Novel liquid homogenizing and separating device, heat exchange equipment and refrigerating system

Abstract

The invention provides a novel liquid uniformizing and separating device, heat exchange equipment and a refrigerating system. The novel liquid uniformizing and separating device comprises a body, a correlation liquid uniformizing assembly, a jet flow part and a flow guide plate. In the correlation liquid homogenizing assembly, a plurality of liquid homogenizing plates are sequentially arranged on the peripheral wall of a mixing cavity in the axial direction of a body, and each liquid homogenizing plate comprises a plurality of refrigerant ports distributed around the mixing cavity in the circumferential direction and solid parts located between the adjacent refrigerant ports. In the axial direction of the body, each solid part of the upper liquid homogenizing plate in every two adjacent liquid homogenizing plates covers the corresponding refrigerant opening in the lower liquid homogenizing plate and is overlapped with projection of the solid parts on the two sides of the corresponding refrigerant opening of the lower liquid homogenizing plate so as to form a set of opposite jet flow channels where refrigerants flow in the opposite directions, and the refrigerants are oppositely jetted and mixed in each set of opposite jet flow channels. The jet flow piece is provided with a jet flow hole for collecting the oppositely-jetted and mixed refrigerants. The flow guide plate is provided with a plurality of flow guide holes corresponding to the branch pipe holes in the body in a one-to-one mode, and the flow guide holes are annularly distributed in the periphery of the projection area, on the flow guide plate, of the jet flow hole around the axis of the body.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration accessories, and in particular to a novel liquid equalizing and liquid separating device, heat exchange equipment and refrigeration system. Background Art

[0002] To improve the performance of refrigeration system units in multi-flow heat exchange assemblies, a distributor is often required before the heat exchanger. However, due to installation space limitations, the two-phase refrigerant, after throttling by the expansion valve, must be redirected through a bend in the pipe before entering the distributor. The centrifugal forces experienced by the gas and liquid phases at the bend differ, causing separation and severely impacting the uniformity of the two-phase refrigerant distribution.

[0003] To this end, the inventor proposed a pre-rectification distributor, heat exchanger assembly and refrigeration equipment in Chinese patent CN118882244A. The refrigerant is pre-rectified by a reflective mixing method through a flow pattern arrangement component, and then subjected to a high-speed jet to achieve full mixing of the gas-liquid two-phase refrigerant. The distributor of this structure has excellent liquid separation performance in scenarios where the refrigerant has a large dryness and a large mass flow rate, but it is still difficult to effectively improve the liquid separation performance in scenarios with low dryness (such as dryness less than 0.15) or low mass flow (branch mass flow rate is less than or equal to 40Kg / h), mainly manifested in poor liquid separation uniformity or poor stability under different working conditions. The reason is that in scenarios with low dryness or low mass flow, the refrigerant is basically in a laminar state after gas-liquid separation in the bend section. Even after reflection and mixing by the flow pattern arrangement component, the two-phase refrigerant is still difficult to achieve a fully mixed diffuse flow pattern, so it is difficult to stably achieve uniform distribution of the two-phase refrigerant.

[0004] In order to enhance the mixing effect, some people have proposed swirl blade or impeller distributors. Although the swirl blade type has a strong turbulent effect, its blades are not only difficult to process but also difficult to apply to the body with a relatively small volume. In the impeller distributor (such as Chinese patent CN217464979U and Chinese patent CN114963483A), the refrigerant is always output axially along the surface of the blade, and the mixing effect of the refrigerant during the transmission process is extremely limited; even in Chinese patent CN114963483A, the refrigerant will generate a reflection vortex when impacting each arc-shaped blade, but for the refrigerant close to laminar flow, the vortex generated by the reflection still makes it difficult for the refrigerant to enter a uniformly mixed diffuse flow type, so it still cannot solve the problem of poor refrigerant distribution uniformity in low dryness and low flow scenarios. More importantly, in an impeller-type distributor, the gap between the blades and the spacing between the branch holes varies depending on the impeller's installation angle, the number of branch holes, and the spacing between them. This results in significant variations in liquid distribution uniformity between distributors of different specifications, and even between units of the same specification, leading to poor product reproducibility. Furthermore, this impeller structure presents challenges such as difficult and costly blade machining and assembly difficulties. Summary of the Invention

[0005] In order to overcome the deficiencies of the prior art, the present invention provides a novel liquid equalizing and liquid separating device, heat exchange equipment and refrigeration system.

[0006] In order to achieve the above-mentioned purpose, the first aspect of the present invention provides a novel liquid equalizing and liquid separating device, which includes a main body and a counter-equalizing component, a jet component and a guide plate arranged in sequence in the inner cavity of the main body along the flow direction of the refrigerant. The counter-equalizing component includes a mixing cavity body with a mixing cavity and a plurality of equalizing plates, and the plurality of equalizing plates are arranged in sequence on the outer peripheral wall of the mixing cavity body along the axial direction of the main body. Each equalizing plate includes a plurality of refrigerant ports distributed circumferentially around the mixing cavity body and a solid portion located between adjacent refrigerant ports; along the axial direction of the main body, each solid portion of the upper equalizing plate in the two adjacent equalizing plates covers the corresponding refrigerant port on the lower equalizing plate, and overlaps with the projection of the solid portion on both sides of the corresponding refrigerant port of the lower equalizing plate to form a group of counter-equalizing channels in which the refrigerant flows in opposite directions. The refrigerant after reflection and mixing in the mixing cavity enters a plurality of counter-equalizing channels, and the refrigerant is mixed in each group of counter-equalizing channels. The jet component has a jet hole, and the refrigerant after counter-mixing is collected at the jet hole. The guide plate has a plurality of guide holes corresponding to the branch pipe holes on the body one by one, and the plurality of guide holes are distributed in a ring shape around the axis of the body and on the periphery of the projection area of ​​the jet hole on the guide plate.

[0007] According to an embodiment of the first aspect of the present invention, a first chamber excluding a mixing chamber is formed between the upstream liquid balancing plate and the inner circumferential wall of the liquid inlet end of the main body, a second chamber is formed between the downstream liquid balancing plate and the jet element, a third chamber is formed between the jet element and the plane where the guide holes on the guide plate are located, and a fourth chamber is formed between the guide plate and the inner circumferential wall of the liquid outlet end of the main body; in two adjacent chambers, the volume ratio of the upstream chamber to the downstream chamber is between 0.7 and 1.35.

[0008] According to an embodiment of the first aspect of the present invention, the new liquid equalization and separation device also includes a spacer sleeve arranged between the guide plate and the liquid outlet end of the main body, and the spacer sleeve is located on the inner periphery of the multiple branch pipe holes, and a fourth chamber is formed between the guide plate, the spacer sleeve and the inner peripheral wall of the liquid outlet end of the main body.

[0009] According to one embodiment of the present invention, among multiple liquid equalizing plates, in the two overlapping areas formed by the overlapping projections of the solid part of the upper liquid equalizing plate and the solid parts on both sides of the corresponding refrigerant port of the lower liquid equalizing plate, the minimum width L0 of each overlapping area satisfies: 0.5mm≤L0≤3.5mm.

[0010] According to an embodiment of the first aspect of the present invention, the axial distance H0 between the solid parts of two adjacent liquid balancing plates satisfies 0<H0≤3mm.

[0011] According to an embodiment of the first aspect of the present invention, parts of the plurality of liquid balancing plates are sequentially abutted, and a flow channel gap is provided between the solid parts of two adjacent liquid balancing plates;

[0012] Alternatively, a plurality of liquid balancing plates are distributed at intervals on the outer peripheral wall of the mixing cavity along the axial direction of the main body, so that a flow channel gap is formed between the solid parts of two adjacent liquid balancing plates.

[0013] According to an embodiment of the first aspect of the present invention, the opposing liquid averaging assembly further includes a limiting sleeve disposed on the outer peripheral wall of the mixing chamber, and two adjacent liquid averaging plates abut against two ends of the limiting sleeve to be spaced apart.

[0014] According to an embodiment of the first aspect of the present invention, the liquid balancing plate is an integral structure, and a connection hole is formed in the middle of the liquid balancing plate and is sleeved on the outer peripheral wall of the mixing chamber;

[0015] Alternatively, the liquid balancing plate includes a plurality of independent solid parts, and the plurality of solid parts are distributed at intervals along the circumference of the mixing cavity and fixed to the outer peripheral wall of the mixing cavity.

[0016] According to an embodiment of the first aspect of the present invention, among the multiple liquid balancing plates, the upstreammost liquid balancing plate is integrally formed with the mixing chamber; the other liquid balancing plates are connected to the outer peripheral wall of the mixing chamber or are sequentially connected to the upstreammost liquid balancing plate.

[0017] According to an embodiment of the first aspect of the present invention, the refrigerant port is a notch groove extending continuously along the radial direction of the liquid equalizing plate to the edge of the liquid equalizing plate, and the notch groove is fan-shaped, rectangular or has a curved groove wall.

[0018] According to an embodiment of the present invention, the refrigerant port is a combination of one or more of a through hole, a flange hole or an arc bubble hole.

[0019] According to an embodiment of the first aspect of the present invention, the counter-jet liquid equalizing component includes more than three liquid equalizing plates, and multiple groups of counter-jet flow channels are formed between two adjacent liquid equalizing plates. The refrigerant undergoes more than two levels of counter-jet mixing in the counter-jet liquid equalizing component.

[0020] According to an embodiment of the first aspect of the present invention, the counter-jet liquid equalizing component includes multiple liquid equalizing units, each liquid equalizing unit includes at least two liquid equalizing plates and multiple groups of counter-jet channels are formed between two adjacent liquid equalizing plates; no counter-jet channels are formed between adjacent liquid equalizing units.

[0021] According to an embodiment of the first aspect of the present invention, on the guide plate, an area opposite to the jet hole protrudes and extends toward the liquid outlet end of the body to form a reflective cavity with an opening facing the jet hole.

[0022] The second aspect of the present invention further provides a heat exchange device, characterized in that it includes the novel liquid equalization and liquid separation device according to claim 1.

[0023] The third aspect of the present invention further provides a refrigeration system, characterized in that it includes the heat exchange device of claim 14.

[0024] In summary, in the new liquid equalizing and liquid separating device provided by the present invention, the reflected mixing and the reflected mixing are integrated in the liquid equalizing component. On the basis of disturbing the input refrigerant flow pattern, the reflected mixing of the refrigerant is realized through multiple groups of reflected flow channels between adjacent liquid equalizing plates, thereby enhancing the turbulence of the two-phase refrigerant so that the refrigerant develops into a stable diffuse flow pattern. The refrigerant after the reflected mixing is collected at the jet hole on the jet component, and the speed is increased by throttling again through the jet hole, thereby increasing the refrigerant flow rate, suppressing the separation of the gas-liquid two-phase, and enhancing the reflected mixing degree of the refrigerant on the guide plate to ensure that the two-phase refrigerant is fully mixed. At the same time, a plurality of guide holes corresponding to the branch pipe holes are provided on the guide plate, so that each branch pipe hole has a basically similar distribution path. This setting makes the distribution path of the refrigerant after full mixing irrelevant to the number of refrigerant ports and their distribution positions on the liquid equalizing component, and the batch products have excellent repeatability; and for products of different specifications, it is only necessary to replace the guide plate to ensure the uniformity and repeatability of the refrigerant distribution.

[0025] Furthermore, the arrangement of the jet-equalizing assembly, jet element, and guide plate creates four chambers within the main body. By precisely controlling the volume ratio between adjacent chambers, the volume expansion of the refrigerant as it flows through them is controlled, preventing a reduction in refrigerant flow rate due to excessive expansion. This ensures high-speed refrigerant flow within each chamber, enhancing mixing while preventing gas-liquid phase segregation caused by reduced flow rate.

[0026] In order to make the above and other objects, features and advantages of the present invention more obvious and easy to understand, preferred embodiments are given below with reference to the accompanying drawings for detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 FIG2 is a schematic structural diagram of a novel liquid equalizing and liquid separating device provided in one embodiment of the present invention.

[0028] Figure 2 Shown Figure 1 Schematic diagram of the structure of the middle-beam equalizing liquid component.

[0029] Figure 3 Shown Figure 2 Schematic diagram of the structure from another perspective.

[0030] Figure 4 Shown Figure 2 Projection diagram of .

[0031] Figure 5 Shown Figure 2 Schematic diagram of projection from another perspective.

[0032] Figure 6 Shown Figure 5 Schematic cross-section along line AA.

[0033] Figure 7 The refrigerant is shown in Figure 5 Flow diagram in .

[0034] Figure 8 The following is a CFD simulation analysis. Figure 1 The new liquid-distributing and equalizing device shown is a schematic diagram of the flow of refrigerant in the jet channel.

[0035] Figure 9 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0036] Figure 10 Shown Figure 9 Schematic cross-section diagram.

[0037] Figure 11 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0038] Figure 12 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0039] Figure 13 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0040] Figure 14 Shown Figure 13 Schematic cross-section diagram.

[0041] Figure 15 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0042] Figure 16 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0043] Figure 17 FIG2 is a schematic structural diagram of a mixing cavity and a first liquid balancing plate in a cross-beam liquid balancing assembly provided in another embodiment of the present invention.

[0044] Figure 18 Shown are included Figure 17 Schematic diagram of the structure of the opposing liquid equalization component.

[0045] Figure 19 Shown Figure 18 Schematic cross-section diagram.

[0046] Figure 20 Shown with Figure 1Schematic diagram of the structure of control sample 1 corresponding to the sample structure shown.

[0047] Figure 20A Shown with Figure 1 Schematic diagram of the structure of control sample 2 corresponding to the sample structure shown.

[0048] Figure 21 Shown is a schematic structural diagram of a novel liquid equalizing and liquid separating device provided in another embodiment of the present invention.

[0049] Figure 21A Shown is a schematic structural diagram of a novel liquid equalizing and liquid separating device provided in another embodiment of the present invention.

[0050] Figure 22 Shown is a structural schematic diagram of the opposing-beam liquid equalizing component provided in the second embodiment of the present invention.

[0051] Figure 23 Shown Figure 22 Projection diagram of .

[0052] Figure 24 Shown Figure 23 Schematic cross-section along line BB.

[0053] Figure 25 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0054] Figure 26 Shown Figure 25 Schematic cross-section diagram.

[0055] Figure 27 Shown is a structural schematic diagram of a cross-beam liquid equalization component provided by another embodiment of the present invention.

[0056] Figure 28 Shown Figure 27 Schematic cross-section diagram.

[0057] Figure 29 Shown Figure 28 Enlarged schematic diagram of point C in the middle.

[0058] Figure 30 FIG. 1 is a schematic structural diagram of a novel liquid equalizing and liquid separating device provided in Example 3 of the present invention.

[0059] Figure 31 Shown is a schematic structural diagram of a novel liquid equalizing and liquid separating device provided in another embodiment of the present invention. DETAILED DESCRIPTION

[0060] Example 1

[0061] In order to improve the liquid separation performance of the traditional distributor, the inventor has proposed a pre-rectification distributor. When the dryness and mass flow of the input refrigerant are both large, the refrigerant is in a disturbed elastic flow. The refrigerant in this state can form a stable diffuse mist flow after being reflected by the mixing chamber, thereby achieving uniform and stable liquid separation performance. However, when the input refrigerant is at a low dryness (such as a dryness lower than 0.15) or a low mass flow (such as a mass flow distributed to each branch is less than or equal to 40Kg / h), the refrigerant is close to a laminar flow; at this time, the refrigerant is still difficult to form a mist flow after pre-rectification, resulting in poor liquid separation uniformity or poor liquid separation stability; liquid separation stability refers to the ability of the distributor to resist external interference (such as refrigerant mass flow, dryness and other factors).

[0062] In view of this, the present embodiment provides a new type of liquid equalizing and liquid separating device, which includes a main body 10 and a counter-equalizing liquid component 20, a jet component 50 and a guide plate 60 arranged in sequence in the inner cavity of the main body 10 along the flow direction of the refrigerant. The counter-equalizing liquid component 20 includes a mixing cavity 11 and a plurality of equalizing plates. The plurality of equalizing plates are arranged in sequence on the outer peripheral wall of the mixing cavity 1 along the axial direction of the main body 10. Each equalizing plate includes a plurality of refrigerant ports distributed circumferentially around the mixing cavity 1 and a solid portion located between adjacent refrigerant ports. Along the axial direction of the main body 10, each solid portion of the upper equalizing plate of the two adjacent equalizing plates covers the corresponding refrigerant port on the lower equalizing plate, and overlaps with the projection of the solid portion on both sides of the corresponding refrigerant port of the lower equalizing plate to form a group of counter-equalizing channels in which the refrigerant flows in opposite directions. The refrigerant after reflection and mixing in the mixing cavity enters the plurality of counter-equalizing channels, and the refrigerant is counter-equalized and mixed in each group of counter-equalizing channels. The ejector 50 has an ejection hole 501, into which the mixed refrigerant is collected. The guide plate 60 has a plurality of guide holes 601 corresponding one-to-one with the branch pipe holes 110 on the body 10. The plurality of guide holes 601 are distributed in a circular pattern around the axis of the body 10, circumferentially around the projection of the ejection holes 501 on the guide plate 60.

[0063] In this embodiment, the new liquid equalization and liquid separation device also includes a plurality of branch pipes 30 connected to the branch pipe holes 110 and a liquid inlet pipe 40 connected to the liquid inlet end of the main body 10. After the refrigerant is input from the liquid inlet pipe 40, it impacts the inner wall of the mixing chamber 11 on the liquid equalization component 20 and reflects to generate vortexes, and the laminar refrigerant is quickly converted into a slug flow. The slug flow refrigerant enters from the multiple refrigerant ports on the liquid equalization plate, and after being throttled and accelerated by the refrigerant port to become a high-speed refrigerant, it is injected into each group of slug flow channels 200. In each group of slug flow channels 200, the high-speed refrigerants collide with each other, the liquid film is torn into droplets and dispersed in the gas phase, forming a uniform mist flow. The mist flow is throttled and accelerated again through the jet hole 501, and then reflected and mixed by the guide plate 60 for the second time, and then distributed into the corresponding multiple branch pipe holes 110 in a one-to-one manner with equal paths and equal resistance through multiple guide holes 601, thereby achieving uniform distribution of the refrigerant. The new liquid equalizing device provided in this embodiment integrates four levels of disturbance of "reflection-counter-high-speed jet-re-reflection", which can achieve full mixing and uniform distribution of gas-liquid two-phase refrigerant under any working conditions, and has extremely excellent liquid separation uniformity, stability and repeatability.

[0064] Although this embodiment uses the example of improving refrigerant liquid separation properties at low dryness or low mass flow rates to illustrate the principles of the novel liquid balancing and separation device, this does not limit the novel liquid balancing and separation device provided by the present invention to applications at low dryness or low mass flow rates. The novel liquid balancing and separation device provided by this embodiment can also be used in other scenarios with higher dryness or higher mass flow rates.

[0065] like Figures 2 to 6 As shown, in this embodiment, the counter-equalizing liquid component 20 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 a plurality of refrigerant ports 211 and a plurality of entity portions 212 located between adjacent refrigerant ports; similarly, the second equalizing plate 22 has a plurality of refrigerant ports 221 and a plurality of entity portions 222 located between adjacent refrigerant ports. Specifically, the two equalizing plates are staggered, and the middle area of ​​the first equalizing plate entity portion 212 covers the corresponding refrigerant ports 221 on the second equalizing plate 22, and the areas on both sides thereof overlap with the projections of the second equalizing plate entity portion 222, thereby forming a first flow channel 201 and a second flow channel 202 to form a group of counter-equalizing channels 200. The refrigerants flow in opposite directions in each group of counter-equalizing channels to achieve counter-equalizing mixing.

[0066] In this embodiment, each liquid balancing plate includes eight refrigerant ports and eight solid portions. The two liquid balancing plates correspondingly form eight independent sets of opposing flow channels 200, each of which includes a first flow channel 201 and a second flow channel 202. However, the present invention is not limited to this. In other embodiments, the number of solid portions and refrigerant ports on the liquid balancing plate may be two, three, four, five, six, seven, or other integers.

[0067] Each refrigerant port 211 on the first liquid balancing plate 21 is connected to two sets of opposing flow channels on both sides. Figure 7 The diagram shows the flow of refrigerant after it enters two adjacent equalizing plates. The arrows in the figure indicate the flow direction. Figure 8 The figure is a schematic diagram of the flow of refrigerant in two adjacent equalizing plates during CFD (Computational Fluid Dynamics) simulation analysis. Figure 2 、 Figure 7 as well as Figure 8 The three adjacent refrigerant ports 211 on the first liquid balancing plate 21 are defined as 211b, 211a and 211c. Figure 2 、 Figure 7 as well as Figure 8 Taking the refrigerant port 211a on the first liquid balancing plate 21 as an example, it has two adjacent refrigerant ports 211b and refrigerant port 211c. Part of the refrigerant input from the refrigerant port 211a flows into the first channel 201 of the jet channel 200, while the other part of the refrigerant enters the second channel 202' of the jet channel 200'. The refrigerant entering the first channel 201 is mixed with the refrigerant in the second channel 202 (from the refrigerant port 211b) in the jet channel 200. Correspondingly, the refrigerant entering the second channel 202' is mixed with the refrigerant in the first channel 201' (from the refrigerant port 211c) in another group of jet channels 200'. By analogy, on the first liquid balancing plate 21, the refrigerant input from the adjacent refrigerant ports 211 will be mixed in the corresponding jet channels before being output from the corresponding refrigerant port 221 on the second liquid balancing plate.

[0068] exist Figure 8 In the figure, the refrigerant input from the refrigerant port 211a flows into the first flow channel 201 and the second flow channel 202' on both sides thereof at a high speed (the refrigerant flow rate is represented by orange in the figure). The refrigerant entering the first flow channel 201 is mixed in the counter-jet flow channel 200, and the flow rate of the refrigerant in the circumferential direction gradually decreases (gradually transitioning from orange to blue), and then flows out from the refrigerant port 221 on the second liquid equalizing plate 22 in the axial direction. Similarly, the refrigerant entering the second flow channel 202' is mixed in the counter-jet flow channel 200', and the flow rate of the refrigerant in the circumferential direction also gradually decreases. Figure 8 The change in the refrigerant flow rate reflects that in the novel liquid-distributing and liquid-equalizing device provided in this embodiment, the input refrigerant undergoes jet mixing in each pair of jet channels.

[0069] In this embodiment, the multiple groups of counter-jet channels 200 between the first liquid balancing plate 21 and the second liquid balancing plate 22 are independent of each other. The refrigerant after being initially disturbed into a slug-like flow by the mixing chamber 11 is diverted into multiple flow paths. The refrigerant in each flow path is mixed into a diffuse mist flow in the corresponding counter-jet channel 200, thereby achieving uniform and stable distribution of the refrigerant. In existing reflective mixing distributors (such as baffle type or impeller type), the intensity of the reflective mixing depends only on the kinetic energy of the incident refrigerant; in this embodiment, the intensity of the counter-jet mixing is related to the sum of the kinetic energies of the two refrigerants flowing in opposite directions. Obviously, under the same working conditions, the counter-jet mixing will further increase the degree of turbulence of the two-phase flow, thereby promoting the full mixing of the gas-liquid two-phase refrigerant.

[0070] Although this embodiment is described by taking the example of the cross-beam liquid equalizing assembly 20 including two liquid equalizing plates, the present invention does not make any limitation to this. In other embodiments, such as Figure 9 and Figure 10 As shown, the cross-beam mixing assembly 20 includes three equalizing plates: a first equalizing plate 21, a second equalizing plate 22, and a third equalizing plate 23. A primary cross-beam mixing structure 200a is formed between the first and second equalizing plates 21, 22. The primary cross-beam mixing structure 200a has multiple sets of primary cross-beam flow channels. A secondary cross-beam mixing structure 200b is formed between the second and third equalizing plates 22, 23. The secondary cross-beam mixing structure 200b has multiple sets of secondary cross-beam flow channels.

[0071] Similar to the present embodiment, in the first-stage counter-jet mixing structure 200a, the first equalizing plate 21 is the upper equalizing plate, and the second equalizing plate 22 is the lower equalizing plate. The refrigerant enters the multiple groups of counter-jet channels 200 located between the two equalizing plates through the multiple refrigerant ports 211 on the first equalizing plate 21, and after counter-jet mixing, enters the multiple refrigerant ports 221 on the second equalizing plate 22, that is, enters the second-stage counter-jet mixing structure 200b. In the second-stage counter-jet mixing structure 200b, the second equalizing plate 22 serves as the upper equalizing plate, and the third equalizing plate 23 serves as the lower equalizing plate. The middle area of ​​the solid portion 222 on the second equalizing plate covers the corresponding refrigerant port 231 on the third equalizing plate 23, and its two side areas overlap with the projection of the third equalizing plate solid portion 232, thereby forming multiple groups of secondary counter-jet channels 200 including the first channel 201 and the second channel 202. The refrigerant enters the multiple groups of counter-jet channels 200 through the multiple refrigerant ports 221 on the second liquid balancing plate 22, and is output from the multiple refrigerant ports 231 on the third liquid balancing plate 23 after counter-jet mixing; that is, the structural counter-jet liquid balancing component 20 performs secondary counter-jet mixing on the refrigerant.

[0072] exist Figure 11In the embodiment, the counter-emission liquid equalizing assembly 20 includes four equalizing plates: a first equalizing plate 21, a second equalizing plate 22, a third equalizing plate 23, and a fourth equalizing plate 24. Multiple sets of primary counter-emission flow channels are formed between the first equalizing plate 21 and the second equalizing plate 22, multiple sets of secondary counter-emission flow channels are formed between the second equalizing plate 22 and the third equalizing plate 23, and multiple sets of tertiary counter-emission flow channels are formed between the third equalizing plate 23 and the fourth equalizing plate 24. Similarly, in other embodiments, the counter-emission liquid equalizing assembly may include more than five equalizing plates.

[0073] However, the present invention does not impose any limitation on this. In other embodiments, the cross-flow equalization component 20 may also include multiple cross-flow equalization units, each cross-flow equalization unit includes at least two cross-flow equalization plates and multiple cross-flow channels are formed between two adjacent cross-flow equalization plates, but no cross-flow channels are formed between adjacent cross-flow equalization units. Figure 12 As shown, the counter-jet liquid equalizing assembly 20 also includes four liquid equalizing plates. The first liquid equalizing plate 21 and the second liquid equalizing plate 22 constitute the first liquid equalizing unit 20_1, and there are multiple sets of counter-jet flow channels between the two. The third liquid equalizing plate 23 and the fourth liquid equalizing plate 24 constitute the second liquid equalizing unit 20_2, and there are also multiple sets of counter-jet flow channels between the two adjacent liquid equalizing plates between the first liquid equalizing unit 20_1 and the second liquid equalizing unit 20_2. However, the axial spacing between the physical parts of the two adjacent liquid equalizing plates (i.e., the second liquid equalizing plate 22 and the third liquid equalizing plate 23) is relatively large (greater than the axial spacing H0 between the physical parts of the two adjacent liquid equalizing plates that form the counter-jet flow channels), so that no counter-jet flow channels are formed between the two liquid equalizing units. Although the counter-jet liquid equalizing assembly 20 of this structure has four liquid equalizing plates, it only performs two-stage counter-jet mixing of the refrigerant. Similarly, when there are five equalizing plates, three adjacent equalizing plates can be arranged to form a equalizing unit with secondary, opposite-beam mixing; the other two plates can form another equalizing unit with primary, opposite-beam mixing. Similarly, no opposite-beam flow paths are formed between adjacent equalizing units. In other embodiments, when there are six or more equalizing plates, the opposite-beam equalizing assembly can also include three or more equalizing units.

[0074] Figure 4 Shown Figure 2 Projection schematic diagram from a top-down perspective, where the area between adjacent red lines is the refrigerant port 211 on the first liquid equalizing plate, the area between adjacent dotted lines is the refrigerant port 221 on the second liquid equalizing plate, and the shaded area is the overlapping area formed by the overlapping projections of the solid part 212 of the upper liquid equalizing plate (i.e., the first liquid equalizing plate 21) and the solid part 222 on both sides of the corresponding refrigerant port 221 of the lower liquid equalizing plate (i.e., the second liquid equalizing plate 22).

[0075] In this embodiment, the minimum width L0 of each overlapping area is set to meet the following requirements: 0.5mm≤L0≤3.5mm. The lower limit of the minimum width L0 determines the size of the two side areas of the solid part 212 of the first equalizing plate, ensuring that a first flow channel 201 and a second flow channel 202 with a certain circumferential length can be formed between the upper and lower equalizing plates, providing space for the counter-mixing of the refrigerant. Furthermore, since the radial size of the equalizing plate is limited by the inner cavity of the main body 10; preferably, the outer diameter of the equalizing plate is substantially close to the inner cavity diameter of the main body 10. For the equalizing plate of a certain size, the upper limit of the minimum width L0 is not only related to the circumferential size of the counter-flow channel 200, but also to the flow cross-sectional area of ​​the refrigerant port 211 on the first equalizing plate 21. The larger the upper limit of the minimum width L0, the larger the circumferential size of the counter-flow channel 200 and the smaller the flow cross-sectional area of ​​the refrigerant port 211 of the first equalizing plate will be, both of which will increase the flow resistance of the refrigerant. Therefore, it is necessary to control the upper limit of the minimum width L0 to limit the pressure loss caused by the refrigerant during the cross-jet mixing, so as to avoid affecting the performance of the refrigeration system unit due to excessive refrigerant pressure loss. Preferably, the minimum width L0 of the overlapping area is set to 1.5mm. However, the present invention does not impose any limitation on this. In other embodiments, the minimum width L0 of the overlapping area can also be other values ​​such as 0.8mm, 1.13mm, 1.3mm, 1.83mm, 2mm, 2.25mm, 2.5mm, 3.0mm, etc.

[0076] In this embodiment, the first liquid equalizing plate refrigerant port 211 and the second liquid equalizing plate refrigerant port 221 are both notched grooves that extend radially and continuously to the edge of the liquid equalizing plate, and the shape of the notched grooves is fan-shaped. Correspondingly, the first liquid equalizing plate entity 212 and the second liquid equalizing plate entity 222 are also fan-shaped. The minimum width L0 of the overlapping area is the width of the overlapping area near the center of the liquid equalizing plate. However, the shape of the refrigerant port of the present invention is not limited in any way. In other embodiments, the refrigerant port may also be a rectangular notched groove or a notched groove with a curved groove wall. In other embodiments, the refrigerant port may also be a hole-shaped, such as one or more combinations of through holes, flanging holes or arc bubble holes, and the outline of the hole-shaped refrigerant port may be circular, elliptical or fan-shaped, etc. Specifically, as Figure 13 and Figure 14 As shown, the first liquid balancing plate refrigerant port 211 and the second liquid balancing plate refrigerant port 221 are both through holes. Figure 15 The first liquid balancing plate refrigerant port 211 and the second liquid balancing plate refrigerant port 221 are both flanged holes.

[0077] Although this embodiment takes the two adjacent liquid balancing plates as having the same structure and the refrigerant ports as fan-shaped notches as an example, the present invention does not impose any limitation on this. In other embodiments, the refrigerant ports of the two adjacent liquid balancing plates may have different structures. Figure 16 As shown, the refrigerant port 211 on the first liquid balancing plate 21 is a through hole, while the refrigerant port 221 on the second liquid balancing plate 22 is a fan-shaped notch.

[0078] In the new liquid-equalizing and liquid-separating device provided in this embodiment, the high-speed counter-injection of the refrigerant in the jet channel 200 is the key to the development of the refrigerant from a bullet-like flow to a mist-like flow, and the effect of the refrigerant counter-injection mixing is positively correlated with its flow rate (that is, the greater the flow rate, the better the counter-injection mixing effect). In the process of the refrigerant flowing, its flow rate will inevitably be affected by factors such as flow resistance and volume change. In order to improve the effect of the counter-injection mixing, this embodiment first throttles and speeds up the refrigerant through the refrigerant port 211 on the first liquid-equalizing plate. On this basis, as Figure 5 and Figure 6 As shown, by controlling the axial spacing H0 between the first liquid balancing plate entity part 212 and the second liquid balancing plate entity part 222, the axial size of the jet channel 200 is limited to prevent the refrigerant from over-expanding due to the excessive space in the jet channel 200, thereby reducing the flow rate. That is, by controlling the axial spacing H0, the flow rate of the refrigerant in the jet channel 200 is maintained or increased to enhance the jet mixing effect. Preferably, the axial spacing H0 is set to 1.5 mm. However, the present invention does not impose any limitation on this. In other embodiments, the axial spacing H0 may 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.

[0079] In this embodiment, the first and second liquid balancing plates 21 and 22 are spaced apart along the axial direction on the outer wall of the mixing chamber 1, so that a flow channel gap 210 is formed between the first and second liquid balancing plate entities 212 and 222. The axial dimension of the flow channel gap 210 is the axial spacing H0. In order to facilitate the precise control of the axial dimension H0 between adjacent liquid balancing plates during assembly, as shown in FIG. Figure 5 and Figure 6 As shown, the cross-sectional liquid equalizing assembly 20 further includes a limiting sleeve 25, which is externally mounted on the outer peripheral wall of the mixing chamber 1. The first and second liquid equalizing plates 21 and 22 respectively abut against the ends of the limiting sleeve to achieve spaced distribution. In this embodiment, the number of limiting sleeves 25 is one. However, the present invention does not impose any limitation on this. In other embodiments, when the cross-sectional liquid equalizing assembly includes more than three spaced liquid equalizing plates, the number of limiting sleeves is also multiple.

[0080] In this embodiment, the limiting sleeve 25 and the two adjacent liquid balancing plates are separate structures. However, the present invention is not limited to this. In other embodiments, the limiting sleeve may be integrally formed with one of the liquid balancing plates. For example, the limiting sleeve may be integrally formed with the first liquid balancing plate or the second liquid balancing plate using a stamping and flanging process.

[0081] In this embodiment, the first and second liquid balancing plates 21 and 22 are both integral structures, with a connection hole formed in the center of each plate, which is sleeved onto the outer peripheral wall of the mixing chamber 1. However, the present invention is not limited to this. In other embodiments, the liquid balancing plate may also include multiple independent solid portions, which are spaced apart along the circumference of the mixing chamber and fixed to the outer peripheral wall of the mixing chamber.

[0082] In this embodiment, the first and second liquid balancing plates 21 and 22 are both plate-like structures with nearly flat surfaces on both sides. However, the present invention is not limited to this. In other embodiments, the liquid balancing plates may also be plate-like structures with ridges on their surfaces or other structures.

[0083] In this embodiment, the two liquid balancing plates are welded separately to the outer wall of the mixing chamber 1. However, the present invention does not impose any limitation on this. In other embodiments, the most upstream liquid balancing plate (i.e., the first liquid balancing plate 21) may be integrally formed with the mixing chamber 1, such as Figure 17 The other liquid balancing plates (such as the second liquid balancing plate 22) are welded to the outer wall of the mixing chamber 1, as shown. Figure 18 and Figure 19 However, the present invention is not limited thereto. In other embodiments, other liquid balancing plates (such as the second liquid balancing plate 22 ) may also be sequentially connected to the most upstream liquid balancing plate (i.e., the first liquid balancing plate 21 ).

[0084] In this embodiment, the mixing chamber 1 is a stretched cylinder, and the mixing chamber 11 is cylindrical. However, the present invention is not limited to this. In other embodiments, the mixing chamber can also be formed by stamping, and its contour can also be one or a combination of a truncated cone, a cone, or a sphere.

[0085] In the new liquid equalizing and liquid separating device provided in this embodiment, due to the limitations of the minimum width L0 of the overlapping area between adjacent liquid equalizing plates and the radial size of the liquid equalizing plates, it is difficult to keep the number of refrigerant ports on the liquid equalizing plates consistent with the number of branch pipe holes 110 on the main body 10. The circumferential installation angle of the opposing liquid equalizing component 20 will affect the distance from each branch pipe hole 110 to the refrigerant port on the downstreammost liquid equalizing plate. If the opposing liquid equalizing component 20 directly distributes the mixed refrigerant to multiple branch pipe holes 110, the uniformity of the refrigerant distribution will vary due to the different distribution paths and distribution resistances of each branch pipe hole 110. Correspondingly, batch products will also have the problem of poor repeatability due to the different circumferential installation angles of the opposing liquid equalizing component 20.

[0086] In order to improve the uniformity of liquid separation and the repeatability of batch products, this embodiment sequentially arranges a jet element 50 and a guide plate 60 downstream of the liquid equalization component 20, as shown in FIG. Figure 1As shown. While strengthening the mixing effect, this setting can also balance the distribution path of the mixed refrigerant with the help of the multiple guide holes 601 on the guide plate 60 that correspond one-to-one to the multiple branch holes 110, ensuring that each branch hole 110 has a basically equal distribution path, and the fully mixed refrigerant is distributed to each branch hole 110 with equal resistance, thereby achieving uniform liquid separation. Since the multiple branch holes 110 are usually arranged at equal intervals at the liquid outlet end of the main body 10; correspondingly, the multiple guide holes 601 are also distributed at equal intervals along the circumferential direction on the guide plate 60. This distribution method allows the guide plate 60 to maintain a one-to-one correspondence with the branch hole 110 regardless of the angle at which it is rotated during assembly, and the circumferential installation angle of the guide plate 60 and the opposing liquid equalizing component 20 no longer affects the refrigerant distribution path of each branch hole 110. In other words, the liquid separation uniformity of the new liquid equalizing and liquid separation device is no longer affected by the installation process, which further improves the refrigerant distribution performance and ensures excellent repeatability between batch products.

[0087] like Figure 1 As shown, the jet hole 501 on the jet element 50 is a flanged hole with the hole wall extending in the direction of the guide plate 60. However, the present invention is not limited to this. In other embodiments, the jet hole can also be a through hole with a substantially constant aperture, or a through hole with a aperture that gradually decreases in the direction of refrigerant flow; or, alternatively, a flanged hole with a straight section added thereto.

[0088] On the guide plate 60, the area opposite to the jet hole 501 protrudes and extends toward the liquid outlet end of the main body 10, forming a reflective cavity 602 with an opening facing the jet hole. The bottom wall of the reflective cavity 602 reflects the high-speed refrigerant ejected from the jet hole 501. The reflected refrigerant collides violently in the reflective cavity 602, further enhancing the turbulence of the two-phase flow to promote sufficient mixing of the refrigerant. In this embodiment, the downstream surface of the reflective cavity 602 basically abuts the inner wall of the liquid outlet end of the main body 10, and an annular chamber is enclosed between the outer peripheral wall of the reflective cavity 602 and the inner peripheral wall of the main body 10. This arrangement can reduce the volume of the chamber between the guide plate 60 and the liquid outlet end of the main body 10, so that the refrigerant maintains a high-speed diffuse flow pattern and is quickly distributed to the multiple branch holes 110.

[0089] In this embodiment, the reflective cavity 602 is a cylindrical cavity with a square longitudinal cross-sectional outline. However, the present invention is not limited to this. In other embodiments, the reflective cavity may be shaped as one or more combinations of a prism with a square longitudinal cross-sectional outline, a truncated cone or pyramid with a trapezoidal longitudinal cross-sectional outline, a cone or pyramid with a triangular longitudinal cross-sectional outline, or a partially circular longitudinal cross-sectional outline; for example, a combination of a cylinder and a partially spherical shape, a combination of a truncated cone and a partially spherical shape, or a combination of a prism and a partially spherical shape.

[0090] In order to verify the liquid separation uniformity and stability of the new liquid-dispensing device provided in this embodiment, Figure 1 The structure shown in the figure is used as a sample structure, and CFD (computational fluid dynamics) simulation is used to analyze its liquid separation performance under different dryness and input mass flow rates; and the pre-rectified distributor (such as Figure 20 As shown) as a control sample structure.

[0091] The software used for CFD simulation analysis is ANSYS software, and its condition settings are as follows:

[0092] Turbulence model: Realizable k-ε model;

[0093] Mesh parameters: Tetrahedral unstructured mesh is used;

[0094] Working conditions: The working fluid is R410A refrigerant and the wall boundary is an adiabatic boundary.

[0095] Boundary conditions: turbulence intensity 5%. Other boundary conditions are shown in the specific data table.

[0096] Evaluation parameters: STD and K. Among them, STD refers to the standard deviation of the refrigerant mass flow rate at the outlet of each branch pipe, and K refers to the standard deviation STD and the mass flow rate M set to each branch pipe. out percentage.

[0097] The specific calculation formula of STD is as follows:

[0098]

[0099] in, is the average refrigerant mass flow rate of all branch outlets, m j is the outlet refrigerant mass flow rate of the jth branch, n is the number of branches, M out To set the mass flow rate distributed to each branch.

[0100] 【1】Analyze the liquid separation uniformity and stability of samples and control samples at different dryness.

[0101] Sample selection: 6 samples and corresponding 6 control samples are selected according to the specifications of the main body 10, the specifications of the liquid inlet pipe 40, the number n of the branch pipes 30, and the specifications of the branch pipes 30. Each sample and the corresponding control sample 1 are simulated and analyzed at dryness of 0, 0.1, 0.15, 0.2, 0.25, 0.3, and 0.35, respectively.

[0102] The common parameters of the samples in the first dryness analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 45mm, the outer diameter of the main section of the liquid inlet pipe D1 = 12.7mm, the number of branches n = 17, the outer diameter of the branch pipe D2 = 3mm; set the input total mass flow rate M in=595Kg / h, set the mass flow rate M distributed to each branch out =35Kg / h.

[0103] The common parameters of the samples in the second dryness analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 45mm, the outer diameter of the main section of the liquid inlet pipe D1 = 16mm, the number of branch pipes n = 17, the outer diameter of the branch pipe D2 = 3.4mm; set the input total mass flow rate M in =935Kg / h, set the mass flow rate M distributed to each branch out =55Kg / h.

[0104] The common parameters of the samples in the third dryness analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 45mm, the outer diameter of the main section of the liquid inlet pipe D1 = 16mm, the number of branches n = 15, the outer diameter of the branch pipe D2 = 3.8mm; set the input total mass flow rate M in =1050Kg / h, set the mass flow rate M distributed to each branch out =70Kg / h.

[0105] The common parameters of the samples in the fourth dryness analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 63.5mm, the outer diameter of the main section of the liquid inlet pipe D1 = 16mm, the number of branches n = 27, the outer diameter of the branch pipe D2 = 3.0mm; set the input total mass flow rate M in =945Kg / h, set the mass flow rate M distributed to each branch out =35Kg / h.

[0106] The common parameters of the samples in the fifth dryness analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 63.5 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 22 mm, the number of branches n = 26, the outer diameter of the branch pipe D2 = 3.4 mm; the total mass flow rate M is set in 0=1430Kg / h, set the mass flow rate M distributed to each branch out =55Kg / h.

[0107] The common parameters of the samples in the sixth dryness analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 63.5 mm, the outer diameter of the main 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 total mass flow rate M is set to in =1680Kg / h, set the mass flow rate M distributed to each branch out =70Kg / h.

[0108] The data of the above samples and the corresponding control sample 1 are summarized in Table 1. After analysis, it is found that in each dryness analysis group, the STD and K value of each sample at different dryness are all lower than the corresponding control sample 1. After reviewing the data of the six dryness analysis groups, it can still be seen that the K value distribution of the samples is more concentrated, with a distribution range of 2.36% to 3.49%, while the K value distribution range of the control sample 1 is: 3.56% to 4.95%. Therefore, it can be concluded that at different dryness, this example Figure 1 The sample structure shown (i.e. the new liquid-dispensing device) is superior to the Figure 20 The control sample shown is a structure (i.e., the existing pre-rectifying distributor structure).

[0109] 【2】Analyze the liquid separation uniformity and stability of the sample and the reference sample at different mass flow rates.

[0110] Sample selection: 7 samples and corresponding 7 control samples are selected according to the specifications of the body 10, the specifications of the liquid inlet pipe 40, the number n of the branch pipes 30 and the specifications of the branch pipes 30. Two input mass flow conditions are analyzed for each sample.

[0111] The common parameters of the samples in the first mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 24 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 6.35 mm, the number of branches n = 2, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0112] The common parameters of the samples in the second mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 24 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 6.35 mm, the number of branches n = 3, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0113] The common parameters of the samples in the third mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 24 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 6.35 mm, the number of branches n = 5, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0114] The common parameters of the samples in the 4th mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 9.52 mm, the number of branches n = 3, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0115] The common parameters of the samples in the 5th mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 9.52 mm, the number of branches n = 5, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0116] The common parameters of the samples in the 6th mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 9.52 mm, the number of branches n = 7, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0117] The common parameters of the samples in the 7th mass flow analysis group and the corresponding control sample 1 are: the outer diameter of the main body D0 = 30 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 9.52 mm, the number of branches n = 10, the outer diameter of the branch pipe D2 = 3 mm, and the dryness is 0.35.

[0118] In the above 7 mass flow analysis groups, each sample is assigned to each branch mass flow M out All of them are less than or equal to 40 kg / h, which means they are all in low mass flow scenarios. The 14 simulation data sets from the above 7 mass flow analysis groups are summarized to form Table 2.

[0119] Analyzing the data in Table 2, we can get that: under low mass flow, the STD value and K value of each sample are smaller than the STD value and K value of the corresponding control sample 1; thus, we can get that: under low mass flow, the liquid separation uniformity of each sample is better than that of the corresponding control sample 1. Furthermore, looking at the K values ​​of all samples and control sample 1 in the mass flow analysis group, we find that the K value distribution of the samples is more concentrated, ranging from 0.88% to 3.38%, while the K value of control sample 1 is distributed between 3.62% and 7.89%. Thus, we can get that: under low mass flow scenario, this embodiment Figure 1 The sample structure shown (i.e. the new liquid-dispensing device) is superior to the Figure 20 The control sample shown is a structure (i.e., the existing pre-rectifying distributor structure).

[0120] Table 3 shows the simulation analysis data under low dryness and high mass flow. From Table 3, we can get: Under the low dryness and high mass flow scenario, this embodiment Figure 1 The new liquid-dispensing device shown is also superior to the Figure 20 The control sample is shown as 1.

[0121] The above simulation analysis data well verifies that the new liquid uniformity and liquid separation device provided in this embodiment can greatly improve the liquid separation performance, thereby effectively solving the problem that the existing distributor is difficult to evenly separate liquids in low dryness or low mass flow scenarios.

[0122] To further validate the performance of the new liquid-dispensing and balancing device provided in this embodiment, the inventors also applied it to experimental testing of an electrochemical energy storage system at a Changzhou-based thermal management system company. This test simulated real-world environmental conditions (such as the heat output of the liquid cooling plate and wind speed) to test and evaluate the thermal performance of the battery pack. The core objective was to verify the cooling system's ability to control battery temperature (e.g., maintaining the temperature difference between the inlet and outlet of the liquid cooling plate below the customer's desired setpoint).

[0123] In the field of electrochemical energy storage thermal management, batteries generate heat during the charging and discharging process. If the cooling system cannot remove the heat in a timely and uniform manner, a temperature gradient will appear inside the battery module (i.e., the battery temperatures at different locations are inconsistent). Excessive temperature gradients can lead to inconsistent battery performance: cells with high temperatures may reach their performance limits prematurely, while cells with low temperatures have not yet fully exerted their performance, thereby affecting the overall system efficiency. The liquid cooling plate is a heat exchange component that is in direct contact with the battery module. The temperature difference between its inlet and outlet is small, indicating that the refrigerant absorbs heat evenly in the liquid cooling plate. The surface temperature of the liquid cooling plate is evenly distributed, which helps to achieve a similar cooling effect throughout the battery module, thereby reducing the temperature gradient inside the battery and improving overall performance and safety.

[0124] In the experimental test of the electrochemical energy storage system of a Changzhou Thermal Management System Co., Ltd., the customer required that the temperature difference between the inlet and outlet of the liquid cooling plate be controlled within 1°C.

[0125] 1. Sample selection

[0126] Test sample: Figure 1 The new liquid equalizing and separating device shown is used as a sample structure to make a test sample with a main body outer diameter D0 = 30 mm, a liquid inlet pipe main section outer diameter D1 = 9.52 mm, a branch pipe number n = 5, and a branch pipe outer diameter D2 = 3 mm.

[0127] Control sample 1: Made according to the specifications of the test sample Figure 20 and Figure 20A The control samples shown are control sample 1 and control sample 2. Figure 20A It is a brass pressure drop type distributor commonly used on the market.

[0128] 2. Test installation steps

[0129] Test installation: Install the ends of the five branch pipes of the test sample at the refrigerant inlets of the five liquid cooling plates on the test unit; and install temperature sensors at the refrigerant inlet and refrigerant outlet of each liquid cooling plate.

[0130] Test steps: [1] Set the compressor frequency, valve opening, and fan speed according to the refrigeration system operating conditions; [2] Observe whether the superheat at the liquid cooling plate outlet meets the requirements, which are required to be ±0.5°C. After the superheat meets the requirements, the inlet and outlet temperature difference of each liquid cooling plate is monitored in real time through the temperature sensors at the refrigerant inlet and outlet of each liquid cooling plate. [3] After the monitoring data tends to be stable, the refrigerant inlet temperature and refrigerant outlet temperature of each liquid cooling plate are counted, and the corresponding inlet and outlet temperature difference is calculated.

[0131] Test conditions: Tests were conducted under the following three operating conditions: Operating condition 1: compressor frequency 40 rps (revolutions per second), valve opening 160°, fan speed 1790 rpm (revolutions per minute); Operating condition 2: compressor frequency 50 rps (revolutions per second), valve opening 190°, fan speed 1790 rpm (revolutions per minute); Operating condition 3: compressor frequency 60 rps (revolutions per second), valve opening 210°, fan speed 1790 rpm (revolutions per minute).

[0132] According to the above test installation steps, the test sample and two control samples were tested on the machine, and the test data were summarized to form Table 4. In Table 4, S refers to the standard deviation of the inlet and outlet temperature difference of the multi-channel liquid cooling plate under various working conditions. The calculation formula is as follows:

[0133]

[0134] in, is the average value of the temperature difference between the inlet and outlet of the multi-channel liquid cooling plate, t j is the temperature difference between the inlet and outlet of the j-th liquid cooling plate, and n is the number of liquid cooling plates, that is, the number of branches.

[0135] From Table 4 we can get:

[0136] ①Control sample 2 ( Figure 20A The existing brass pressure-drop distributor (shown in Figure 4) exhibits uneven liquid distribution under all three operating conditions, as indicated by the bolded sections in Table 4. In Condition 1, the inlet and outlet temperature differences (referred to as temperature differences in Table 4) between two cooling plates exceed the set value, resulting in uneven liquid distribution between the two channels. In Condition 2, the inlet and outlet temperature differences between one cooling plate exceed the set value, resulting in uneven liquid distribution between one channel. And in Condition 3, the inlet and outlet temperature differences between one cooling plate exceed the set value, resulting in uneven liquid distribution between the three channels.

[0137] ②Control sample 1 ( Figure 20 The pre-rectified distributor shown in Figure 4 has uneven liquid distribution under working condition 1 (as indicated by the bold mark in Table 4), while the liquid distribution uniformity is excellent under the other two working conditions. That is, the control sample 1 has uneven liquid distribution when the compressor speed is low (40rps). The low compressor speed corresponds to a low refrigerant mass flow rate distributed to each branch pipe, that is, Figure 20The control sample 1 (pre-rectified distributor) shown has the problem of uneven liquid distribution in low mass flow scenarios.

[0138] ③ The test sample provided in this embodiment has an inlet and outlet temperature difference of less than 0.5°C for each liquid cooling plate under three working conditions, which can well meet customer requirements (the inlet and outlet temperature difference is less than or equal to 1°C).

[0139] The above electrochemical energy storage system experimental test well reflects that the performance of the new liquid equalization and liquid separation device provided in this embodiment is far better than Figure 20 and Figure 20A The existing refrigerant distributor.

[0140] In the novel liquid balancing and liquid separation device provided in this embodiment, the liquid balancing assembly 20, the jet element 50 and the guide plate 60 divide the inner cavity of the body into four chambers. Specifically, Figure 1 As shown, the red dotted line between the upstream surface of the most upstream liquid balancing plate (i.e., the first liquid balancing plate 21) and the inner peripheral wall of the liquid inlet end of the body 10 is enclosed as a first chamber 101 that does not include the mixing chamber 11, and its volume is V1. The black dotted line between the downstream surface of the most downstream liquid balancing plate (i.e., the second liquid balancing plate 22) and the upstream surface of the jet element 50 is enclosed as a second chamber 102, and its volume is V2. The red dotted line between the plane where the downstream surface of the jet element 50 is located and the plane where the guide hole 601 on the guide plate 60 is located is enclosed as a third chamber 103, and its volume is V3. The black dotted line between the guide plate 60 and the inner peripheral wall of the liquid outlet end of the body 10 is enclosed as a fourth chamber 104, and its volume is V4.

[0141] In the gas-liquid two-phase refrigerant, the Froude number that characterizes the ratio of the inertial force of the liquid phase refrigerant to the gravity is greater than 7, which is a condition for the refrigerant to develop into a stable diffuse mist flow. The inertial force of the liquid phase refrigerant is related to its flow rate, and the flow rate is related to the volume of the chamber through which the refrigerant flows. In the CFD simulation analysis data shown in Tables 1 to 3, in the four chambers separated by the liquid balancing component 20, the jet component 50 and the guide plate 60, the volumes of the two adjacent chambers are basically close, and the volume ratio is between 0.95 and 1.1. In order to further improve the performance of the new liquid balancing and liquid separation device, the inventors based on Figure 1 The new liquid-distribution device shown is designed with the following analysis scheme to verify the effect of the volume change of adjacent chambers on the uniformity of refrigerant distribution.

[0142] 【1】The effect of chamber volume ratio on liquid separation uniformity was simulated and analyzed under the same dryness and different mass flow rates.

[0143] by Figure 1The new liquid-dispensing and dispensing device shown in the figure was used as a sample structure. The analysis sample consisted of a main body with an outer diameter D0 of 24 mm, a main inlet pipe with an outer diameter D1 of 6.35 mm, two branch pipes, and a branch pipe outer diameter D2 of 3 mm. The dryness was 0.35. The effects of different chamber ratios on liquid dispensing uniformity were analyzed under two mass flow rates.

[0144] The first chamber ratio analysis group: set the total mass flow rate M in 0=50Kg / h, set the mass flow rate M distributed to each branch out =25Kg / h, the liquid separation uniformity of the four chambers under six chamber ratios was analyzed.

[0145] The 2nd chamber ratio analysis group: set the total mass flow rate M in 0=80Kg / h, set the mass flow rate M distributed to each branch out =40Kg / h, the liquid separation uniformity of the four chambers under six chamber ratios was analyzed.

[0146] The above analysis data are summarized to form Table 5.

[0147] 【2】The effect of chamber volume ratio on liquid separation uniformity was simulated and analyzed under the same mass flow rate and different dryness.

[0148] by Figure 1 The new liquid-distributing device shown in the figure is used as the sample structure. The outer diameter of the main body D0 = 45 mm, the outer diameter of the main section of the liquid inlet pipe D1 = 16 mm, the number of branches n = 17, and the outer diameter of the branch pipe D2 = 3 mm are selected as the analysis sample. The total input mass flow rate M is set. in 0=595Kg / h, set the mass flow rate M distributed to each branch out =35Kg / h. Under two dryness conditions, the effect of different chamber ratios on liquid separation uniformity was analyzed.

[0149] The first chamber ratio analysis group: When the dryness is 0, the liquid distribution uniformity of the four chambers under six chamber ratios is analyzed.

[0150] Second chamber ratio analysis group: When the dryness is 0.35, the liquid distribution uniformity of the four chambers under six chamber ratios is analyzed.

[0151] The above analysis data are summarized to form Table 6.

[0152] Analysis of the data in Tables 5 and 6 reveals the following: ① Regardless of whether the refrigerant has the same dryness and different mass flow rates, or the same mass flow rate and different dryness, the volume ratio of the four chambers affects the uniformity of refrigerant separation. An excessively large downstream chamber volume will cause excessive refrigerant expansion, making it difficult for the inertial force of the liquid refrigerant to overcome gravity, resulting in a gas-liquid phase deviation. On the other hand, an excessively small downstream chamber volume will not provide sufficient mixing space for the refrigerant, preventing the two phases from fully mixing, also affecting liquid separation uniformity.

[0153] ② As shown in the bold data in Tables 5 and 6, when the ratio of adjacent chambers is within the range of 0.7 to 1.35, the K value of each sample is less than 3.5%. This performance is far superior to the optimal liquid separation performance of the control sample 1 (i.e., the existing pre-rectified distributor) in Tables 1, 2, and 3, which has an optimal liquid separation performance of K = 3.56%. Therefore, preferably, in this embodiment, the volume ratio between the upstream and downstream chambers of two adjacent chambers is within the range of 0.7 to 1.35. That is, 0.7 ≤ V1 / V2 ≤ 1.35, 0.7 ≤ V2 / V3 ≤ 1.35, and 0.7 ≤ V3 / V4 ≤ 1.35.

[0154] Figure 21 The figure shows a schematic structural diagram of a novel liquid-equalizing and liquid-separating device provided in another embodiment of the present invention. In this structure, the novel liquid-equalizing and liquid-separating device further includes a spacer 70 disposed between the guide plate 60 and the liquid outlet end of the main body 10. The spacer 70 is located on the inner periphery of the plurality of branch pipe holes 110, and a fourth chamber 104 is defined between the guide plate 60, the spacer 70, and the inner peripheral wall of the liquid outlet end of the main body 10. For novel liquid-equalizing and liquid-separating devices with a large number of branch pipes 30, the volume of the fourth chamber 104 can be controlled by adding the spacer 70 so that the volume ratio between the fourth chamber 104 and the third chamber 103 satisfies 0.7≤V3 / V4≤1.35.

[0155] Figure 21A This is a schematic diagram of the structure of a new type of liquid equalization and separation device provided by another embodiment of the present invention. Figure 1 Basically the same, the difference is: Figure 21A In the embodiment, the liquid balancing assembly 20 includes two groups of liquid balancing units. Figure 21AIn the embodiment, the counter-jet liquid equalizing component 20 includes four liquid equalizing plates, namely the first liquid equalizing plate 21, the second liquid equalizing plate 22, the third liquid equalizing plate 23 and the fourth liquid equalizing plate 24. The first liquid equalizing plate 21 and the second liquid equalizing plate 22 constitute the first liquid equalizing unit 20_1, and there are multiple groups of counter-jet channels between the two. The third liquid equalizing plate 23 and the fourth liquid equalizing plate 24 constitute the second liquid equalizing unit 20_2, and there are also multiple groups of counter-jet channels between the two. However, no counter-jet channel is formed between the second liquid equalizing plate 22 and the third liquid equalizing plate 23, and the axial spacing between the physical parts of the two is relatively large (greater than the axial spacing H0 between the physical parts of the two adjacent liquid equalizing plates that form the counter-jet channel). However, the present invention does not impose any limitation on this. In other embodiments, the axial spacing between the physical parts of the second liquid equalizing plate and the third liquid equalizing plate can also be controlled to form three-level counter-jet mixing between the four liquid equalizing plates.

[0156] Correspondingly, this embodiment also provides a heat exchange device, which includes the above-mentioned new liquid equalization and separation device and a heat exchanger assembly. The heat exchanger assembly can be a heat exchanger structure such as a fin heat exchanger, a shell and tube heat exchanger or a microchannel heat exchanger.

[0157] Correspondingly, this embodiment also provides a refrigeration system including the above-mentioned heat exchange device.

[0158] Example 2

[0159] This embodiment is substantially the same as the first embodiment and its variations, except that the connection method between adjacent equalizing plates in the opposing equalizing assembly 20 is different. In this embodiment, multiple equalizing plates are sequentially abutted, with a flow channel gap 210 between the solid portions of two adjacent equalizing plates.

[0160] Specifically, if Figure 22 、 Figure 23 as well as Figure 24 As shown, the first liquid balancing plate 21 also includes a middle portion 213 located on the periphery of the mixing chamber 1, and a plurality of solid portions 212 are circumferentially distributed around the middle portion 213. Similarly, the second liquid balancing plate 22 also includes a middle portion 223 located on the periphery of the mixing chamber 1, and a plurality of solid portions 222 are circumferentially distributed around the middle portion 223. The middle portions 213, 223 of the two liquid balancing plates are relatively raised and connected to each other so that a flow channel gap 210 is formed between the first liquid balancing plate solid portion 212 and the second liquid balancing plate solid portion 222. The structures of the two liquid balancing plates in this structure are exactly the same, and only the direction and angle of one of the liquid balancing plates need to be adjusted during assembly. However, the present invention does not impose any limitation on this. In other embodiments, only the middle portion of one of the liquid balancing plates may be raised, and the middle portion of the other liquid balancing plate may be a plane.

[0161] In other embodiments, if there are three liquid equalizing plates, a second liquid equalizing plate located in the middle can also be set as a flat plate structure with surfaces on both sides close to flat. The middle parts of the first liquid equalizing plate and the third liquid equalizing plate both protrude toward the second liquid equalizing plate and are connected to the second liquid equalizing plate, forming a flow channel gap between the solid parts of adjacent liquid equalizing plates.

[0162] Figure 25 and Figure 26 The figure shows a cross-beam liquid equalizing assembly provided by another embodiment of the present invention. In this structure, the end of the first liquid equalizing plate entity 212 is connected to the end of the second liquid equalizing plate entity 222, and a flow channel gap 210 is still formed between the two entities.

[0163] Figure 27 、 Figure 28 as well as Figure 29 The figure shows a counter-equalizing liquid assembly provided by another embodiment of the present invention. In this structure, ridges 204 are formed on the surface of the solid part of each equalizing liquid plate, and grooves 203 are formed between adjacent ridges 204. After the two equalizing liquid plates are overlapped and assembled, the ridges 204 on the first equalizing liquid plate and the ridges 204' on the second equalizing liquid plate are relatively abutted, the grooves 203 on the first equalizing liquid plate and the grooves 203' on the second equalizing liquid plate are opposite, and a flow channel gap 210 is formed between the two grooves. However, the present invention does not impose any limitation on this. In other embodiments, of the two adjacent equalizing liquid plates, only one of the equalizing liquid plates may be provided with ridges and grooves on its solid part, and the surface of the solid part of the other equalizing liquid plate may be flat; after the two equalizing liquid plates are overlapped, a flow channel gap is formed at the location of the grooves.

[0164] Example 3

[0165] This embodiment is basically the same as the first embodiment and its variations, except that the structure of the guide plate 60 is different.

[0166] like Figure 30 As shown, in this embodiment, the guide plate 60 is a flat plate. The upstream and downstream surfaces of the guide plate 60 opposite the jet holes 501 are both flat to reflect the high-speed refrigerant. The reflected refrigerant is then distributed to the corresponding branch pipe holes 110 through the multiple guide holes 601 on the guide plate 60 with equal resistance.

[0167] Figure 31 FIG2 is a schematic diagram of the structure of a novel liquid balancing and liquid separation device according to another embodiment of the present invention. In this structure, a spacer 70 is also provided between the guide plate 60 and the liquid outlet end of the body 10 for adjusting the volume of the fourth chamber 104 .

[0168] In summary, in the new liquid equalizing and liquid separating device provided by the present invention, the reflected mixing and the reflected mixing are integrated in the liquid equalizing component. On the basis of disturbing the input refrigerant flow pattern, the reflected mixing of the refrigerant is realized through multiple groups of reflected flow channels between adjacent liquid equalizing plates, thereby enhancing the turbulence of the two-phase refrigerant so that the refrigerant develops into a stable diffuse flow pattern. The refrigerant after the reflected mixing is collected at the jet hole on the jet component, and the speed is increased by throttling again through the jet hole, thereby increasing the refrigerant flow rate, suppressing the separation of the gas-liquid two-phase, and enhancing the reflected mixing degree of the refrigerant on the guide plate to ensure that the two-phase refrigerant is fully mixed. At the same time, a plurality of guide holes corresponding to the branch pipe holes are provided on the guide plate, so that each branch pipe hole has a basically similar distribution path. This setting makes the distribution path of the refrigerant after full mixing irrelevant to the number of refrigerant ports and their distribution positions on the liquid equalizing component, and the batch products have excellent repeatability; and for products of different specifications, it is only necessary to replace the guide plate to ensure the uniformity and repeatability of the refrigerant distribution.

[0169] Furthermore, the arrangement of the jet-equalizing assembly, jet element, and guide plate creates four chambers within the main body. By precisely controlling the volume ratio between adjacent chambers, the volume expansion of the refrigerant as it flows through them is controlled, preventing a reduction in refrigerant flow rate due to excessive expansion. This ensures high-speed refrigerant flow within each chamber, enhancing mixing while preventing gas-liquid phase segregation caused by reduced flow rate.

[0170] Although the present invention has been disclosed above by means of preferred embodiments, this is not intended to limit the present invention. Anyone skilled in the art may make slight changes and modifications 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 required by the claims.

[0171] Table 1

[0172]

[0173] Table 2

[0174]

[0175] Table 3

[0176]

[0177] Table 4

[0178]

[0179] Table 5

[0180]

[0181] Table 6

[0182]

Claims

1. A new type of liquid equalization and separation device, characterized in that: include: The main body and the opposing liquid equalizing components, the jet components and the guide plates are sequentially arranged in the inner cavity of the main body along the flow direction of the refrigerant; The counter-jet liquid equalizing component includes a mixing cavity body having a mixing cavity and a plurality of liquid equalizing plates. The plurality of liquid equalizing plates are sequentially arranged on the outer peripheral wall of the mixing cavity body along the axial direction of the main body. Each liquid equalizing plate includes a plurality of refrigerant ports circumferentially distributed around the mixing cavity and a solid portion located between adjacent refrigerant ports. Along the axial direction of the main body, each solid portion of the upper liquid equalizing plate of the two adjacent liquid equalizing plates covers the corresponding refrigerant port on the lower liquid equalizing plate, and overlaps with the projection of the solid portions on both sides of the corresponding refrigerant port of the lower liquid equalizing plate to form a group of counter-jet flow channels in which the refrigerants flow in opposite directions. The refrigerants reflected and mixed by the mixing cavity enter the plurality of counter-jet flow channels, and the refrigerants are counter-jet mixed in each group of counter-jet flow channels. The jet component has a jet hole, and the mixed refrigerant is collected in the jet hole; The guide plate has a plurality of guide holes corresponding to the branch pipe holes on the body. The plurality of guide holes are distributed in a ring shape around the axis of the body and on the periphery of the projection area of ​​the jet hole on the guide plate.

2. The novel liquid-distributing device according to claim 1, characterized in that: A first chamber excluding a mixing chamber is formed between the upstream liquid balancing plate and the inner circumferential wall of the liquid inlet end of the main body, a second chamber is formed between the downstream liquid balancing plate and the jet element, a third chamber is formed between the jet element and the plane where the guide holes on the guide plate are located, and a fourth chamber is formed between the guide plate and the inner circumferential wall of the liquid outlet end of the main body; in two adjacent chambers, the volume ratio of the upstream chamber to the downstream chamber is between 0.7 and 1.

35.

3. The novel liquid-distributing device according to claim 2, characterized in that: The novel liquid equalizing and separating device further comprises a spacer sleeve arranged between the guide plate and the liquid outlet end of the main body, and the spacer sleeve is located on the inner periphery of the plurality of branch pipe holes, and a fourth chamber is formed between the guide plate, the spacer sleeve and the inner peripheral wall of the liquid outlet end of the main body.

4. The novel liquid-distributing device according to claim 1, characterized in that: Among the multiple liquid balancing plates, in the two overlapping areas formed by the overlapping projections of the solid part of the upper liquid balancing plate and the solid parts on both sides of the corresponding refrigerant ports of the lower liquid balancing plate, the minimum width L0 of each overlapping area satisfies: 0.5mm≤L0≤3.5mm.

5. The novel liquid-distributing device according to claim 1, characterized in that: The axial spacing H0 between the solid parts of two adjacent liquid balancing plates satisfies 0<H0≤3mm.

6. The novel liquid-distributing device according to claim 1, characterized in that: The parts of the plurality of liquid balancing plates are in contact with each other in sequence, and there is a flow channel gap between the solid parts of two adjacent liquid balancing plates; Alternatively, a plurality of liquid balancing plates are distributed at intervals on the outer peripheral wall of the mixing cavity along the axial direction of the main body, so that a flow channel gap is formed between the solid parts of two adjacent liquid balancing plates.

7. The novel liquid-distributing device according to claim 6, characterized in that: The opposing liquid balancing assembly further comprises a limiting sleeve which is sheathed on the outer peripheral wall of the mixing chamber, and two adjacent liquid balancing plates abut against two ends of the limiting sleeve to be spaced apart.

8. The novel liquid-distributing device according to claim 1, characterized in that: The liquid balancing plate is an integral structure, and a connection hole is formed in the middle of the liquid balancing plate and is sleeved on the peripheral wall of the mixing chamber; Alternatively, the liquid balancing plate includes a plurality of independent solid parts, and the plurality of solid parts are distributed at intervals along the circumference of the mixing cavity and fixed to the outer peripheral wall of the mixing cavity.

9. The novel liquid-distributing device according to claim 1, characterized in that: Among the multiple liquid balancing plates, the most upstream liquid balancing plate is integrally formed with the mixing cavity; the other liquid balancing plates are connected to the peripheral wall of the mixing cavity or are sequentially connected to the most upstream liquid balancing plate.

10. The novel liquid equalization and liquid separation device according to claim 1, characterized in that: The refrigerant port is a notch groove that continuously extends along the radial direction of the liquid balancing plate to the edge of the liquid balancing plate. The notch groove is fan-shaped, rectangular or has a curved groove wall.

11. The novel liquid equalization and liquid separation device according to claim 1, characterized in that: The refrigerant port is one or more combinations of a through hole, a flange hole or an arc bubble hole.

12. The novel liquid-distributing device according to claim 1, characterized in that: The counter-jet liquid equalizing component includes more than three liquid equalizing plates, and multiple groups of counter-jet flow channels are formed between two adjacent liquid equalizing plates. The refrigerant is subjected to more than two levels of counter-jet mixing in the counter-jet liquid equalizing component.

13. The novel liquid equalization and liquid separation device according to claim 1, characterized in that: The counter-jet liquid averaging assembly includes a plurality of liquid averaging units, each of which includes at least two liquid averaging plates, and a plurality of counter-jet flow channels are formed between two adjacent liquid averaging plates; and no counter-jet flow channels are formed between adjacent liquid averaging units.

14. The novel liquid equalization and liquid separation device according to claim 1, characterized in that: On the guide plate, an area opposite to the jet hole protrudes and extends toward the liquid outlet end of the body, forming a reflective cavity with an opening facing the jet hole.

15. A heat exchange device, characterized in that: The invention comprises the novel liquid equalizing and liquid separating device as claimed in claim 1.

16. A refrigeration system, characterized in that: Including the heat exchange equipment according to claim 15.

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