along the B-B line is shown.

[0055] Figure 29 A structure diagram of the control sample corresponding to the sample structure is shown.

[0056] Figure 30 A cross-sectional diagram of the control sample is shown. Figure 29

[0057] A structure diagram of the control sample corresponding to the sample structure is shown. Figure 31

[0058] A cross-sectional diagram of the control sample is shown. Figure 32 Figure 31 A cross-sectional diagram of the control sample is shown.

[0059] Figure 33 Figure 32 An enlarged diagram of the control sample at C in the structure diagram is shown. DETAILED DESCRIPTION

[0060] Embodiment One

[0061] ​​To improve the dispensing performance of traditional distributors, the inventors proposed a distributor structure with a mixing chamber. When the dryness and mass flow rate of the input refrigerant are both high, the refrigerant exhibits a turbulent, slug-like flow. In this state, the refrigerant, after reflection by the mixing chamber, can form a stable, diffused mist flow, thus achieving uniform and stable dispensing performance. However, when the input refrigerant has a low dryness (e.g., dryness below 0.15) or a low mass flow rate (e.g., the mass flow rate distributed to each branch pipe is less than or equal to 40 kg / h), the refrigerant is close to a laminar flow. In this case, the refrigerant, after reflection by the mixing chamber, still struggles to form a mist flow, resulting in poor dispensing uniformity or stability. Dispensing stability refers to the distributor's ability to resist external interference (such as refrigerant mass flow rate, dryness, etc.).

[0062] In view of this, this embodiment provides a multi-stage mixing and equalization assembly for steadily improving the performance of a distributor, comprising a mixing chamber 1 and a counter-jet mixing component 2. The mixing chamber 1 has a mixing cavity 11. The counter-jet mixing component 2 includes multiple equalization plates arranged sequentially along the axial direction on the outer peripheral wall of the mixing chamber 1. Each equalization plate includes multiple refrigerant ports circumferentially distributed around the mixing chamber 1 and a solid portion located between adjacent refrigerant ports. Along the distributor axial direction, in two adjacent equalization plates, each solid portion of the upper equalization plate covers the corresponding refrigerant port on the lower equalization plate and overlaps with the projection of the solid portions on both sides of the corresponding refrigerant port on the lower equalization plate to form a set of counter-jet channels for refrigerant to flow in opposite directions. The refrigerant, after being reflected and mixed by the mixing cavity 11, enters the multiple sets of counter-jet channels in the counter-jet mixing component 2, and the refrigerant is mixed in each set of counter-jet channels.

[0063] like Figures 1 to 5 As shown, in this embodiment, the through-jet mixing component 2 includes two equalizing plates, namely a first equalizing plate 21 and a second equalizing plate 22. Divided along the refrigerant flow direction, the first equalizing plate 21 is the upper equalizing plate, and the second equalizing plate 22 is the lower equalizing plate. The first equalizing plate 21 has multiple refrigerant ports 211 and multiple solid portions 212 located between adjacent refrigerant ports; similarly, the second equalizing plate 22 has multiple refrigerant ports 221 and multiple solid portions 222 located between adjacent refrigerant ports. Specifically, the two equalizing plates are staggered, with the middle region of the solid portion 212 of the first equalizing plate covering the corresponding refrigerant port 221 on the second equalizing plate 22, and its two side regions overlapping the projection of the solid portion 222 of the second equalizing plate, thereby forming a first flow channel 201 and a second flow channel 202 to form a set of through-jet flow channels 200. The refrigerant flows in opposite directions within each set of through-jet flow channels to achieve through-jet mixing.

[0064] In this embodiment, each equalizing plate includes eight coolant ports and eight solid portions. Corresponding to the solid portions and the coolant ports on the equalizing plates, eight independent counter-flow channels 200 are formed between the two equalizing plates, and each of the eight counter-flow channels 200 includes a first flow channel 201 and a second flow channel 202. However, the present application is not limited to this. In other embodiments, the number of solid portions and the number of coolant ports on the equalizing plates can also be three, five, seven or other integers.

[0065] For each coolant port 211 on the first equalizing plate 21, it is connected to two groups of counter-flow channels located on both sides. Figure 6 The flow diagram of the coolant entering the counter-flow mixing device 2 is shown in the figure, and the arrows represent the flow direction, Figure 7 The flow diagram of the coolant in the counter-flow mixing device 2 during the CFD (Computational Fluid Dynamics) simulation analysis process is shown in the figure. For convenience of description, Figure 1 Figure 6 Figure 7 In the figures, the three adjacent coolant ports on the first equalizing plate 21 are defined as 211b, 211a and 211c. Taking the coolant port 211a on the first equalizing plate 21 in Figure 1 Figure 6 Figure 7 For example, the coolant port 211a on the first equalizing plate 21 has two adjacent coolant ports 211b and 211c. Part of the coolant input from the coolant port 211a flows into the first flow channel 201 of the counter-flow channel 200, and the other part of the coolant enters the second flow channel 202' of the counter-flow channel 200'. The coolant entering the first flow channel 201 is mixed with the coolant from the second flow channel 202 (from the coolant port 211b) in the counter-flow channel 200. Correspondingly, the coolant entering the second flow channel 202' is mixed with the coolant from the first flow channel 201' (from the coolant port 211c) in the other group of counter-flow channels 200'. In this way, on the first equalizing plate 21, the coolant input from the adjacent coolant ports 211 is mixed in the corresponding counter-flow channels and then output from the corresponding coolant ports on the second equalizing plate.

[0066] In the figure, Figure 7 In the figure, the high-speed jet of the coolant input from the coolant port 211a enters the first flow channel 201 and the second flow channel 202' on both sides (the flow rate of the coolant is represented by orange in the figure). The coolant entering the first flow channel 201 is mixed in the counter-flow channel 200, and the flow rate of the coolant gradually decreases in the circumferential direction (from orange to blue), and then the coolant is output from the coolant port on the second equalizing plate in the axial direction. Similarly, the coolant entering the second flow channel 202' is mixed in the counter-flow channel 200', and the flow rate of the coolant also gradually decreases in the circumferential direction. Figure 7 The change of the flow rate of the coolant in the figure reflects that in the multi-stage mixing type equalizing assembly provided in this embodiment, the input coolant is mixed in each counter-flow channel. ​​​​

[0067] In the multi-stage mixing liquid homogenizing assembly provided by the embodiment, the inner wall of the mixing chamber 11 reflects the refrigerant entering the distributor, and the refrigerant is initially dispersed into droplets. The reflected refrigerant and the subsequent input refrigerant form a vortex in the mixing chamber 11 to promote the mixing of the gas-liquid two-phase refrigerant, that is, to achieve the first-stage mixing of the refrigerant. For the refrigerant with low dryness or low mass flow, the input flow pattern is basically close to the laminar flow of gas-liquid two-phase separation. After the first-stage mixing in the mixing chamber 11, although part of the liquid film is dispersed into droplets, the liquid film is difficult to be fully dispersed due to the thick liquid film, and thus the flow pattern of the mixed refrigerant can only develop into a slug flow and cannot reach a dispersed mist flow. Then, the slug flow refrigerant enters the impingement mixing member 2. In the impingement mixing member 2, the refrigerant enters from the plurality of refrigerant ports 211 on the first liquid homogenizing plate 21, and after being throttled and accelerated to high-speed refrigerant, the refrigerant enters each group of impingement flow channels 200. In each group of impingement flow channels 200, the high-speed refrigerant flows in opposite directions, and after impingement, a turbulent flow is formed to enhance the degree of disorder of the two-phase flow so that the refrigerant gradually develops into a dispersed mist flow. In the embodiment, the plurality of groups of impingement flow channels 200 are independent of each other, and after the refrigerant with a slug flow is preliminarily disturbed in the mixing chamber 11, the refrigerant is divided into multiple flow paths when entering the impingement mixing member 2. The refrigerant in each flow path is impingement mixed (i.e., the second-stage mixing of the refrigerant) in the corresponding impingement flow channel 200 to form a dispersed mist flow, and then the refrigerant is uniformly and stably distributed.

[0068] In the existing reflective mixing type distributor (such as a baffle type or an impeller type), the intensity of the reflective mixing depends only on the kinetic energy of the incident refrigerant. In the embodiment, the intensity of the impingement mixing is related to the sum of the kinetic energy of the two refrigerants flowing in opposite directions. Obviously, under the same working conditions, the impingement mixing can more improve the degree of disorder of the two-phase flow, and then promote the full mixing of the gas-liquid two-phase refrigerant.

[0069] In the multi-stage mixing liquid homogenizing assembly provided by the embodiment, the mixing chamber 11 provides the first-stage mixing to disturb the stratified flow of the gas-liquid two-phase separation into a slug flow. The plurality of groups of impingement flow channels 200 between the first liquid homogenizing plate 21 and the second liquid homogenizing plate 22 in the impingement mixing member 2 provide the second-stage mixing to gradually develop the slug flow into a stable mist flow. The mixing chamber 11 and the impingement mixing member 2 are combined to form the multi-stage mixing of the refrigerant.

[0070] Although the embodiment takes the example that the impingement mixing member 2 includes two liquid homogenizing plates. However, the present application does not make any limitation in this regard. In other embodiments, for example, Figure 8 and Figure 9As shown, the through-jet mixing component 2 includes three equalizing plates: a first equalizing plate 21, a second equalizing plate 22, and a third equalizing plate 23. A primary through-jet mixing structure 200a is formed between the first equalizing plate 21 and the second equalizing plate 22, and this primary through-jet mixing structure 200a has multiple sets of primary through-jet flow channels. A secondary through-jet mixing structure 200b is formed between the second equalizing plate 22 and the third equalizing plate 23, and this secondary through-jet mixing structure 200b has multiple sets of secondary through-jet flow channels.

[0071] Similar to this embodiment, in the primary through-jet mixing structure 200a, the first liquid leveling plate 21 is the upper liquid leveling plate, and the second liquid leveling plate 22 is the lower liquid leveling plate. The refrigerant enters the multiple sets of through-jet flow channels 200 located between the two liquid leveling plates through multiple refrigerant ports 211 on the first liquid leveling plate 21. After through-jet mixing, it enters the multiple refrigerant ports 221 on the second liquid leveling plate 22, that is, it enters the secondary through-jet mixing structure 200b. In the secondary through-jet mixing structure 200b, the second liquid leveling plate 22 serves as the upper liquid leveling plate, and the third liquid leveling plate 23 serves as the lower liquid leveling plate. The middle region of the solid portion 222 on the second liquid leveling plate covers the corresponding refrigerant port 231 on the third liquid leveling plate 23, and its two side regions overlap with the projection of the solid portion 232 of the third liquid leveling plate, thereby forming multiple sets of secondary through-jet flow channels 200 including the first flow channel 201 and the second flow channel 202. The refrigerant enters multiple sets of opposing flow channels 200 through multiple refrigerant ports 221 on the second liquid distribution plate 22, and after being mixed by opposing flow, it is output from multiple refrigerant ports 231 on the third liquid distribution plate 23. This structure performs three-stage mixing of the refrigerant: primary mixing provided by the mixing chamber 11, secondary mixing provided by the primary opposing flow mixing structure 200a, and tertiary mixing provided by the tertiary opposing flow mixing structure 200b.

[0072] exist Figure 10 In this multi-stage mixing assembly 2, four liquid distribution plates are included: a first liquid distribution plate 21, a second liquid distribution plate 22, a third liquid distribution plate 23, and a fourth liquid distribution plate 24. Multiple sets of primary liquid distribution channels are formed between the first liquid distribution plate 21 and the second liquid distribution plate 22; multiple sets of secondary liquid distribution channels are formed between the second liquid distribution plate 22 and the third liquid distribution plate 23; and multiple sets of tertiary liquid distribution channels are formed between the third liquid distribution plate 23 and the fourth liquid distribution plate 24. This multi-stage mixing liquid distribution assembly performs four-stage mixing of the refrigerant: primary mixing provided by the mixing chamber 11 and tertiary liquid distribution mixing within the mixing assembly 2. Similarly, in other embodiments, the mixing assembly may include five or more liquid distribution plates.

[0073] However, the present invention does not limit this in any way. In other embodiments, the jet mixing component 2 may also include multiple equalization units, each equalization unit including at least two equalization plates and multiple sets of jet channels formed between adjacent equalization plates, but jet channels are not formed between adjacent equalization units. Figure 11As shown, the cross-flow mixing element 2 also includes four liquid equalizing plates, the first liquid equalizing plate 21 and the second liquid equalizing plate 22 form a first liquid equalizing unit 20_1, and there are multiple sets of cross-flow channels between the two. The third liquid equalizing plate 23 and the fourth liquid equalizing plate 24 form a second liquid equalizing unit 20_2, and there are also multiple sets of cross-flow channels between the two. However, the axial spacing between the solid portions of the two liquid equalizing plates adjacent to the first liquid equalizing unit 20_1 and the second liquid equalizing unit 20_2 (i.e., the second liquid equalizing plate 22 and the third liquid equalizing plate 23) is large (greater than the axial spacing H0 between the solid portions of the two adjacent liquid equalizing plates forming the cross-flow channels), so that no cross-flow channels are formed between the two liquid equalizing units. The cross-flow mixing element 2 of this structure has four liquid equalizing plates, but only performs two-stage cross-flow mixing on the refrigerant. Similarly, when there are five liquid equalizing plates, three adjacent liquid equalizing plates can be arranged to form a liquid equalizing unit with two-stage cross-flow mixing, and the other two liquid equalizing plates can form another liquid equalizing unit with one-stage cross-flow mixing. Similarly, no cross-flow channels are formed between adjacent liquid equalizing units. In other embodiments, when the number of liquid equalizing plates is six or more, the cross-flow mixing element can also include three or more liquid equalizing units.

[0074] Although this embodiment illustrates the principle of the multi-stage mixing type liquid equalizing assembly by improving the refrigerant distribution in the low dryness or low mass flow state. However, this is not to limit the multi-stage mixing type liquid equalizing assembly provided by the present application to only be applied to low dryness or low mass flow. The multi-stage mixing type liquid equalizing assembly provided by this embodiment can also be used in other scenarios with higher dryness or mass flow.

[0075] Figure 3 As shown Figure 1 The projection schematic view from the top view, where the adjacent red lines are the refrigerant ports 211 on the first liquid equalizing plate, the adjacent dashed lines are the refrigerant ports 221 on the second liquid equalizing plate, and the shaded part is the overlap area formed by the projection overlap of the solid portion 212 of the upper liquid equalizing plate (i.e., the first liquid equalizing plate 21) and the solid portion 222 of the lower liquid equalizing plate (i.e., the second liquid equalizing plate 22) on both sides of the corresponding refrigerant ports 221.

[0076] The minimum width L0 of each overlap region satisfies 0.5mm≤L0≤3.5mm. The lower limit of the minimum width L0 determines the size of the two side regions of the first liquid equalizing plate entity 212, ensuring that the first flow channel 201 and the second flow channel 202 have a certain circumferential length between the upper and lower liquid equalizing plates, providing space for the mixing of the refrigerant. Further, since the radial size of the liquid equalizing plate is limited by the inner cavity of the distributor, the outer diameter of the liquid equalizing plate is preferably substantially close to the inner cavity diameter of the distributor body. For a liquid equalizing plate of a certain size, the upper limit of the minimum width L0 is related not only to the circumferential size of the cross-flow channel 200, but also to the flow area of the refrigerant port 211 on the first liquid equalizing plate 21. The greater the upper limit of the minimum width L0, the greater the circumferential size of the cross-flow channel 200 and the smaller the flow area of the refrigerant port 211 on the first liquid equalizing plate, both of which increase the flow resistance of the refrigerant. Therefore, the upper limit of the minimum width L0 needs to be controlled to limit the pressure loss caused by the mixing of the refrigerant, so as to avoid affecting the performance of the refrigeration system unit due to excessive pressure loss of the refrigerant. Preferably, the minimum width L0 of the overlap region is set to 1.5mm. However, the present application does not make any limitation in this regard. In other embodiments, the minimum width L0 of the overlap region can also be 0.8mm, 1.13mm, 1.3mm, 1.83mm, 2mm, 2.25mm, 2.5mm, 3.0mm, etc.

[0077] In this embodiment, the first liquid equalizing plate refrigerant port 211 and the second liquid equalizing plate refrigerant port 221 are both notch slots extending continuously to the edge of the liquid equalizing plate in the radial direction, and the shape of the notch slot is a sector. Correspondingly, the first liquid equalizing plate entity 212 and the second liquid equalizing plate entity 222 are also sector-shaped. The minimum width L0 of the overlap region is the width of the overlap region near the center of the liquid equalizing plate. However, the shape of the refrigerant port of the present application is not limited in this regard. In other embodiments, the refrigerant port can also be a rectangular notch slot or a curved and irregular notch slot. In other embodiments, the refrigerant port can also be a hole, such as one or a combination of through holes, flanged holes, or arc bubble holes, and the outline of the hole-shaped refrigerant port can be circular, elliptical, or sector-shaped, etc. Specifically, as shown in Figure 12 and Figure 13 the first liquid equalizing plate refrigerant port 211 and the second liquid equalizing plate refrigerant port 221 are both through holes. As shown in Figure 14 the first liquid equalizing plate refrigerant port 211 and the second liquid equalizing plate refrigerant port 221 are both flanged holes.

[0078] Although this embodiment takes the structure of two adjacent liquid equalizing plates being the same and the refrigerant ports being sector-shaped notch slots as an example. However, the present application does not make any limitation in this regard. In other embodiments, the structures of the refrigerant ports of two adjacent liquid equalizing plates can also be different. As shown in Figure 15 the refrigerant port 211 on the first liquid equalizing plate 21 is a through hole, while the refrigerant port 221 on the second liquid equalizing plate 22 is a sector-shaped notch.

[0079] In the multi-stage mixing and equalization assembly provided in this embodiment, the high-speed jetting of the refrigerant within the jetting channel 200 is crucial for the refrigerant to evolve from a slug-like flow to a mist-like flow. The effectiveness of the jetting mixing is positively correlated with its flow velocity (i.e., the higher the flow velocity, the better the jetting mixing effect). During the refrigerant's flow, its flow velocity is inevitably affected by factors such as flow resistance and volume changes. To improve the jetting mixing effect, this embodiment first throttles and accelerates the refrigerant through the refrigerant inlet 211 on the first equalization plate. Based on this, as... Figure 4 and Figure 5 As shown, by controlling the axial distance H0 between the first liquid equalization plate solid portion 212 and the second liquid equalization plate solid portion 222, the axial dimension of the jet channel 200 is limited, preventing the refrigerant from over-expanding due to excessive space within the jet channel 200, thus avoiding a decrease in flow velocity. In other words, controlling the axial distance H0 maintains or increases the refrigerant flow velocity within the jet channel 200 to enhance the jet mixing effect. Preferably, the axial distance H0 is set to 1.5 mm. However, the present invention does not limit this. In other embodiments, the axial distance H0 can also be other values ​​greater than 0 and less than or equal to 3 mm, such as 0.5 mm, 0.8 mm, 1.2 mm, 1.8 mm, 2.0 mm, 2.5 mm, etc.

[0080] In this embodiment, the first equalizing plate 21 and the second equalizing plate 22 are axially spaced on the outer peripheral wall of the mixing chamber 1, so that a flow channel gap 210 is formed between the solid portion 212 of the first equalizing plate and the solid portion 222 of the second equalizing plate. The axial dimension of the flow channel gap 210 is the axial distance H0. To facilitate precise control of the axial dimension H0 between adjacent equalizing plates during assembly, such as... Figure 5 As shown, the through-jet mixing component 2 also includes a limiting sleeve 25, which is fitted over the outer peripheral wall of the mixing chamber 1. The first liquid distribution plate 21 and the second liquid distribution plate 22 respectively abut against the two ends of the limiting sleeve to achieve an intermittent distribution. In this embodiment, the number of limiting sleeves 25 is one. However, the present invention does not limit this. In other embodiments, when the through-jet mixing component includes three or more intermittently distributed liquid distribution plates, the number of limiting sleeves is also multiple. In this embodiment, the limiting sleeve 25 and the two adjacent liquid distribution plates are separate structures. However, the present invention does not limit this. In other embodiments, the limiting sleeve can also be integrally formed with one of the liquid distribution plates. For example, it can be integrally formed on the first liquid distribution plate or integrally formed on the second liquid distribution plate using a stamping and flanging process.

[0081] In the embodiment, the first liquid uniformizing plate 21 and the second liquid uniformizing plate 22 are both of an integral structure, and each of the liquid uniformizing plates is formed with a connecting hole sleeved on the outer peripheral wall of the mixing cavity 1. However, the present application is not limited thereto. In other embodiments, the liquid uniformizing plate can also include a plurality of independent physical parts, and the plurality of physical parts are spaced apart along the circumference of the mixing cavity and fixed to the outer peripheral wall of the mixing cavity.

[0082] In the embodiment, the first liquid uniformizing plate 21 and the second liquid uniformizing plate 22 are both of a plate structure with both sides of the surface being close to a plane. However, the present application is not limited thereto. In other embodiments, the liquid uniformizing plate can also be of a plate structure with a convex ridge on the surface or other structures.

[0083] In the embodiment, the two liquid uniformizing plates are both connected to the outer peripheral wall of the mixing cavity 1 in a split type. However, the present application is not limited thereto. In other embodiments, the most upstream liquid uniformizing plate (i.e. the first liquid uniformizing plate 21) can be integrally formed with the mixing cavity 1, as shown in Figure 16 . And the other liquid uniformizing plates (such as the second liquid uniformizing plate 22) are welded to the outer peripheral wall of the mixing cavity 1, as shown in Figure 17 and Figure 18 . However, the present application is not limited thereto. In other embodiments, the other liquid uniformizing plates (such as the second liquid uniformizing plate 22) can also be sequentially connected to the most upstream liquid uniformizing plate (i.e. the first liquid uniformizing plate 21).

[0084] In the embodiment, the mixing cavity 1 is a stretching cylinder, and the mixing cavity 11 is in a columnar shape. However, the present application is not limited thereto. In other embodiments, the mixing cavity can also be formed in a punching manner, and the profile thereof can also be one or a combination of a circular truncated cone, a circular cone, and a sphere.

[0085] To verify the performance of the multi-stage mixing type liquid uniformizing assembly 20 provided in the embodiment, the multi-stage mixing type liquid uniformizing assembly 20 is applied to two different types of distributors, and each of the distributors has a plurality of specifications. Under different dryness and input mass flow rates, the CFD (Computational Fluid Dynamics) simulation is used to analyze the distribution uniformity and stability of the distributor sample provided with the multi-stage mixing type liquid uniformizing assembly in the embodiment and the existing distributor sample with the same specification.

[0086] The software used in the CFD simulation analysis is the ANSYS software, and the conditions are set as shown below:

[0087] Turbulence model: Realizable k-ε model;

[0088] Mesh parameters: tetrahedral unstructured mesh is used;

[0089] Working condition: the working medium is R410A refrigerant, and the wall boundary is an adiabatic boundary.

[0090] Boundary conditions: Turbulence intensity 5%, other boundary conditions see the specific data table.

[0091] Evaluation parameters: STD and K. Wherein, STD refers to the standard deviation of the refrigerant mass flow rate at the outlet of each branch pipe, and K refers to the percentage of the standard deviation STD to the set distribution of the mass flow rate M out of each branch pipe.

[0092] The specific calculation formula of STD is as follows:

[0093]

[0094] Wherein, is the average value of the refrigerant mass flow rate at the outlet of all branch pipes, m j is the refrigerant mass flow rate at the outlet of the jth branch pipe, n is the number of branch pipes, and M out is the set distribution of the mass flow rate of each branch pipe.

[0095] Simulation analysis of the first sample structure:

[0096] Figure 19 The first sample structure of the distributor provided by the embodiment is shown, which has a multi-stage mixed liquid equalizing assembly 20 installed in the distributor body 10. Figure 20 The existing sample structure of the distributor corresponding to structure one (control sample structure) is shown, which is a refrigeration distributor with a mixing chamber proposed by the inventor in Chinese patent CN216204506U.

[0097] 【1】Analysis of the sample and the control sample under different dryness fractions to analyze the distribution uniformity and stability.

[0098] Sample selection: According to the specifications of the distributor body 10, the specifications of the liquid inlet pipe 40, the number n of branch pipes 30, and the specifications of the branch pipes 30, six samples and corresponding six control samples are selected. Each sample and the corresponding control sample is simulated and analyzed under a dryness fraction of 0, 0.1, 0.15, 0.2, 0.25, 0.3, and 0.35.

[0099] Common parameters of the sample and the corresponding control sample in the first dryness fraction analysis group: the outer diameter D0 of the body is 45 mm, the outer diameter D1 of the main body segment of the liquid inlet pipe is 12.7 mm, the number n of branch pipes is 17, the outer diameter D2 of the branch pipe is 3 mm; the set input total mass flow rate M in is 595 Kg / h, and the set distribution of the mass flow rate M out of each branch pipe is 35 Kg / h.

[0100] Common parameters of sample and control sample in the 2nd degree analysis group: body outer diameter D0 = 45 mm, main body section outer diameter D1 = 16 mm, branch pipe number n = 17, branch pipe outer diameter D2 = 3.4 mm; set input total mass flow rate M in = 935 Kg / h, set mass flow rate M out = 55 Kg / h distributed to each branch pipe.

[0101] Common parameters of sample and control sample in the 3rd degree analysis group: body outer diameter D0 = 45 mm, main body section outer diameter D1 = 16 mm, branch pipe number n = 15, branch pipe outer diameter D2 = 3.8 mm; set input total mass flow rate M in = 1050 Kg / h, set mass flow rate M out = 70 Kg / h distributed to each branch pipe.

[0102] Common parameters of sample and control sample in the 4th degree analysis group: body outer diameter D0 = 72 mm, main body section outer diameter D1 = 22 mm, branch pipe number n = 31, branch pipe outer diameter D2 = 3.0 mm; set input total mass flow rate M in = 1085 Kg / h, set mass flow rate M out = 35 Kg / h distributed to each branch pipe.

[0103] Common parameters of sample and control sample in the 5th degree analysis group: body outer diameter D0 = 72 mm, main body section outer diameter D1 = 22 mm, branch pipe number n = 30, branch pipe outer diameter D2 = 3.4 mm; set input total mass flow rate M in = 1650 Kg / h, set mass flow rate M out = 55 Kg / h distributed to each branch pipe.

[0104] Common parameters of sample and control sample in the 6th degree analysis group: body outer diameter D0 = 72 mm, main body section outer diameter D1 = 22 mm, branch pipe number n = 27, branch pipe outer diameter D2 = 3.8 mm; set input total mass flow rate M in = 1890 Kg / h, set mass flow rate M out = 70 Kg / h distributed to each branch pipe.

[0105] The 42 groups of data in the above 6 groups of dryness analysis are summarized in Table 1 and analyzed to obtain: in each group of dryness analysis, regardless of the change of dryness, the STD value and K value of each sample are less than the STD value and K value of the corresponding control sample, i.e. the dispensing uniformity of each sample is better than that of the corresponding control sample. Further, it can be found in the 6 groups of dryness analysis that the K value of all samples is distributed between 1.95% and 3.03%, while the K value of all control samples is distributed between 3.51% and 4.65%. Obviously, the K value distribution range of the sample provided in the embodiment will be narrower; in other words, it has more excellent dispensing stability under different specifications and different dryness conditions. It can be obtained that: under different dryness conditions (including low dryness conditions with dryness less than 0.15), the sample structure with the multi-stage mixed liquid distribution assembly 20 shown in the embodiment is better than the control sample structure shown in Figure 19 in terms of dispensing uniformity and dispensing stability. Figure 20

[0106] 【2】Analysis of the dispensing uniformity and stability of the sample and the control sample under different mass flow rates.

[0107] Sample selection: 7 samples and 7 corresponding control samples are selected according to the specification of the liquid distributor body 10, the specification of the liquid inlet pipe 40, the number n of branch pipes 30 and the specification of the branch pipes 30, and two different input mass flow rates are analyzed for each sample.

[0108] Common parameters of the sample and the corresponding control sample in the first mass flow rate analysis group: body outer diameter D0 = 24 mm, liquid inlet pipe body segment outer diameter D1 = 6.35 mm, branch pipe number n = 2, branch pipe outer diameter D2 = 3 mm, dryness is 0.35.

[0109] Common parameters of the sample and the corresponding control sample in the second mass flow rate analysis group: body outer diameter D0 = 24 mm, liquid inlet pipe body segment outer diameter D1 = 6.35 mm, branch pipe number n = 3, branch pipe outer diameter D2 = 3 mm, dryness is 0.35.

[0110] Common parameters of the sample and the corresponding control sample in the third mass flow rate analysis group: body outer diameter D0 = 24 mm, liquid inlet pipe body segment outer diameter D1 = 6.35 mm, branch pipe number n = 5, branch pipe outer diameter D2 = 3 mm, dryness is 0.35.

[0111] Common parameters of the sample and the corresponding control sample in the fourth mass flow rate analysis group: body outer diameter D0 = 30 mm, liquid inlet pipe body segment outer diameter D1 = 9.52 mm, branch pipe number n = 3, branch pipe outer diameter D2 = 3 mm, dryness is 0.35.

[0112] ​Common parameters of the sample and the corresponding control sample in the 5th mass flow analysis group: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 9.52 mm, the number of branch pipes n = 5, the outer diameter of the branch pipes D2 = 3 mm, and the dryness is 0.35.

[0113] Common parameters of the sample and the corresponding control sample in the 6th mass flow analysis group: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 9.52 mm, the number of branch pipes n = 7, the outer diameter of the branch pipes D2 = 3 mm, and the dryness is 0.35.

[0114] Common parameters of the sample and the corresponding control sample in the 7th mass flow analysis group: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 9.52 mm, the number of branch pipes n = 10, the outer diameter of the branch pipes D2 = 3 mm, and the dryness is 0.35.

[0115] In the above 7 mass flow analysis groups, the mass flow M of each sample allocated to each branch pipe out is less than or equal to 40 Kg / h, that is, it is in a low mass flow scenario. The 14 groups of data of the above 7 mass flow analysis groups are summarized in Table 2, and after analysis, it can be obtained that in the low mass flow scenario, the STD value and the K value of each sample are less than those of the corresponding control sample, that is, the distribution uniformity of each sample is better than that of the corresponding control sample. Further, by observing the K values of all samples in the 7 mass flow analysis groups, it is found that the K values are distributed between 1.8% and 3.49%, while the K values of all control samples are distributed between 3.53% and 9.51%. Therefore, it can be obtained that in the low mass flow scenario, the sample structure of the distributor provided in the embodiment Figure 19 has the multi-stage mixed liquid distribution assembly 20, and the sample structure of the distributor provided in the embodiment Figure 20 has the control sample structure.

[0116] Table 3 is the simulation analysis data under a large mass flow, and from Table 3, it can be obtained that in the large mass flow scenario, the sample structure of the distributor provided in the embodiment Figure 19 has the multi-stage mixed liquid distribution assembly 20, and the sample structure of the distributor provided in the embodiment Figure 20 has the control sample structure.

[0117] The above simulation analysis verifies that the multi-stage mixed liquid distribution assembly 20 provided in the embodiment has excellent distribution uniformity and stability in each application scenario in the first sample structure of the distributor. In order to further verify the compatibility of the multi-stage mixed liquid distribution assembly 20, it is applied to the second sample structure of the distributor and simulation analysis is carried out under different dryness and different input mass flow.

[0118] Simulation analysis of the second sample structure:

[0119] As Figure 21 shown, the second liquid distributor sample structure includes a liquid distributor body 10 and a multi-stage mixed liquid equalization assembly 20, a jet plate 50 and a reflective mixed flow guide plate 60 arranged in the liquid distributor body 10 in sequence. The corresponding control sample structure is the pre-flow regulating distributor proposed by the inventor in Chinese Patent CN118882244A, as Figure 22 shown.

[0120] 【1】Analyze the liquid distribution uniformity and stability of the samples and the control samples at different dryness levels.

[0121] Sample selection: Select 6 samples and corresponding 6 control samples according to the specifications of the liquid distributor body 10, the specifications of the liquid inlet pipe 40, the number n of branch pipes 30 and the specifications of the branch pipes 30, and simulate and analyze each sample and the corresponding control sample at a dryness level of 0, 0.1, 0.15, 0.2, 0.25, 0.3, 0.35, respectively.

[0122] Common parameters of the samples and the corresponding control samples in the first dryness analysis group: body outer diameter D0 = 45 mm, liquid inlet pipe body segment outer diameter D1 = 12.7 mm, branch pipe number n = 17, branch pipe outer diameter D2 = 3 mm; set the total input mass flow rate M in = 595 Kg / h, and set the mass flow rate M out distributed to each branch pipe = 35 Kg / h.

[0123] Common parameters of the samples and the corresponding control samples in the second dryness analysis group: body outer diameter D0 = 45 mm, liquid inlet pipe body segment outer diameter D1 = 16 mm, branch pipe number n = 17, branch pipe outer diameter D2 = 3.4 mm; set the total input mass flow rate M in = 935 Kg / h, and set the mass flow rate M out distributed to each branch pipe = 55 Kg / h.

[0124] Common parameters of the samples and the corresponding control samples in the third dryness analysis group: body outer diameter D0 = 45 mm, liquid inlet pipe body segment outer diameter D1 = 16 mm, branch pipe number n = 15, branch pipe outer diameter D2 = 3.8 mm; set the total input mass flow rate M in = 1050 Kg / h, and set the mass flow rate M out distributed to each branch pipe = 70 Kg / h.

[0125] Common parameters of the samples and the corresponding control samples in the fourth dryness analysis group: body outer diameter D0 = 63.5 mm, liquid inlet pipe body segment outer diameter D1 = 16 mm, branch pipe number n = 27, branch pipe outer diameter D2 = 3.0 mm; set the total input mass flow rate M in = 945 Kg / h, and set the mass flow rate Mout = 35 Kg / h.

[0126] Common parameters of the sample and the corresponding control sample in the 5th dryness analysis group: the outer diameter of the main body D0 = 63.5 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 22 mm, the number of branch pipes n = 26, the outer diameter of the branch pipe D2 = 3.4 mm; the set total mass flow rate M in 0 = 1430 Kg / h, the set mass flow rate M out = 55 Kg / h.

[0127] Common parameters of the sample and the corresponding control sample in the 6th dryness analysis group: the outer diameter of the main body D0 = 63.5 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 22 mm, the number of branch pipes n = 24, the outer diameter of the branch pipe D2 = 3.8 mm; the set total mass flow rate M in = 1680 Kg / h, the set mass flow rate M out = 70 Kg / h.

[0128] The data of the above samples and the corresponding control samples are summarized in Table 4, and after analysis, it is obtained that in each dryness analysis group, the STD and K value of each sample at different dryness are still less than those of the corresponding control sample. After observing the data of the 6th dryness analysis group, it is still obtained that the K distribution of the sample is more concentrated, and the distribution range is 2.36% to 3.49%, while the K value distribution range of the control sample is 3.56% to 4.95%. Thus, it is obtained that under different dryness, the second liquid distributor sample structure provided in the embodiment Figure 21 is superior to the control sample structure shown in the embodiment Figure 22 in terms of liquid distribution uniformity and stability.

[0129] 【2】Analysis of liquid distribution uniformity and stability of the sample and the control sample under different mass flow rates.

[0130] Sample selection: 7 samples and 7 corresponding control samples are selected according to the specification of the liquid distributor main body 10, the specification of the liquid inlet pipe 40, the number n of branch pipes 30 and the specification of the branch pipe 30, and each sample is analyzed under two input mass flow rates.

[0131] Common parameters of the sample and the corresponding control sample in the 1st mass flow rate analysis group: the outer diameter of the main body D0 = 24 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 6.35 mm, the number of branch pipes n = 2, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0132] Common parameters of the sample and the corresponding control sample in the 2nd mass flow rate analysis group: the outer diameter of the main body D0 = 24 mm, the outer diameter of the main body section of the liquid inlet pipe D1 = 6.35 mm, the number of branch pipes n = 3, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0133] Common parameters of samples and corresponding control samples in the 3rd mass flow analysis group: bulk outer diameter D0 = 24 mm, main section outer diameter D1 = 6.35 mm, number of branch pipes n = 5, branch pipe outer diameter D2 = 3 mm, dryness = 0.35.

[0134] Common parameters of samples and corresponding control samples in the 4th mass flow analysis group: bulk outer diameter D0 = 30 mm, main section outer diameter D1 = 9.52 mm, number of branch pipes n = 3, branch pipe outer diameter D2 = 3 mm, dryness = 0.35.

[0135] Common parameters of samples and corresponding control samples in the 5th mass flow analysis group: bulk outer diameter D0 = 30 mm, main section outer diameter D1 = 9.52 mm, number of branch pipes n = 5, branch pipe outer diameter D2 = 3 mm, dryness = 0.35.

[0136] Common parameters of samples and corresponding control samples in the 6th mass flow analysis group: bulk outer diameter D0 = 30 mm, main section outer diameter D1 = 9.52 mm, number of branch pipes n = 7, branch pipe outer diameter D2 = 3 mm, dryness = 0.35.

[0137] Common parameters of samples and corresponding control samples in the 7th mass flow analysis group: bulk outer diameter D0 = 30 mm, main section outer diameter D1 = 9.52 mm, number of branch pipes n = 10, branch pipe outer diameter D2 = 3 mm, dryness = 0.35.

[0138] In the above 7 mass flow analysis groups, each sample is allocated to each branch pipe mass flow M out is less than or equal to 40 Kg / h, i.e. is in a low mass flow scenario. After summarizing the 14 groups of simulation data in the above 7 mass flow analysis groups, Table V is formed.

[0139] From the analysis of the data in Table V, it can be obtained that under the low mass flow, the STD value and K value of each sample are less than the STD value and K value of the corresponding control sample. Thus, it can be obtained that under the low mass flow, the liquid distribution uniformity of each sample is superior to that of the corresponding control sample. Further, from the K values of all samples and control samples in the mass flow analysis groups, it is found that the K values of the samples are more concentrated, which are distributed between 0.88% and 3.38%, while the K values of the control samples are distributed between 3.62% and 7.89%. Thus, it can be obtained that under the low mass flow scenario, the liquid distribution uniformity and stability of the sample structure of the liquid distributor with the multi-stage mixed liquid distribution assembly 20 provided in the embodiment are superior to those of the control sample structure shown in Figure 21 . Figure 22 .

[0140] Table VI is simulation analysis data under the condition of low dryness and large mass flow rate. From Table VI, it can be seen that under the condition of low dryness and large mass flow rate, the second sample structure of the distributor provided in the embodiment has extremely excellent liquid distribution performance (including liquid distribution uniformity and stability), and the performance is far superior to that of the corresponding control sample structure. Figure 21 The sample structure of the distributor provided in the embodiment has excellent liquid distribution performance (including liquid distribution uniformity and stability) under different dryness and different mass flow rates, and the performance is far superior to that of the corresponding control sample structure. Figure 22 The sample structure of the distributor provided in the embodiment has excellent liquid distribution performance (including liquid distribution uniformity and stability) under different dryness and different mass flow rates, and the performance is far superior to that of the corresponding control sample structure.

[0141] As described above, the second sample structure of the distributor provided in the embodiment has excellent liquid distribution performance (including liquid distribution uniformity and stability) under different dryness and different mass flow rates, and the performance is far superior to that of the corresponding control sample structure. Figure 21 The CFD simulation analysis of the two sample structures of the distributor verifies that the multi-stage mixed liquid distribution assembly provided in the embodiment can greatly improve the performance of the distributor and solve the problem that the existing distributor is difficult to uniformly distribute liquid under the condition of low dryness or low mass flow rate. Figure 22 Corresponding to the multi-stage mixed liquid distribution assembly 20 described above, the embodiment also provides a distributor, which includes the multi-stage mixed liquid distribution assembly 20 described above, the mixing cavity 1 of the multi-stage mixed liquid distribution assembly 20 is substantially coaxial with the body 10 of the distributor, and the edges of the first liquid distribution plate 21 and the second liquid distribution plate 22 are substantially abutted with the inner circumferential wall of the body 10 of the distributor. Specifically, the distributor can be the first sample structure of the distributor as shown in

[0142] The second sample structure of the distributor as shown in Figure 19 The second sample structure of the distributor as shown in Figure 21 The second sample structure of the distributor as shown in Figure 21 The second sample structure of the distributor as shown in Figure 23 The second sample structure of the distributor as shown in The second sample structure of the distributor as shown in

[0143] The second sample structure of the distributor as shown in Figure 24 The second sample structure of the distributor as shown in Figure 25 The second sample structure of the distributor as shown in Figure 24 The second sample structure of the distributor as shown in Figure 21 The second sample structure of the distributor as shown in Figure 24In the embodiment, the multi-stage mixed liquid equalizing assembly 20 includes four liquid equalizing plates, i.e., a first liquid equalizing plate 21, a second liquid equalizing plate 22, a third liquid equalizing plate 23, and a fourth liquid equalizing plate 24. The first liquid equalizing plate 21 and the second liquid equalizing plate 22 form a first liquid equalizing unit 20_1, and a plurality of pairs of jet channels are formed between the first liquid equalizing plate 21 and the second liquid equalizing plate 22. The third liquid equalizing plate 23 and the fourth liquid equalizing plate 24 form a second liquid equalizing unit 20_2, and a plurality of pairs of jet channels are also formed between the third liquid equalizing plate 23 and the fourth liquid equalizing plate 24. However, no pair of jet channels is formed between the second liquid equalizing plate 22 and the third liquid equalizing plate 23, and the axial spacing between the solid portions of the second liquid equalizing plate 22 and the third liquid equalizing plate 23 is relatively large (larger than the axial spacing H0 between the solid portions of the adjacent liquid equalizing plates). However, the present application is not limited in this regard. In other embodiments, the axial spacing between the solid portions of the second liquid equalizing plate and the third liquid equalizing plate can be controlled to form three pairs of jet channels between the four liquid equalizing plates.

[0144] In Figure 25 In the embodiment, the multi-stage mixed liquid equalizing assembly 20 includes four liquid equalizing plates, i.e., a first liquid equalizing plate 21, a second liquid equalizing plate 22, a third liquid equalizing plate 23, and a fourth liquid equalizing plate 24. The first liquid equalizing plate 21 and the second liquid equalizing plate 22 form a first liquid equalizing unit 20_1, and a plurality of pairs of jet channels are formed between the first liquid equalizing plate 21 and the second liquid equalizing plate 22. The third liquid equalizing plate 23 and the fourth liquid equalizing plate 24 form a second liquid equalizing unit 20_2, and a plurality of pairs of jet channels are also formed between the third liquid equalizing plate 23 and the fourth liquid equalizing plate 24. However, no pair of jet channels is formed between the second liquid equalizing plate 22 and the third liquid equalizing plate 23, and the axial spacing between the solid portions of the second liquid equalizing plate 22 and the third liquid equalizing plate 23 is relatively large (larger than the axial spacing H0 between the solid portions of the adjacent liquid equalizing plates). However, the present application is not limited in this regard. In other embodiments, the axial spacing between the solid portions of the second liquid equalizing plate and the third liquid equalizing plate can be controlled to form three pairs of jet channels between the four liquid equalizing plates.

[0145] Correspondingly, the embodiment also provides a refrigeration system including the above-mentioned distributor and / or multi-stage mixed liquid equalizing assembly.

[0146] Embodiment Two

[0147] The embodiment is basically the same as Embodiment One and its variations, except that in the multi-stage mixed liquid equalizing assembly 20, the connection modes between the adjacent liquid equalizing plates are different. In the embodiment, the plurality of liquid equalizing plates are sequentially abutted, and the solid portions of the adjacent liquid equalizing plates have a flow channel gap 210 therebetween.

[0148] Specifically, as Figure 26 , Figure 27 and Figure 28As shown, the first liquid uniformizing plate 21 further comprises a middle portion 213 located at the outer periphery of the mixing cavity 1, and a plurality of solid portions 212 are distributed circumferentially around the middle portion 213. Similarly, the second liquid uniformizing plate 22 further comprises a middle portion 223 located at the outer periphery of the mixing cavity 1, and a plurality of solid portions 222 are distributed circumferentially around the middle portion 223. The middle portions 213, 223 of the two liquid uniformizing plates are both relatively protruding and connected to each other, so that the flow channel gaps 210 are formed between the solid portions 212 of the first liquid uniformizing plate and the solid portions 222 of the second liquid uniformizing plate. In this structure, the two liquid uniformizing plates are completely identical in structure, and only the direction and angle of one of the liquid uniformizing plates need to be adjusted during assembly. However, the present application does not make any limitation in this regard. In other embodiments, only the middle portion of one of the liquid uniformizing plates can be protruding, and the middle portion of the other liquid uniformizing plate can be a flat surface.

[0149] In other embodiments, if the number of liquid uniformizing plates is three, the second liquid uniformizing plate located in the middle can also be provided in a flat plate structure with the two side surfaces being close to flat surfaces, and the middle portions of the first liquid uniformizing plate and the third liquid uniformizing plate are both protruding towards the second liquid uniformizing plate and connected to the second liquid uniformizing plate, so that the flow channel gaps are formed between the solid portions of the adjacent liquid uniformizing plates.

[0150] Figure 29 and Figure 30 As shown, the first liquid uniformizing plate 21 further comprises a middle portion 213 located at the outer periphery of the mixing cavity 1, and a plurality of solid portions 212 are distributed circumferentially around the middle portion 213. Similarly, the second liquid uniformizing plate 22 further comprises a middle portion 223 located at the outer periphery of the mixing cavity 1, and a plurality of solid portions 222 are distributed circumferentially around the middle portion 223. The middle portions 213, 223 of the two liquid uniformizing plates are both relatively protruding and connected to each other, so that the flow channel gaps 210 are formed between the solid portions 212 of the first liquid uniformizing plate and the solid portions 222 of the second liquid uniformizing plate. In this structure, the two liquid uniformizing plates are completely identical in structure, and only the direction and angle of one of the liquid uniformizing plates need to be adjusted during assembly. However, the present application does not make any limitation in this regard. In other embodiments, only the middle portion of one of the liquid uniformizing plates can be protruding, and the middle portion of the other liquid uniformizing plate can be a flat surface.

[0151] Figure 31 、 Figure 32 and Figure 33 As shown, the first liquid uniformizing plate 21 further comprises a middle portion 213 located at the outer periphery of the mixing cavity 1, and a plurality of solid portions 212 are distributed circumferentially around the middle portion 213. Similarly, the second liquid uniformizing plate 22 further comprises a middle portion 223 located at the outer periphery of the mixing cavity 1, and a plurality of solid portions 222 are distributed circumferentially around the middle portion 223. The middle portions 213, 223 of the two liquid uniformizing plates are both relatively protruding and connected to each other, so that the flow channel gaps 210 are formed between the solid portions 212 of the first liquid uniformizing plate and the solid portions 222 of the second liquid uniformizing plate. In this structure, the two liquid uniformizing plates are completely identical in structure, and only the direction and angle of one of the liquid uniformizing plates need to be adjusted during assembly. However, the present application does not make any limitation in this regard. In other embodiments, only the middle portion of one of the liquid uniformizing plates can be protruding, and the middle portion of the other liquid uniformizing plate can be a flat surface.

[0152] In summary, the multi-stage mixed liquid uniform assembly provided by the application realizes multi-stage mixing of refrigerant through a mixing cavity and a pair of mixing elements. The mixing cavity reflects the input laminar refrigerant, disperses the liquid film into droplets to promote gas-liquid two-phase mixing, and then develops the refrigerant into a dispersed mist flow. The mixed refrigerant is reflected into the pair of mixing elements, and at least one pair of mixing is performed between the multiple liquid uniform plates. The adjacent liquid uniform plates in the pair of mixing elements are configured as follows: each solid part of the upper liquid uniform plate not only covers the corresponding refrigerant port on the lower liquid uniform plate, but also overlaps with the projection of the solid part on both sides of the refrigerant port, so as to form a group of pair of flow channels with opposite flow directions in the two overlapping areas. The mixed refrigerant is throttled and accelerated through the refrigerant port, and then enters the multiple groups of pair of flow channels between the adjacent liquid uniform plates. The high-speed refrigerant with opposite flow directions in each group of pair of flow channels collides and forms a turbulent flow, which enhances the turbulence degree of the two-phase flow, so as to develop the two-phase flow into a stable dispersed mist flow, and then greatly improves the distribution uniformity and stability of the two-phase refrigerant.

[0153] Further, by controlling the axial spacing between the solid parts of the adjacent liquid uniform plates, the collision mixing space is provided for the refrigerant in the pair of flow channels, while avoiding the expansion of the refrigerant due to the excessively large flow channel, ensuring the continuous high-speed convection of the refrigerant, and improving the effect of the pair of mixing.

[0154] Although the present application has been disclosed by the preferred embodiments as above, it is not intended to limit the present application, and any person skilled in the art can make some changes and modifications without departing from the spirit and scope of the present application, so the protection scope of the present application shall be subject to the scope claimed by the claims.

[0155] Table I

[0156]

[0157] Table II

[0158]

[0159] Table III

[0160]

[0161] Table IV

[0162]

[0163] Table V

[0164]

[0165] Table VI

[0166]

Claims

1. A multi-stage hybrid liquid homogenizing assembly, characterized by, A multi-stage mixed liquid distribution assembly is provided, comprising: a mixing cavity having a mixing chamber; a pair of opposed flow mixing element comprising a plurality of liquid distribution plates arranged along an axis of the mixing cavity in sequence, each liquid distribution plate comprising a plurality of refrigerant ports arranged circumferentially around the mixing cavity and a solid portion between adjacent refrigerant ports; along the axis of the mixing cavity, each solid portion of an upper liquid distribution plate covers a corresponding refrigerant port of a lower liquid distribution plate and overlaps with the projections of the solid portions on both sides of the corresponding refrigerant port of the lower liquid distribution plate to form a group of pair of opposed flow channels for the mixed refrigerant to flow in opposite directions, the mixed refrigerant enters the pair of opposed flow mixing element through the mixing chamber and is mixed in each group of pair of opposed flow channels.

2. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The minimum width L0 of each overlap region formed by the overlap of the solid portion of the upper liquid distribution plate and the projections of the solid portions on both sides of the corresponding refrigerant port of the lower liquid distribution plate satisfies 0.5mm≤L0≤3.5mm.

3. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The axial distance H0 between the solid portions of adjacent liquid distribution plates satisfies 0<H0≤3mm.

4. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The liquid distribution plates are arranged in sequence and abut each other locally, and the solid portions of adjacent liquid distribution plates are separated by a flow channel gap. Alternatively, the liquid distribution plates are arranged in sequence along the axis of the mixing cavity and are separated by a flow channel gap.

5. The multi-stage hybrid liquid homogenizing assembly of claim 4, wherein, The pair of opposed flow mixing element further comprises a limiting sleeve sleeved on the outer wall of the mixing cavity, and the ends of adjacent liquid distribution plates abut the limiting sleeve to be arranged in sequence.

6. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The liquid distribution plate is of an integral structure, and a connecting hole is formed in the middle of the liquid distribution plate to be sleeved on the outer wall of the mixing cavity. Alternatively, the liquid distribution plate comprises a plurality of independent solid portions, and the plurality of solid portions are arranged in sequence and fixed on the outer wall of the mixing cavity.

7. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The most upstream liquid distribution plate is integrally formed with the mixing cavity, and the other liquid distribution plates are connected to the outer wall of the mixing cavity or are sequentially connected to the most upstream liquid distribution plate.

8. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The refrigerant port is a notch slot continuously extending to the edge of the liquid distribution plate in the radial direction of the liquid distribution plate, and the notch slot is a fan-shaped, rectangular, or a slot with a curved wall.

9. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The refrigerant port is one or a combination of through holes, flanged holes, or arc bubble holes.

10. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The pair of opposed flow mixing element comprises three or more liquid distribution plates, and a plurality of groups of pair of opposed flow channels are formed between adjacent liquid distribution plates, and the refrigerant is mixed in two or more stages in the pair of opposed flow mixing element.

11. The multi-stage hybrid liquid homogenizing assembly of claim 1, wherein, The pair of opposed flow mixing element comprises a plurality of liquid distribution units, each liquid distribution unit comprises at least two liquid distribution plates and a plurality of groups of pair of opposed flow channels are formed between adjacent liquid distribution plates, and no pair of opposed flow channels are formed between adjacent liquid distribution units.

12. A liquid separator, characterized by A multi-stage mixed liquid distribution assembly is provided, comprising: a mixing cavity having a mixing chamber; a pair of opposed flow mixing element comprising a plurality of liquid distribution plates arranged along an axis of the mixing cavity in sequence, each liquid distribution plate comprising a plurality of refrigerant ports arranged circumferentially around the mixing cavity and a solid portion between adjacent refrigerant ports; 13. A refrigeration system characterized by, along the axis of the mixing cavity, each solid portion of an upper liquid distribution plate covers a corresponding refrigerant port of a lower liquid distribution plate and overlaps with the projections of the solid portions on both sides of the corresponding refrigerant port of the lower liquid distribution plate to form a group of pair of opposed flow channels for the mixed refrigerant to flow in opposite directions, the mixed refrigerant enters the pair of opposed flow mixing element through the mixing chamber and is mixed in each group of pair of opposed flow channels. The minimum width L0 of each overlap region formed by the overlap of the solid portion of the upper liquid distribution plate and the projections of the solid portions on both sides of the corresponding refrigerant port of the lower liquid distribution plate satisfies 0.5mm≤L0≤3.5mm. The axial distance H0 between the solid portions of adjacent liquid distribution plates satisfies 0<H0≤3mm. The liquid distribution plates are arranged in sequence and abut each other locally, and the solid portions of adjacent liquid distribution plates are separated by a flow channel gap. Alternatively, the liquid distribution plates are arranged in sequence along the axis of the mixing cavity and are separated by a flow channel gap. The pair of opposed flow mixing element further comprises a limiting sleeve sleeved on the outer wall of the mixing cavity, and the ends of adjacent liquid distribution plates abut the limiting sleeve to be arranged in sequence. The liquid distribution plate is of an integral structure, and a connecting hole is formed in the middle of the liquid distribution plate to be sleeved on the outer wall of the mixing cavity. Alternatively, the liquid distribution plate comprises a plurality of independent solid portions, and the plurality of solid portions are arranged in sequence and fixed on the outer wall of the mixing cavity. The most upstream liquid distribution plate is integrally formed with the mixing cavity, and the other liquid distribution plates are connected to the outer wall of the mixing cavity or are sequentially connected to the most upstream liquid distribution plate. The refrigerant port is a notch slot continuously extending to the edge of the liquid distribution plate in the radial direction of the liquid distribution plate, and the notch slot is a fan-shaped, rectangular, or a slot with a curved wall. The refrigerant port is one or a combination of through holes, flanged holes, or arc bubble holes. The pair of opposed flow mixing element comprises three or more liquid distribution plates, and a plurality of groups of pair of opposed flow channels are formed between adjacent liquid distribution plates, and the refrigerant is mixed in two or more stages in the pair of opposed flow mixing element. The pair of opposed flow mixing element comprises a plurality of liquid distribution units, each liquid distribution unit comprises at least two liquid distribution plates and a plurality of groups of pair of opposed flow channels are formed between adjacent liquid distribution plates, and no pair of opposed flow channels are formed between adjacent liquid distribution units. A multi-stage mixed liquid distribution assembly is provided, comprising: a mixing cavity having a mixing chamber; a pair of opposed flow mixing element comprising a plurality of liquid distribution plates arranged along an axis of the mixing cavity in sequence, each liquid distribution plate comprising a plurality of refrigerant ports arranged circumferentially around the mixing cavity and a solid portion between adjacent refrigerant ports; along the axis of the mixing cavity, each solid portion of an upper liquid distribution plate covers a corresponding refrigerant port of a lower liquid distribution plate and overlaps with the projections of the solid portions on both sides of the corresponding refrigerant port of the lower liquid distribution plate to form a group of pair of opposed flow channels for the mixed refrigerant to flow in opposite directions, the mixed refrigerant enters the pair of opposed flow mixing element through the mixing chamber and is mixed in each group of pair of opposed flow channels. The minimum width L0 of each overlap region formed by the overlap of the solid portion of the upper liquid distribution plate and the projections of the solid portions on both sides of the corresponding refrigerant port of the lower liquid distribution plate satisfies 0.5mm≤L0≤3.5mm. The axial distance H0 between the solid portions of adjacent liquid distribution plates satisfies 0<H0≤3mm. The liquid distribution plates are arranged in sequence and abut each other locally, and the solid portions of adjacent liquid distribution plates are separated by a flow channel gap. Alternatively, the liquid distribution plates are arranged in sequence along the axis of the mixing cavity and are separated by a flow channel gap. The pair of opposed flow mixing element further comprises a limiting sleeve sleeved on the outer wall of the mixing cavity, and the ends of adjacent liquid distribution plates abut the limiting sleeve to be arranged in sequence. The liquid distribution plate is of an integral structure, and a connecting hole is formed in the middle of the liquid distribution plate to be sleeved on the outer wall of the mixing cavity. Alternatively, the liquid distribution plate comprises a plurality of independent solid portions, and the plurality of solid portions are arranged in sequence and fixed on the outer wall of the mixing cavity. The most upstream liquid distribution plate is integrally formed with the mixing cavity, and the other liquid distribution plates are connected to the outer wall of the mixing cavity or are sequentially connected to the most upstream liquid distribution plate. The refrigerant port is a notch slot continuously extending to the edge of the liquid distribution plate in the radial direction of the liquid distribution plate, and the notch slot is a fan-shaped, rectangular, or a slot with a curved wall. The refrigerant port is one or a combination of through holes, flanged holes, or arc bubble holes. The pair of opposed flow mixing element comprises three or more liquid distribution plates, and a plurality of groups of pair of opposed flow channels are formed between adjacent liquid distribution plates, and the refrigerant is mixed in two or more stages in the pair of opposed flow mixing element. The pair of opposed flow mixing element comprises a plurality of liquid distribution units, each liquid distribution unit comprises at least two liquid distribution plates and a plurality of groups of pair of opposed flow channels are formed between adjacent liquid distribution plates, and no pair of opposed flow channels are formed between adjacent liquid distribution units.

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