Liquid separation partition plate and distributor

Abstract

The invention provides a liquid separation partition plate and a distributor. The liquid separation partition plate is arranged in the distributor and comprises a plurality of partition plates. The multiple partition plates are distributed in the axial direction of the distributor in a staggered mode, and each partition plate comprises a plurality of refrigerant ports distributed in the circumferential direction and solid parts located between the adjacent refrigerant ports. When the two adjacent partition plates are projected in the axial direction of the distributor, each entity part of the upper partition plate covers the corresponding refrigerant opening in the lower partition plate and is overlapped with the entity parts on the two sides of the corresponding refrigerant opening in the lower partition plate so as to form a set of opposite jet flow channels where refrigerants flow in the opposite directions, and the refrigerants are mixed in each set of opposite jet flow channels in an opposite mode.

Description

[0001] This application claims two priorities:

[0002] First priority information: Application number: 2025216581535, application date: August 5, 2025, invention title: liquid separator and dispenser.

[0003] Second priority information: Application No. 2025211113026, application date: May 30, 2025, invention title: priority of the prior application for a branch pipe end jet structure, distributor branch pipe and distributor. Technical Field

[0004] This invention relates to the field of refrigeration accessories, and particularly to a liquid separator and distributor. Background Technology

[0005] In refrigeration systems, a distributor is a device connected between the outlet of a thermostatic expansion valve and a multi-branch heat exchanger. It is used to evenly distribute the refrigerant, after being throttled by the expansion valve, into the multiple branches of the heat exchanger. Sieve-type distributors are widely used in existing refrigeration systems due to their simple structure and low cost. However, because some of the sieve holes are directly opposite the distributor's inlet pipe, the incoming refrigerant does not have enough time to mix before quickly passing through the opposite sieve holes to the outlet side for distribution. Therefore, this results in poor refrigerant distribution uniformity.

[0006] To address this issue, the inventors proposed a partition-type distributor, heat exchanger assembly, and refrigeration equipment with superior distribution uniformity in Chinese patent CN223077187U. In this design, multiple partition holes on the partition are misaligned with the inlet pipe, preventing the refrigerant from directly flowing to the outlet side. This solution effectively solves the problem of poor distribution uniformity caused by direct refrigerant flow. However, since the refrigerant only reflects off the partition before passing through the partition holes, the degree of reflection and mixing is affected by factors such as the inlet chamber pressure, refrigerant flow rate, and dryness fraction, thus limiting the improvement in distribution performance.

[0007] To further improve the mixing effect of refrigerant within the distributor, Chinese patent CN104457046A proposes installing swirl vanes within the distributor. The refrigerant, after being rectified by the spiral channels on the vanes, can significantly improve the mixing effect. However, spiral vanes are not only difficult to manufacture but also hard to apply to the relatively small size of the distributor body. Furthermore, Chinese patents CN217464979U and CN114963483A also propose installing impellers within the distributor, hoping to improve the refrigerant mixing effect through the impeller. However, in both impeller designs, the refrigerant is output axially along the blade surface, resulting in extremely limited mixing during transmission. Although in Chinese patent CN114963483A, the refrigerant, due to the obstruction of the curved blade surface, generates reflective vortices when impacting each curved blade, thus enhancing the mixing effect; however, this is different from the invention of the Chinese patent...

[0008] Similar to the baffle-type distributor proposed in CN223077187U, the mixing effect of the vortex is affected by factors such as refrigerant pressure, refrigerant flow rate, and dryness, making it difficult to effectively improve distribution performance. Furthermore, this impeller structure also suffers from problems such as difficult blade processing, high processing costs, and assembly difficulties, which greatly limit its application in distributors.

[0009] In addition to the main structure, the performance of the distributor is also affected by the local resistance loss at the bends in the branch pipes and the friction loss along the length, which gradually reduces the refrigerant flow rate. When the refrigerant flow rate is too low, the inertial force of the liquid refrigerant will be less than its gravity, causing the liquid refrigerant to separate from the gas phase due to gravity, thus seriously affecting the heat exchange performance. Summary of the Invention

[0010] In order to overcome the shortcomings of the prior art, the present invention provides a liquid separator and distributor that can promote the full mixing of two-phase refrigerants.

[0011] To achieve the above objectives, a first aspect of the present invention provides a liquid distribution baffle, which is disposed within a distributor and includes multiple baffles. The multiple baffles are staggered along the axial direction of the distributor, and each baffle includes multiple refrigerant ports distributed circumferentially and a solid portion located between adjacent refrigerant ports;

[0012] When two adjacent baffles are projected along the distributor axis, each solid part of the upper baffle covers the corresponding refrigerant port on the lower baffle and overlaps with the solid parts on both sides of the corresponding refrigerant port on the lower baffle to form a set of opposing jet channels for refrigerant flow. The refrigerant forms opposing jet mixing in each set of opposing jet channels.

[0013] According to an embodiment of the first aspect of the present invention, in the two overlapping areas formed by the projection overlap of the solid portion of the upper partition and the solid portions on both sides of the corresponding refrigerant inlet of the lower partition, the minimum width L0 of each overlapping area satisfies: 0.5mm≤L0≤3.5mm.

[0014] According to an embodiment of the first aspect of the present invention, a plurality of partitions are sequentially partially abutted to create a flow channel gap between the solid portions of two adjacent partitions.

[0015] According to an embodiment of the first aspect of the present invention, the partition further includes a central portion, and a plurality of solid portions are circumferentially distributed around the central portion; among the plurality of partitions, at least one partition has a central portion that protrudes and connects to the central portions of adjacent partitions, so that the solid portions of adjacent partitions are spaced apart.

[0016] According to an embodiment of the first aspect of the present invention, the liquid separation baffle further includes a connecting column, and multiple baffles are sequentially arranged on the connecting column along the axial direction, with adjacent baffles partially abutting each other to form a flow channel gap between the corresponding solid parts;

[0017] Alternatively, adjacent partitions can be spaced apart to create flow channel gaps between the corresponding solid parts.

[0018] According to an embodiment of the first aspect of the present invention, the partition is an integral structure, and a connecting hole for fitting onto the connecting post is formed in the middle of the partition;

[0019] Alternatively, the partition may comprise multiple independent solid parts, which are distributed at circumferential intervals along the connecting column and fixed to the connecting column.

[0020] According to an embodiment of the first aspect of the present invention, the liquid separation partition further includes a limiting sleeve sleeve fitted over the connecting column, with two adjacent partitions abutting the two ends of the limiting sleeve at intervals.

[0021] According to an embodiment of the first aspect of the present invention, the axial distance H0 between two adjacent partition solid portions satisfies 0 < H0 ≤ 3 mm.

[0022] According to an embodiment of the first aspect of the present invention, the refrigerant inlet is a notch or groove that extends radially and continuously to the edge of the partition, and the notch or groove is fan-shaped, rectangular, or has a curved surface.

[0023] According to an embodiment of the first aspect of the present invention, the refrigerant port is one or more combinations of a through hole, a flanged hole, or an arc bubble hole.

[0024] According to an embodiment of the first aspect of the present invention, the liquid separator includes three or more separators, and multiple sets of anti-jet flow channels are formed between adjacent separators, and the refrigerant undergoes two or more stages of anti-jet mixing within the liquid separator.

[0025] According to an embodiment of the first aspect of the present invention, the liquid separation baffle includes a plurality of opposing jet units, each opposing jet unit including at least two baffles and multiple sets of opposing jet channels are formed between adjacent two baffles; however, opposing jet channels are not formed between adjacent opposing jet units.

[0026] A second aspect of the present invention also provides a dispenser, which includes a dispenser body and the aforementioned liquid separation baffles. The liquid separation baffles are disposed within the dispenser body, and the edge of each baffle substantially abuts against the inner peripheral wall of the dispenser body.

[0027] According to an embodiment of the second aspect of the present invention, the distributor further includes multiple branch pipes welded to the liquid outlet end of the distributor body. At least one branch pipe includes a branch pipe body and a branch pipe end jet structure disposed downstream of the branch pipe body. The branch pipe end jet structure includes a transmission pipe section, an assembly pipe section, and a jet section. The transmission pipe section is disposed downstream of the branch pipe body, and the jet section is disposed near or downstream of the downstream end of the transmission pipe section to accelerate the refrigerant. A jet throat is formed at the minimum inner diameter of the jet section. The inner diameter of the jet throat is smaller than the inner diameter at the downstream end of the transmission pipe section, and the difference Δd between the inner diameter of the jet throat and the inner diameter at the downstream end of the transmission pipe section satisfies: 0.03mm≤Δd≤1.65mm, and the axial length L1 of the jet section ≤350mm. The upstream end of the assembly pipe section is connected to the transmission pipe section or the jet section, and the outer diameter of the downstream end of the assembly pipe section is larger than the outer diameter of the transmission pipe section to match the welding of external pipelines.

[0028] According to an embodiment of the second aspect of the present invention, the axial length L2 of the assembled pipe section is ≤35mm, and the axial length of the assembled pipe section refers to the total axial length from its upstream end face to its downstream end face.

[0029] According to an embodiment of the second aspect of the present invention, the assembly pipe section is integrally formed at the downstream end of the transmission pipe section, and the jet section is embedded and welded to the downstream end of the transmission pipe section or inside the assembly pipe section.

[0030] According to an embodiment of the second aspect of the present invention, the jet section is a jet pipe embedded in the assembly pipe section and welded to the downstream end of the transmission pipe section;

[0031] Alternatively, the jet section is a jet orifice plate, which is embedded and welded to the downstream end of the transmission pipe section or inside the assembly pipe section. Jet holes are formed on the jet orifice plate, and the jet throat is formed at the minimum inner diameter of the jet holes.

[0032] According to an embodiment of the second aspect of the present invention, the assembly pipe section is welded to the downstream end of the transmission pipe section, and the jet section is disposed at the downstream end of the transmission pipe section or embedded in the assembly pipe section.

[0033] According to an embodiment of a second aspect of the present invention, the jetting part is a jetting nozzle integrally formed or welded to the downstream end of the transmission pipe section, the jetting nozzle extending into the assembly pipe section and its downstream end forming a jetting throat.

[0034] According to an embodiment of the second aspect of the present invention, the jet section is embedded near the downstream end of the transmission pipe section or embedded in the assembly pipe section. The jet section is a jet pipe or a jet orifice plate, and a jet hole is formed on the jet orifice plate, with a jet throat formed at the minimum inner diameter of the jet hole.

[0035] According to an embodiment of a second aspect of the present invention, the jet hole is a flanged hole whose wall extends in the direction of the downstream end of the assembly pipe section, and a jet throat is formed at the downstream end of the flanged hole.

[0036] According to an embodiment of the second aspect of the present invention, the jet hole is a through hole formed based on the axial thickness of the jet hole plate, and the jet hole is a constant diameter hole with a substantially unchanged diameter.

[0037] Alternatively, the jet orifice includes a jet throat and a guide orifice section, with the guide orifice section located upstream of the jet throat and having a larger orifice diameter than the jet throat.

[0038] Alternatively, the jet orifice is a Venturi orifice, which includes a guide orifice section, a jet throat, and a diffuser orifice section distributed sequentially along the direction of refrigerant flow. The orifice diameters of the guide orifice section and the diffuser orifice section are both larger than the orifice diameter at the jet throat.

[0039] According to an embodiment of a second aspect of the present invention, the jet section is a jet pipe, with its upstream end connected to a transmission pipe section and its downstream end connected to an assembly pipe section.

[0040] According to an embodiment of the second aspect of the present invention, the transmission pipe section, the jet section and the assembly pipe section are distributed sequentially along the refrigerant transmission direction and are integrally formed.

[0041] According to an embodiment of a second aspect of the present invention, the branch pipe end jet structure further includes an outer bushing welded to the assembly pipe section, the outer bushing being configured to increase the outer diameter at the assembly pipe section to match the welding of the external pipeline.

[0042] According to an embodiment of the second aspect of the present invention, the distributor further includes multiple branch pipes welded to the liquid outlet end of the distributor body. At least one branch pipe includes a branch pipe body and a branch pipe end jet structure disposed downstream of the branch pipe body. The branch pipe end jet structure includes a transmission pipe section, an assembly pipe section, and a jet section. The transmission pipe section is disposed downstream of the branch pipe body, and the assembly pipe section is disposed downstream of the transmission pipe section to match the welding of external pipelines. The jet section is disposed downstream of the assembly pipe section or embedded in the assembly pipe section. A jet throat is formed at the minimum inner diameter of the jet section. The inner diameter of the jet throat is smaller than the inner diameter at the downstream end of the transmission pipe section and the inner diameter of the assembly section on the assembly pipe section, respectively. The difference Δd between the inner diameter of the jet throat and the inner diameter at the downstream end of the transmission pipe section satisfies: 0.03mm≤Δd≤1.65mm, and the axial length L1 of the jet section ≤350mm.

[0043] According to an embodiment of a second aspect of the present invention, the transmission pipe section, the assembly pipe section, and the jet section are arranged sequentially along the transmission direction of the refrigerant and are integrally formed.

[0044] In summary, the liquid distribution baffle provided by this invention comprises multiple baffles staggered along the axial direction of the distributor. Adjacent baffles are configured such that each solid portion of the upper baffle not only covers the corresponding refrigerant port on the lower baffle but also overlaps with the projected solid portions on both sides of the refrigerant port, thereby forming a set of opposing jet flow channels in the two overlapping areas. The refrigerant, after being throttled and accelerated through the refrigerant port of the upper baffle, enters the multiple sets of opposing jet flow channels between adjacent baffles. Within each set of opposing jet flow channels, the high-speed refrigerant flowing in opposite directions collides and forms turbulence, enhancing the turbulence of the two-phase flow and allowing it to develop into a stable, diffused mist flow, thereby significantly improving the uniformity and stability of the two-phase refrigerant distribution. Furthermore, by controlling the axial spacing between the solid portions of adjacent baffles, a collision and mixing space is provided for the refrigerant within the opposing jet flow channels while preventing refrigerant expansion due to excessively large flow channels, ensuring continuous high-speed convection of the refrigerant and improving the effect of opposing jet mixing.

[0045] Furthermore, for the distributor branch pipe, a branch pipe end jet structure is installed at its downstream end. The high-speed jet from the narrower inner diameter jet section effectively eliminates the gas-liquid two-phase separation phenomenon caused by local resistance loss, friction loss, and refrigerant expansion during refrigerant transmission through the branch pipe. This ensures the refrigerant is output to the downstream heat exchange components in a fully mixed, dispersed flow pattern, thereby improving heat exchange efficiency. Simultaneously, the jet section significantly increases the kinetic energy of the gas-liquid two-phase refrigerant to overcome the flow resistance generated by the refrigerant's volume expansion due to phase change in the downstream heat exchange tubes. This ensures the uniformity of refrigerant distribution is unaffected by differences in downstream heat exchange capacity, ensuring a consistently uniform distribution to all heat exchange tubes, thus improving system heat exchange efficiency. Additionally, since the downstream end of the branch pipe is connected to the downstream heat exchange components, the cooling capacity generated by some liquid refrigerant flash evaporation during the jet section's pressure reduction and acceleration process can also be utilized by the heat exchange components, further improving heat exchange efficiency. By setting a larger outer diameter assembly pipe section at the downstream end of the transmission pipe section or on the jet section, the design of the transmission pipe section and the jet section only needs to meet the requirements of the downstream heat exchange components for refrigerant transmission performance without having to consider assembly issues, ensuring that the distributor branch pipe can simultaneously meet the dual requirements of refrigerant transmission performance and welding assembly.

[0046] 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

[0047] Figure 1 The diagram shown is a schematic diagram of the liquid separation partition provided in Embodiment 1 of the present invention.

[0048] Figure 2 As shown Figure 1 A projection diagram.

[0049] Figure 3 As shown Figure 2 A cross-sectional view along line AA.

[0050] Figure 4 As shown Figure 1 A structural diagram from another perspective.

[0051] Figure 5 The image shows the refrigerant in... Figure 1 The diagram shows the flow pattern in the separatory plate.

[0052] Figure 6 As shown Figure 1 A projection diagram from another perspective.

[0053] Figure 7 The diagram shown is a schematic diagram of the liquid separation partition provided in another embodiment of the present invention.

[0054] Figure 8 As shown Figure 7 A cross-sectional schematic diagram.

[0055] Figure 9 The diagram shown is a schematic diagram of the liquid separation partition provided in another embodiment of the present invention.

[0056] Figure 10 As shown Figure 9 A cross-sectional schematic diagram.

[0057] Figure 11 The diagram shown is a schematic diagram of the liquid separation partition provided in another embodiment of the present invention.

[0058] Figure 12 The diagram shown is a schematic diagram of the liquid separation partition provided in another embodiment of the present invention.

[0059] Figure 13 The diagram shown is a schematic diagram of the liquid separation partition provided in another embodiment of the present invention.

[0060] Figure 14 As shown Figure 13 A cross-sectional schematic diagram.

[0061] Figure 15 As shown Figure 14 Enlarged diagram of point B in the middle.

[0062] Figure 16 The diagram shown is a schematic diagram of the distributor provided in Embodiment 1 of the present invention.

[0063] Figure 17 The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0064] Figure 17A The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0065] Figure 18 As shown Figure 16 A schematic diagram of the jet structure at the end of the middle branch pipe.

[0066] Figure 19 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0067] Figure 20 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0068] Figure 21 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0069] Figure 22 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0070] Figure 23 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0071] Figure 24 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0072] Figure 25 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0073] Figure 26 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0074] Figure 27 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0075] Figure 28 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0076] Figure 29 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0077] Figure 30 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0078] Figure 31 The diagram shown is a structural schematic of an existing brass impeller type distributor.

[0079] Figure 32 The diagram shown is a schematic diagram of the liquid separation partition provided in Embodiment 2 of the present invention.

[0080] Figure 33 As shown Figure 32 A structural diagram from another perspective.

[0081] Figure 34 As shown Figure 32 A cross-sectional schematic diagram.

[0082] Figure 35 The diagram shown is a schematic diagram of the liquid separation partition provided in another embodiment of the present invention.

[0083] Figure 36 As shown Figure 35 A cross-sectional schematic diagram.

[0084] Figure 37 The diagram shown is a cross-sectional view of a liquid separator provided in another embodiment of the present invention.

[0085] Figure 38 The diagram shown is a schematic diagram of the distributor provided in Embodiment 2 of the present invention.

[0086] Figure 39 The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0087] Figure 40 The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0088] Figure 41 The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0089] Figure 42 The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0090] Figure 43 The diagram shown is a schematic diagram of the distributor provided in another embodiment of the present invention.

[0091] Figure 44 The diagram shown is a schematic diagram of the distributor provided in Embodiment 3 of the present invention.

[0092] Figure 45 As shown Figure 44 A structural diagram from another perspective.

[0093] Figure 46 The diagram shown is a cross-sectional view of a liquid separator provided in another embodiment of the present invention.

[0094] Figure 47 The diagram shown is a cross-sectional view of a liquid separator provided in another embodiment of the present invention.

[0095] Figure 48 As shown Figure 47 A schematic diagram of the integrally formed connecting column and the first partition plate.

[0096] Figure 49 The diagram shown is a schematic diagram of the jet structure at the end of the branch pipe in Embodiment 4 of the present invention.

[0097] Figure 50 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0098] Figure 51 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0099] Figure 52 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0100] Figure 53 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0101] Figure 54 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0102] Figure 55 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0103] Figure 56 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0104] Figure 57 The diagram shown is a schematic diagram of the branch pipe end jet structure provided in Embodiment 5 of the present invention.

[0105] Figure 58 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0106] Figure 59 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0107] Figure 60 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0108] Figure 61 The diagram shown is a partial schematic of the branch pipe provided in Embodiment Six of the present invention.

[0109] Figure 62 As shown Figure 61 A schematic diagram of the jet structure at the end of the middle branch pipe.

[0110] Figure 63 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0111] Figure 64 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0112] Figure 65 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0113] Figure 66 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0114] Figure 67 The diagram shown is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention.

[0115] Figure 68 The diagram shown is a structural schematic of a branch pipe provided in another embodiment of the present invention. Detailed Implementation

[0116] Example 1

[0117] In existing refrigerant distributors, baffle-type and some impeller-type distributors rely on reflection to create vortices to enhance the mixing uniformity of two-phase refrigerants. However, the reflection mixing effect is greatly affected by refrigerant parameters (such as refrigerant pressure, mass flow rate, and dryness fraction), and it is still difficult to effectively improve the liquid separation performance in low dryness fraction and low mass flow rate situations. Moreover, the impeller-type structure also suffers from problems such as structural complexity and high manufacturing difficulty. In the swirl blade structure, the refrigerant can improve the mixing effect after being rectified by the spiral channel, but it also suffers from structural complexity and manufacturing difficulties.

[0118] In view of this, this embodiment provides a liquid-distributing baffle and distributor with excellent mixing effect and simple structure. The liquid-distributing baffle provided in this embodiment includes multiple baffles staggered along the axial direction of the distributor. Each baffle includes multiple refrigerant ports distributed circumferentially and a solid portion located between adjacent refrigerant ports. When two adjacent baffles are projected along the axial direction of the distributor, each solid portion of the upper baffle covers the corresponding refrigerant port on the lower baffle and overlaps with the solid portions on both sides of the corresponding refrigerant port on the lower baffle to form a set of opposing jet flow channels for refrigerant flow. The refrigerant forms opposing jet mixing in each set of opposing jet flow channels.

[0119] like Figure 1 , Figure 2 as well as Figure 3As shown, the liquid separation baffle 20 provided in this embodiment includes two baffles, namely a first baffle 21 and a second baffle 22. Divided along the refrigerant flow direction, the first baffle 21 is the upper baffle, and the second baffle 22 is the lower baffle. The first baffle 21 has multiple refrigerant ports 211 and multiple solid portions 212 located between adjacent refrigerant ports; similarly, the second baffle 22 has multiple refrigerant ports 221 and multiple solid portions 222 located between adjacent refrigerant ports. Specifically, the two baffles are staggered, with the middle region of the solid portion 212 of the first baffle covering the corresponding refrigerant port 221 on the second baffle 22, and its two side regions respectively overlapping the projection of the solid portion 222 of the second baffle, thereby forming a set of opposing flow channels 200 including a first flow channel 201 and a second flow channel 202. The refrigerant flows in opposite directions within each set of opposing flow channels 200 to achieve opposing mixing.

[0120] In this embodiment, each partition includes three refrigerant inlets and three solid portions. Three independent sets of opposing flow channels 200 are formed between two partitions, and each set of opposing flow channels 200 includes a first flow channel 201 and a second flow channel 202. However, the present invention does not impose any limitations on this. In other embodiments, the number of solid portions and refrigerant inlets on the partition may also be two or more other integers.

[0121] Each refrigerant port 211 on the first partition 21 is connected to two sets of opposing jet channels located on both sides. Figure 5 A schematic diagram showing the flow of refrigerant after it enters the separator 20 is provided. The arrows in the diagram indicate the flow direction. For ease of description, [the diagram is omitted here]. Figure 4 and Figure 5 The three adjacent refrigerant ports on the first partition 21 are defined as 211b, 211a, and 211c. Figure 4 and Figure 5 Taking the refrigerant inlet 211a on the first partition 21 as an example, it has two adjacent refrigerant inlets 211b and 211c. Part of the refrigerant input from refrigerant inlet 211a flows into the first channel 201 of the anti-jet flow channel 200, while the other part enters the second channel 202' of the anti-jet flow channel 200'. The refrigerant entering the first channel 201 mixes with the refrigerant in the second channel 202 (from refrigerant inlet 211b) within the anti-jet flow channel 200. Correspondingly, the refrigerant entering the second channel 202' mixes with the refrigerant in the first channel 201' (from refrigerant inlet 211c) within another set of anti-jet flow channels 200'. And so on, on the first partition 21, the refrigerant input from adjacent refrigerant inlets 211 mixes with the refrigerant in the corresponding anti-jet flow channels before being output from the corresponding refrigerant inlet 221 on the second partition.

[0122] In the liquid-distributing baffle 20 provided in this embodiment, refrigerant enters from multiple refrigerant ports 211 on the first baffle 21. After being throttled and accelerated by the refrigerant ports 211 into high-speed refrigerant, it is injected into each set of opposing flow channels 200. Within each set of opposing flow channels 200, the high-speed refrigerant flows towards each other, and after impact collision, turbulence is formed. The liquid film gradually thins and is broken into fine droplets, which are then uniformly dispersed into the gas phase refrigerant, and the refrigerant gradually develops into a diffuse flow pattern. In this embodiment, the multiple sets of opposing flow channels 200 are independent of each other. After the refrigerant enters the liquid-distributing baffle 20, it is divided into multiple flow paths. The refrigerant in each flow path is mixed in the corresponding opposing flow channel 200 to form a diffuse mist flow, thereby achieving uniform and stable distribution of the refrigerant.

[0123] In existing reflective mixing distributors (such as baffle or impeller types), the intensity of reflective mixing depends only on the kinetic energy of the incident refrigerant; however, in this embodiment, the intensity of jet mixing is related to the sum of the kinetic energies of the two opposing refrigerant streams. Clearly, under the same operating conditions, jet mixing will significantly increase the turbulence of the two-phase flow, thereby promoting thorough mixing of the gas and liquid refrigerants.

[0124] Although this embodiment is described using a liquid separator 20 comprising two separators as an example, the present invention does not limit this. In other embodiments, such as Figure 7 and Figure 8 As shown, the liquid separation baffle 20 may also include three baffles: a first baffle 21, a second baffle 22, and a third baffle 23. A primary through-jet mixing structure 200a is formed between the first baffle 21 and the second baffle 22, and the 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 baffle 22 and the third baffle 23, and the secondary through-jet mixing structure 200b has multiple sets of secondary through-jet flow channels. Similar to this embodiment, in the primary through-jet mixing structure 200a, the first baffle 21 is the upper baffle, and the second baffle 22 is the lower baffle. The refrigerant enters the multiple sets of through-jet flow channels 200 located between the two baffles through multiple refrigerant ports 211 on the first baffle 21, and after through-jet mixing, enters the multiple refrigerant ports 221 on the second baffle 22, i.e., enters the secondary through-jet mixing structure 200b. In the two-stage through-jet mixing structure 200b, the second partition 22 serves as the upper partition, and the third partition 23 serves as the lower partition. The middle region of the solid portion 222 on the second partition covers the corresponding refrigerant port 231 on the third partition 23, and its two side regions overlap with the projection of the solid portion 232 of the third partition, thereby forming multiple sets of two-stage through-jet flow channels 200, including the first flow channel 201 and the second flow channel 202. The refrigerant enters the multiple sets of through-jet flow channels 200 through the multiple refrigerant ports 221 on the second partition 22, and after through-jet mixing, it is output from the multiple refrigerant ports 231 on the third partition 23. This structure performs two-stage through-jet mixing of the refrigerant.

[0125] exist Figure 9 and Figure 10 In this structure, the liquid-dispensing baffle 20 includes four baffles: a first baffle 21, a second baffle 22, a third baffle 23, and a fourth baffle 24. Multiple sets of primary jet flow channels are formed between the first baffle 21 and the second baffle 22; multiple sets of secondary jet flow channels are formed between the second baffle 22 and the third baffle 23; and multiple sets of tertiary jet flow channels are formed between the third baffle 23 and the fourth baffle 24. This liquid-dispensing baffle structure enables three-stage jet mixing of the refrigerant. Figures 7 to 10 Similarly, in other embodiments, the liquid separation partition may include five or more partitions.

[0126] like Figure 11 As shown, this embodiment also provides another liquid separation baffle structure, which also includes four baffles, but the axial distance between the solid parts of the second baffle 22 and the third baffle 23 is larger (greater than the axial distance H0 between the solid parts of two adjacent baffles forming the jet channel), and no jet channel is formed between the second baffle 22 and the third baffle 23. Figure 11 In this configuration, the first partition 21 and the second partition 22 form a pair of jet units 2_1, with multiple sets of jet channels between them; the third partition 23 and the fourth partition 24 form another pair of jet units 2_2. The axial distance between the solid portions of adjacent partitions (i.e., the second partition 22 and the third partition 23) between two jet units 2_1 and 2_2 is relatively large (greater than the axial distance H0 between the solid portions of adjacent partitions forming jet channels), so that no jet channel is formed between the two jet units. This liquid-distributing partition structure performs two-stage jet mixing of the refrigerant. Similarly, when there are five partitions, three adjacent partitions can form a group of jet units with two-stage jet mixing; while the other two can form another jet unit with one-stage jet mixing; again, no jet channel is formed between adjacent jet units. In other embodiments, when the number of partitions is six or more, the liquid-distributing partition may also include three or more jet units.

[0127] Figure 6 As shown Figure 1 In the top-down projection diagram, the area between adjacent red lines is the refrigerant inlet 211 on the first partition, the area between adjacent dashed lines is the refrigerant inlet 221 on the second partition, and the shaded area is the overlapping area formed by the projection of the solid part 212 of the upper partition (i.e., the first partition 21) and the solid parts 222 on both sides of the corresponding refrigerant inlet 221 of the lower partition (i.e., the second partition 22).

[0128] In this embodiment, the minimum width L0 of each overlapping area is set to satisfy: 0.5mm ≤ L0 ≤ 3.5mm. The lower limit of the minimum width L0 determines the dimensions of the two sides of the first partition body 212, 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 partitions, providing space for the refrigerant to mix. Furthermore, since the radial dimension of the partition is limited by the inner cavity of the distributor, preferably, the outer diameter of the partition is approximately close to the inner cavity diameter of the distributor body. For a partition of a defined size, the upper limit of the minimum width L0 is related not only to the circumferential dimension of the jet flow channel 200, but also to the flow cross-sectional area of ​​the refrigerant port 211 on the first partition 21. The larger the upper limit of the minimum width L0, the larger the circumferential dimension of the jet flow channel 200 and the smaller the flow cross-sectional area of ​​the refrigerant port 211 on the first partition, 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 reciprocating mixing process, and 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 1.5 mm. 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 0.8 mm, 1.13 mm, 1.5 mm, 1.83 mm, 2 mm, 2.25 mm, 2.5 mm, and 3.0 mm.

[0129] In this embodiment, both the first partition refrigerant inlet 211 and the second partition refrigerant inlet 221 are radially continuous notches extending to the edge of the partition, and the notches are fan-shaped. Correspondingly, the first partition solid portion 212 and the second partition solid portion 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 partition. However, the shape of the refrigerant inlet is not limited in any way. In other embodiments, the refrigerant inlet may also be a rectangular notch or a notch with curved walls. In other embodiments, the refrigerant inlet may also be perforated, such as one or more combinations of through holes, flanged holes, or arc-shaped holes, and the outline of the perforated refrigerant inlet may be circular, elliptical, or fan-shaped. For example, both the first partition refrigerant inlet and the second partition refrigerant inlet may be through holes, or both refrigerant inlets on the two partitions may be flanged holes.

[0130] Although this embodiment uses two adjacent partitions with identical structures and both refrigerant inlets in a fan-shaped notch pattern as an example, the present invention does not limit this. In other embodiments, the refrigerant inlet structures of adjacent partitions may also be different. For example... Figure 12 As shown, the refrigerant port 211 on the first partition 21 is a through hole, while the refrigerant port 221 on the second partition 22 is a fan-shaped notch.

[0131] In the liquid separation baffle 20 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 of the refrigerant is positively correlated with its flow velocity (i.e., the higher the flow velocity, the better the jetting mixing effect). During the flow of the refrigerant, its flow velocity is inevitably affected by factors such as flow resistance and its volume change. To improve the jetting mixing effect, this embodiment first throttles and accelerates the refrigerant through the refrigerant inlet 211 on the first baffle. Based on this, as... Figure 3 As shown, by controlling the axial distance H0 between the first partition body 212 and the second partition body 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, which would lead to 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.

[0132] In this embodiment, both the first partition 21 and the second partition 22 are integral structures, with adjacent partitions partially abutting each other to create a flow channel gap 210 between their solid portions. Based on this flow channel gap 210, an inter-flow channel 200 is formed in the overlapping area of ​​the solid portions of the adjacent partitions. Figure 2 and Figure 3 As shown, the first partition 21 also includes a central portion 213, with multiple solid portions 212 circumferentially distributed around the central portion 213. Similarly, the second partition 22 also includes a central portion 223, with multiple solid portions 222 circumferentially distributed around the central portion 223. The central portions 213 and 223 of the two partitions are relatively protruding and interconnected, so that a flow channel gap 210 is formed between the solid portions 212 of the first partition and the solid portions 222 of the second partition. In this structure, the structures of the two partitions are completely identical, and only the direction and angle of one partition need to be adjusted during assembly. However, the present invention does not limit this in any way. In other embodiments, only the central portion of one partition may be protruding, while the central portion of the other partition may be a plane.

[0133] In other embodiments, if there are three partitions, the second partition 22 located in the middle can also be a flat plate structure with both sides nearly flat. The middle portion 213 of the first partition and the middle portion 233 of the third partition both protrude towards the second partition 22 and are connected to the middle portion 223 of the second partition, forming a flow channel gap 210 between the solid portions of adjacent partitions. Figure 7 and Figure 8 As shown. Alternatively, when the number of partitions is... Figure 9 and Figure 10 When there are four partitions, the middle part 213 of the first partition and the middle part 223 of the second partition can be set to protrude and abut against each other so that a flow channel gap 210 is formed between their solid parts; the second partition 22 and the third partition 23 are separated by a limiting sleeve 25 so that a flow channel gap 210 is formed between their solid parts; the third partition 23 and the fourth partition 24 form a flow channel gap 210 by abutting each other through the protrusion of the middle part.

[0134] In this embodiment, both the first partition body 221 and the second partition body 222 are plate structures with nearly flat surfaces on both sides. However, the present invention does not limit this in any way. In other embodiments, such as Figures 13 to 15 As shown, each partition plate has a raised ridge 204 formed on its solid surface, and a groove 203 is formed between adjacent raised ridges 204. After the two partition plates are stacked and assembled, the raised ridges 204 on the first partition plate and the raised ridges 204' on the second partition plate abut against each other, and the grooves 203 on the first partition plate and the grooves 203' on the second partition plate face each other, forming a flow channel gap 210 between the two grooves. However, the present invention does not limit this in any way. In other embodiments, in two adjacent partition plates, only one partition plate may have raised ridges and grooves formed on its solid surface, while the solid surface of the other partition plate may be flat; after the two partition plates are stacked, a flow channel gap is formed at the location of the groove.

[0135] Correspondingly, such as Figure 16 As shown, this embodiment also provides a distributor, which includes a distributor body 10, an inlet pipe 40 connected to the liquid inlet side of the distributor body 10, multiple branch pipes 30 connected to the liquid outlet side of the distributor body 10, and a liquid separating baffle 20 provided in this embodiment. The liquid separating baffle 20 is disposed within the distributor body 10, and the edge of each baffle substantially abuts against the inner peripheral wall of the distributor body 10. However, the present invention does not impose any limitations on this. In other embodiments, the liquid separating baffle provided in this embodiment may also be combined with other distributor components and disposed within the distributor body. Figure 17 As shown, the distributor also includes a guide cone 50 disposed within the distributor body 10 and located downstream of the liquid separation baffle 20; or, as Figure 17A As shown, the dispenser also includes a septum 60 disposed within the dispenser body 10 and located downstream of the liquid separation septum 20.

[0136] like Figure 16 As shown, although this embodiment is described using the distributor body 10 including a stretching cylinder 101, an end cap 102, and an end plate 103 as an example, the present invention does not limit this in any way. In other embodiments, the distributor body may also be an integral structure with a dispensing cavity formed by turning or casting; or it may include a main structure formed by turning or casting and an end plate, with the main structure and the end plate surrounding the dispensing cavity.

[0137] Besides the main structure, the performance of the distributor is also affected by the resistance within the branch pipes, leading to gas-liquid separation. To improve the transmission performance of the two-phase refrigerant within the distributor's branch pipes, Chinese patent CN118960259A proposes setting an acceleration section in the middle of the branch pipe, while Chinese patent CN210486186U proposes installing a sonic nozzle in the distribution chamber. However, in practical applications, it has been found that these two solutions are still difficult to effectively improve heat exchange performance when the branch pipe length is long or the refrigerant dryness is high. After conducting extensive experiments and analyses, the inventors discovered that when the branch pipe is short and the refrigerant dryness is low, the refrigerant accelerated in the distribution chamber or the middle of the branch pipe does not have enough time to separate before quickly entering the downstream heat exchange components to improve heat exchange performance. However, when the branch pipe is long, the dryness is high, or there is a bend downstream of the acceleration section, the accelerated refrigerant is still affected by local resistance loss and / or friction loss, reducing the refrigerant flow rate input to the heat exchange components. In addition, the distribution uniformity of the distributor is also gradually deteriorated by the difference in heat exchange capacity of each heat exchange tube in the downstream heat exchange components. Research has found that the heat exchange capacity of each heat exchange tube varies due to the distribution of the airflow within the heat exchange components. In tubes with strong heat exchange capacity, the liquid phase of the two-phase refrigerant rapidly transforms into a large-volume gas phase after entering. Limited by the internal space, the expanding gas phase inevitably compresses the incoming refrigerant, causing flow resistance. Stronger heat exchange results in faster phase change, greater flow resistance, and less refrigerant flowing in. Conversely, tubes with weak heat exchange capacity receive more refrigerant due to lower phase change resistance, further worsening the uniformity of liquid distribution. This worsening of distribution uniformity further amplifies the differences in heat exchange capacity, ultimately creating a vicious cycle. This not only severely affects the heat exchange performance of the refrigeration system, but the incomplete evaporation of the liquid refrigerant also poses a risk of liquid slugging to the compressor.

[0138] Furthermore, because the downstream end of the distributor branch pipe needs to be welded to each branch of the heat exchange component, its pipe diameter is usually large, which causes the gas-liquid separation to intensify due to expansion when the decelerated refrigerant enters. Moreover, whether it's the speed-up section or the sonic nozzle, while depressurizing and accelerating the refrigerant, it inevitably causes some liquid refrigerant to flash. The cooling capacity generated by flashing is conducted to the outside air through the branch pipe wall, not only causing a loss of cooling capacity but also increasing the dryness of the two-phase refrigerant, thus affecting the mixing uniformity of the gas and liquid phases.

[0139] In view of this, such as Figure 16 and Figure 18 As shown, the downstream end of the branch pipe 30 in the distributor provided in this embodiment is also provided with a branch pipe end jet structure 3, which includes a transmission pipe section 31, a jet section 32, and an assembly pipe section 33. The transmission pipe section 31 is located downstream of the branch pipe body 3a, and the jet section 32 is located near or downstream of the downstream end of the transmission pipe section 31 to accelerate the refrigerant. A jet throat 321 is formed at the point where the inner diameter of the jet section 32 is the smallest. The inner diameter d2 of the jet throat 321 is smaller than the inner diameter d1 at the downstream end of the transmission pipe section 31, and the difference between the two inner diameters is Δd (Δ

[0140] d = d1 - d2) satisfies: 0.03mm ≤ Δd ≤ 1.65mm. The axial length L1 of the jet section 32 is ≤ 350mm. The upstream end of the assembly pipe section 33 is connected to the transmission pipe section 31 or the jet section 32, and the outer diameter of the downstream end of the assembly pipe section 33 is larger than the outer diameter of the transmission pipe section 31 to match the welding of external pipelines.

[0141] The branch pipe end jet structure 3 provided in this embodiment increases the refrigerant velocity at the downstream end of the branch pipe by setting a jet section 32 near or on the downstream side of the transmission pipe section 31, thereby forming a high-speed jet. Under the combined action of shear force and vortex effect, the high-speed refrigerant breaks the interfacial tension between the gas and liquid phases, causing the refrigerant to atomize into a uniform, dispersed flow pattern. The setting of the jet section 32 can re-rectify the gas-liquid separated refrigerant in the branch pipe caused by local resistance loss, friction loss, and phase change expansion into a uniform, dispersed flow pattern and stably output it to the downstream heat exchange components, significantly improving the uniformity of refrigerant distribution and enhancing heat transfer efficiency. At the same time, the high-speed jet of the jet section 32 will also greatly increase the input kinetic energy of the two-phase refrigerant, effectively overcoming the flow resistance generated by the phase change expansion of the refrigerant in the downstream heat exchange tube, ensuring that the refrigerant can smoothly enter the high-efficiency heat exchange tube, thereby achieving uniform refrigerant distribution. The jet section 32 effectively suppresses the distribution deterioration cycle caused by differences in heat exchange, ensuring that the distribution uniformity of each distributor is not affected by the downstream heat exchange components, thus steadily improving heat exchange performance. Furthermore, since the jet section 32 is formed at the downstream end of the branch pipe, the cooling capacity released by some of the liquid refrigerant flashing during pressure reduction and speed increase can also be absorbed by the downstream heat exchange components, further improving heat exchange performance. At the same time, this embodiment also effectively controls the pressure drop loss of the refrigerant on the jet section 32 by limiting the axial length L1 of the jet section 32.

[0142] In refrigeration systems, since the distributor branch pipes need to be assembled and welded to the various branches of the heat exchange components, existing technologies typically set the downstream end of the branch pipe to be larger to meet the welding assembly requirements. However, setting the downstream end of the branch pipe to be larger not only reduces the refrigerant flow rate but also leads to increased gas-liquid separation due to refrigerant expansion. Therefore, this embodiment provides an assembly pipe section 33 with a larger outer diameter at the downstream end of the transmission pipe section 31 or on the jet section 32 to match the welding of external pipes. This arrangement allows the design of the jet section 32 to only meet the input refrigerant performance requirements of the heat exchange components, without needing to consider assembly requirements; similarly, the design of the assembly pipe section 33 only needs to focus on assembly requirements, without needing to consider refrigerant transmission performance. This arrangement decouples the refrigerant transmission performance at the downstream end of the branch pipe from the assembly requirements, satisfying both welding assembly needs and ensuring that the output refrigerant flow rate and uniformity meet the requirements of the downstream heat exchange components, thereby improving heat exchange efficiency.

[0143] Furthermore, in this embodiment, the axial length L2 of the assembly pipe section 33 is set to ≤ 35mm. This setting allows the high-speed refrigerant output from the jet section 32 to quickly enter the downstream heat exchange assembly before it has time to expand. In this embodiment, the assembly pipe section 33 includes a connecting part 331 and an assembly part 332 located downstream of the connecting part 331. The connecting part 331 is welded to the downstream end of the transmission pipe section 31. The axial length L2 of the assembly pipe section 33 refers to the total axial length from the upstream end face of the connecting part 331 to the downstream end face of the assembly part 332. Preferably, the axial length L2 of the assembly pipe section 33 is set to approximately 15mm. However, the present invention does not impose any limitation on this.

[0144] In this embodiment, the jet nozzle 32 is disposed at the downstream end of the transmission pipe section 31. Specifically, the transmission pipe section 31 is a reducing pipe with an inner diameter that gradually decreases in the refrigerant transmission direction, and the jet nozzle 32 is a jet nozzle integrally formed at the downstream end of the transmission pipe section 31. The jet nozzle extends into the assembly pipe section 33, and its downstream end forms a jet throat 321. However, the present invention does not limit the specific structure of the transmission pipe section. In its embodiments, such as... Figure 19 As shown, the transmission pipe section 31 can also be a straight pipe section with a basically unchanged inner diameter.

[0145] Preferably, the inner diameter difference Δd between the inner diameter d1 at the downstream end of the transmission pipe section 31 and the inner diameter d2 at the jet throat 321 is set to 0.8 mm, and the axial length L1 of the jet section 32 is set to 10 mm. However, the present invention does not limit this in any way. In other embodiments, the inner diameter difference Δd can also be set to other values ​​within the range of 0.03 mm to 1.65 mm, such as 0.04 mm, 0.06 mm, 0.1 mm, 0.15 mm, 0.2 mm, 0.5 mm, 1.0 mm, 1.2 mm, 1.5 mm, or 1.6 mm, etc.; the length L1 of the jet section can also be other length values ​​less than 350 mm. In this embodiment, since the jet section 32 is integrally formed in the transmission pipe section 31, the axial length L1 of the jet section 32 refers to the axial length from the connection between the downstream end of the transmission pipe section 31 and the jet section 32 to the downstream end of the jet section 32. Figure 18 As shown, in this embodiment, the downstream end of the jet section 32 is substantially flush with the downstream end of the assembly pipe section 33. However, the present invention does not impose any limitation on this. In other embodiments, the downstream end of the jet section may also be located within the assembly pipe section or extend out of the assembly pipe section to enter the branch of the rear heat exchange assembly.

[0146] In this embodiment, the jet nozzle (jet section 32) is a variable diameter nozzle with a gradually decreasing inner diameter. However, the present invention does not impose any limitations on this. In other embodiments, the inner diameter of the jet nozzle may remain substantially unchanged. Figure 20The diagram illustrates another embodiment of the present invention, providing a branch pipe end jet structure. In this structure, a through hole is formed at the downstream end of the transmission pipe section 31, serving as a jet nozzle (jet portion 32). Furthermore, in other embodiments, the jet nozzle (jet portion 32) may be welded to the downstream end of the transmission pipe section 31. Specifically, as shown... Figure 21 As shown, the jet nozzle (jet section 32) is inner-welded to the downstream end of the transmission pipe section 31, while the connecting part 331 on the assembly pipe section 33 is outer-welded to the downstream end of the transmission pipe section 31. Alternatively, as... Figure 22 As shown, the jet nozzle (jet part 32) and the connecting part 331 on the assembly pipe section 33 are respectively welded to the downstream end of the transmission pipe section 31.

[0147] Although this embodiment uses a jet nozzle as an example for illustration, the present invention does not limit this. In other embodiments, the jet section 32 may also be a jet orifice plate embedded and welded to the assembly pipe section 33, with jet holes 323 formed on the jet orifice plate (jet section 32) and a jet throat 321 formed at the minimum inner diameter of the jet hole 323, such as... Figures 23 to 27 As shown. Specifically, in Figure 23 In this configuration, the jet orifice 323 is a flanged hole extending from the hole wall towards the downstream end of the assembly pipe section 33, with the jet throat 321, having the smallest inner diameter, formed at the downstream end of the flanged hole. Alternatively, as... Figure 24 and Figure 25 As shown, the jet orifice 323 is a through hole formed based on the axial thickness of the jet orifice plate (jet section 32). The jet orifice 323 is a constant-diameter hole with a substantially unchanged diameter, and a jet throat 321 is formed at any point on it. Alternatively, as... Figure 26 and Figure 27 As shown, the jet orifice 323 includes a jet throat 321 and a guide orifice section 322. The guide orifice section 322 is located upstream of the jet throat 321 and its diameter is larger than the diameter d2 at the jet throat 321. The guide orifice section 322 with a larger inner diameter can quickly guide the refrigerant into the jet orifice 323, thereby reducing the refrigerant transmission resistance. In addition, in other embodiments, the jet orifice can also be provided as a smooth-lined Venturi orifice to reduce jet resistance. The Venturi orifice includes a guide orifice section, a jet throat, and a diffuser orifice section distributed sequentially along the refrigerant flow direction, and the diameters of the guide orifice section and the diffuser orifice section are both larger than the diameter at the jet throat.

[0148] Figure 28The diagram shows a schematic of a branch pipe end jet structure according to another embodiment of the present invention. In this structure, the connecting portion 331 on the assembly pipe section 33 is welded to the downstream end of the transmission pipe section 31. The jetting portion 32 is a jetting orifice plate embedded near the downstream end of the transmission pipe section 31. Jetting holes 323 are formed on the jetting orifice plate, and a jetting throat 321 is formed at the minimum inner diameter of the jetting holes 323. Preferably, the downstream end face of the jetting orifice plate is substantially flush with the downstream end face of the transmission pipe section 31. Figures 23 to 27 Similarly, in this structure, the jet hole 323 can also be a flanged hole, a constant diameter through hole, or a variable diameter through hole.

[0149] In this embodiment, the size of the connecting portion 331 of the assembly pipe section 33 needs to match the outer diameter of the transmission pipe section 31. Due to the limitation of the material's plastic deformation capacity, the outer diameter of the downstream end of the assembly pipe section 33 can only increase slightly compared to the outer diameter of the transmission pipe section 31. Furthermore, the branch dimensions of heat exchange components of different specifications are very likely to be different, with some heat exchange components having branch dimensions much larger than the outer diameter of the transmission pipe section 31. In this case, the outer diameter of the downstream end of the assembly pipe section 33, formed by plastic processing methods such as flaring or diameter-reducing stretching, will be difficult to weld and match with the branch of the heat exchange component. To solve this problem, in other embodiments, a branch pipe end jet structure can be provided, including an outer sleeve 34. The outer sleeve 34 is welded to the assembly portion 332 on the assembly pipe section 33, increasing the outer diameter at the assembly portion 332 to match the branch of the heat exchange component with a larger pipe diameter, such as... Figure 29 and Figure 30 As shown. In Figure 29 In this embodiment, the number of outer sleeves 34 is one. However, the present invention does not limit this in any way. In other embodiments, when the outer diameter at the assembly pipe section needs to be increased significantly or the increased dimension is a non-standard pipe wall thickness, the branch pipe end jet structure can also be provided, including multiple outer sleeves arranged sequentially, and each outer sleeve is a commercially available standard wall thickness pipe fitting, such as... Figure 30 As shown.

[0150] To verify the performance of the distributor with liquid separation baffle 20 and branch pipe end jet structure 3 provided in this embodiment, Figure 16 Multiple samples of the dispenser structure shown were fabricated. CFD (Computational Fluid Dynamics) simulations were used to analyze this embodiment under different specifications and different dryness levels. Figure 16 The sample shown is of the same specification. Figure 31 The uniformity and stability of the distribution of the existing brass impeller-type distributor (hereinafter referred to as the control sample) are shown.

[0151] The CFD simulation analysis uses ANSYS software, and its conditions are set as follows:

[0152] Turbulence model: Realizable k-ε model;

[0153] Mesh parameters: Tetrahedral unstructured mesh is used;

[0154] Operating conditions: The working fluid is R410A refrigerant, and the wall boundary is an adiabatic boundary.

[0155] Boundary conditions: Turbulence intensity 5%, other boundary conditions are detailed in the data table.

[0156] Evaluation parameters: STD and K. STD refers to the standard deviation of the refrigerant mass flow rate at each branch outlet, and K refers to the ratio of the standard deviation STD to the set mass flow rate M allocated to each branch. out The percentage.

[0157] The specific formula for calculating STD is as follows:

[0158]

[0159] in, The average refrigerant mass flow rate at all branch outlets, m j Let M be the refrigerant mass flow rate at the outlet of the j-th branch pipe, n be the number of branch pipes, and M be the refrigerant mass flow rate at the outlet of the j-th branch pipe. out To set the mass flow rate allocated to each branch pipe.

[0160] Figure 16 The diagram shows the sample structure of the dispenser provided in this embodiment. Figure 31 The existing brass impeller type dispenser (i.e., the control sample structure) is used.

[0161] [1] The distribution uniformity and stability of the sample and the corresponding control sample were analyzed at the same dryness of 0.22.

[0162] Sample selection: Based on the specifications of the dispenser body 10, the specifications of the inlet pipe 40, the number n of the branch pipes 30, and the specifications of the branch pipe body 3a in the branch pipe 30, 8 samples and 8 corresponding control samples were selected.

[0163] Common parameters of the samples and corresponding control samples in the first analysis group: outer diameter of the main body D0 = 19 mm, outer diameter of the main body of the inlet pipe D1 = 6.35 mm, number of branch pipes n = 2, outer diameter of the main body of the branch pipe D2 = 3.4 mm, and the total mass flow rate M is set to be input. in =38.36Kg / h, set the mass flow rate M distributed to each branch pipe out =19.18Kg / h.

[0164] Common parameters of the samples and corresponding control samples in the second analysis group: outer diameter of the main body D0 = 19 mm, outer diameter of the main body of the inlet pipe D1 = 6.35 mm, number of branch pipes n = 3, outer diameter of the main body of the branch pipe D2 = 3.4 mm, and the total mass flow rate M is set to be input. in=53.71Kg / h, set the mass flow rate M distributed to each branch pipe out =17.9Kg / h.

[0165] Common parameters of the samples and corresponding control samples in the third analysis group: outer diameter of the main body D0 = 19 mm, outer diameter of the main body of the inlet pipe D1 = 6.35 mm, number of branch pipes n = 4, outer diameter of the main body of the branch pipe D2 = 3.4 mm, and the total mass flow rate M is set to be input. in =76.73Kg / h, set the mass flow rate M distributed to each branch pipe out =19.18Kg / h.

[0166] Common parameters of the samples and corresponding control samples in the fourth analysis group: outer diameter of the main body D0 = 19 mm, outer diameter of the main body of the inlet pipe D1 = 6.35 mm, number of branch pipes n = 5, outer diameter of the main body of the branch pipe D2 = 3.4 mm, and the total mass flow rate M is set to be input. in =76.73Kg / h, set the mass flow rate M distributed to each branch pipe out =15.35Kg / h.

[0167] Common parameters of the samples and corresponding control samples in analysis group 5: outer diameter of the main body D0 = 19 mm, outer diameter of the main body of the inlet pipe D1 = 9.52 mm, number of branch pipes n = 6, outer diameter of the main body of the branch pipe D2 = 3.4 mm, and the total mass flow rate M is set to be input. in =110.49Kg / h, set the mass flow rate M distributed to each branch pipe out =18.42Kg / h.

[0168] Common parameters of the samples and corresponding control samples in analysis group 6: outer diameter of the main body D0 = 21 mm, outer diameter of the main body of the inlet pipe D1 = 12.7 mm, number of branch pipes n = 5, outer diameter of the main body of the branch pipe D2 = 3.8 mm, and the total mass flow rate M is set to be input. in =184.15Kg / h, set the mass flow rate M distributed to each branch pipe out = 36.83 kg / h.

[0169] Common parameters of the samples and corresponding control samples in analysis group 7: outer diameter of the main body D0 = 21 mm, outer diameter of the main body of the inlet pipe D1 = 12.7 mm, number of branch pipes n = 7, outer diameter of the main body of the branch pipe D2 = 3.8 mm, and the total mass flow rate M is set to be input. in =184.15Kg / h, set the mass flow rate M distributed to each branch pipe out =26.31Kg / h.

[0170] Common parameters of the samples and corresponding control samples in analysis group 8: outer diameter of the main body D0 = 21 mm, outer diameter of the main body of the inlet pipe D1 = 12.7 mm, number of branch pipes n = 8, outer diameter of the main body of the branch pipe D2 = 3.8 mm, and the total mass flow rate M is set to be input. in =184.15Kg / h, set the mass flow rate M distributed to each branch pipe out =23.02Kg / h.

[0171] In the above 8 analysis groups, the mass flow rate M distributed to each branch pipe in each sample is... out All values ​​were less than or equal to 40 kg / h, indicating a low mass flow rate scenario. Table 1 summarizes the data from the eight analysis groups. Analysis shows that under low mass flow rate conditions, the STD and K values ​​of each sample were lower than those of the corresponding control samples, indicating better distribution uniformity for each sample compared to the control samples. Furthermore, examining the K values ​​of all samples across the eight mass flow rate analysis groups reveals that they ranged from 0.5% to 3.02%, while the K values ​​of all control samples ranged from 3.68% to 8.37%. Therefore, it can be concluded that under low mass flow rate conditions, this embodiment... Figure 16 The dispenser sample shown, featuring a liquid-dispensing baffle 20 and a branch pipe end jet structure 3, outperforms other dispensers in both uniformity and stability. Figure 31 The existing brass impeller dispenser shown is a control sample.

[0172] [2] Analyze the distribution uniformity and stability of samples under different dryness conditions.

[0173] Sample selection: Based on the specifications of the dispenser body 10, the specifications of the inlet pipe 40, the number n of branch pipes 30, and the specifications of the branch pipe body 3a within the branch pipe 30, four samples and four corresponding control samples were selected. Simulation analysis was performed on each sample and the corresponding control sample at dryness fractions of 0, 0.1, 0.15, 0.2, 0.25, 0.3, and 0.35, respectively.

[0174] Common parameters for samples and corresponding control samples in the first dryness analysis group: outer diameter of the main body D0 = 45 mm, outer diameter of the main body of the inlet pipe D1 = 12.7 mm, number of branch pipes n = 17, outer diameter of the main body of the branch pipe D2 = 3.4 mm; set the input total mass flow rate M. in =595Kg / h, set the mass flow rate M distributed to each branch pipe out =35Kg / h.

[0175] Common parameters for samples and control samples in the second dryness analysis group: outer diameter of the main body D0 = 45 mm, outer diameter of the main body of the inlet pipe D1 = 16 mm, number of branch pipes n = 15, outer diameter of the main body of the branch pipe D2 = 3.8 mm; set the input total mass flow rate M. in=825Kg / h, set the mass flow rate M distributed to each branch pipe out =55g / h.

[0176] Common parameters for samples and control samples in the third dryness analysis group: outer diameter of the main body D0 = 72 mm, outer diameter of the main body of the inlet pipe D1 = 22 mm, number of branch pipes n = 31, outer diameter of the main body of the branch pipe D2 = 3.4 mm; set the input total mass flow rate M. in =1085Kg / h, set the mass flow rate M distributed to each branch pipe out =35Kg / h.

[0177] Common parameters for samples and control samples in the fourth dryness analysis group: outer diameter of the main body D0 = 72 mm, outer diameter of the main body of the inlet pipe D1 = 22 mm, number of branch pipes n = 27, outer diameter of the main body of the branch pipe D2 = 3.8 mm; set the input total mass flow rate M. in =485Kg / h, set the mass flow rate M distributed to each branch pipe out =55Kg / h.

[0178] After summarizing the 28 data sets from the four dryness analysis groups, Table 2 was compiled and analyzed. The results show that in each dryness analysis group, regardless of the change in dryness, the STD and K values ​​of each sample were lower than those of the corresponding control sample, indicating that the distribution uniformity of each sample was superior to that of the corresponding control sample. Furthermore, a review of the four dryness analysis groups reveals that the K values ​​of all samples ranged from 2.04% to 3.29%, while the K values ​​of all control samples ranged from 3.10% to 4.37%; the distribution ranges of the two are quite similar. In other words, both the samples and control samples exhibited superior separation stability under different specifications and dryness conditions. Therefore, it can be concluded that under different dryness scenarios (including low dryness scenarios with a dryness of less than 0.15), this embodiment... Figure 16 The dispenser sample structures shown are basically similar in terms of dispensing stability. Figure 31 The existing brass impeller dispenser shown is a control sample, but its dispensing uniformity is far superior to that of the existing brass impeller dispenser (i.e., control sample).

[0179] [3] To further verify the performance of the distributor provided in this embodiment on the air conditioning unit, the sample and control sample in the second analysis group in Table 1 were selected and sent to Zhejiang Nuomeisheng Testing Technology Co., Ltd. for whole unit testing. The effects of the two on the EER performance (cooling energy efficiency ratio) of the same unit under rated cooling conditions were compared and analyzed.

[0180] 3.1 The test used a variable frequency split-type wall-mounted room air conditioner, model KFR-35W / BpR3QC(B1), and its relevant parameters are shown in the table below:

[0181]

[0182] 3.2 Test conditions: Rated cooling (test mode).

[0183] 3.3 During the test, the outdoor unit was sampled 7 times to obtain data for each test item.

[0184] Table 3 summarizes the test data of the sample taken 7 times under rated cooling mode, and calculates the average value. Similarly, Table 4 summarizes the test data and average value of the control sample under the same conditions. Analysis of Tables 3 and 4 shows that: when the sample provided in this embodiment is tested on an outdoor unit, the average EER of the unit is 5.718; while the average EER of the unit with the corresponding control sample is 5.512. Compared to the control sample, the sample improves the EER by 3.74%.

[0185] The whole-machine test of the samples and corresponding control samples in the second analysis group in Table 1: On the one hand, it effectively verifies the results provided in this embodiment. Figure 16 The distributor structure significantly improves the EER performance of the entire unit under rated cooling conditions. Furthermore, the test results also indirectly confirm the accuracy of the simulation analysis results in Tables 1 and 2; specifically, in a refrigeration system, the more uniform the refrigerant distribution (the smaller its STD and K values), the higher its heat exchange efficiency, and the better its corresponding EER performance. The actual whole-unit test accurately reflects, through the EER index, that the distribution performance of the samples in the second analysis group in Table 1 is superior to the corresponding control group; this conclusion is completely consistent with the conclusions drawn from the STD and K values ​​obtained from the simulation analysis in Table 1, confirming that the simulation analysis data in Tables 1 and 2 of this embodiment have accurate guiding significance for product performance research.

[0186] Example 2

[0187] This embodiment is basically the same as Embodiment 1 and its variations, except that: Figures 32 to 34 As shown, the liquid separation baffle also includes a connecting column 1, and multiple baffles are arranged sequentially along the axial direction on the connecting column 1. Adjacent baffles partially abut each other to form a flow channel gap 210 between the corresponding solid parts.

[0188] Similar to Embodiment 1, the liquid separating baffle 20 includes two baffles, namely a first baffle 21 and a second baffle 22. The middle portion 213 of the first baffle and the middle portion 223 of the second baffle protrude relative to each other and abut against each other to form a flow channel gap. A connecting hole 214 for fitting onto the connecting post 1 is also formed on the middle portion 213 of the first baffle, and a connecting hole 224 for fitting onto the connecting post 1 is also formed on the middle portion 223 of the second baffle, and the two connecting holes are substantially coaxial. However, the present invention does not limit this in any way. In other embodiments, such as... Figure 35 and Figure 36 As shown, the middle part of the two partitions still has corresponding connecting holes 214 and 224 that are sleeved on the connecting post 1; however, the middle part of the two partitions does not protrude and abut, but the ends of the first partition body 212 and the second partition body 222 are connected, and a flow channel gap 210 is still formed between the two body parts.

[0189] In this embodiment, both the first partition 21 and the second partition 22 are integral structures, and each partition has a connecting hole formed in the middle of its center, which is fitted onto the outer peripheral wall of the connecting column 1. However, the present invention does not impose any limitations on this. In other embodiments, the partition may also include multiple independent solid parts, which are spaced apart along the circumference of the connecting column and fixed to the outer peripheral wall of the connecting column.

[0190] In this embodiment, as Figure 34 As shown, the connecting column 1 is a conical-cylindrical combination structure including a conical guide section 11 and a cylindrical section 12. The conical guide section 11 is close to the liquid inlet side of the distributor body 10, and the first baffle 21 and the second baffle 22 are respectively sleeved on the cylindrical section 12. The conical guide section 11 uniformly guides the input refrigerant to multiple refrigerant ports 211 on the first baffle 21, ensuring that the refrigerant uniformly enters multiple sets of anti-jet channels 200 for sufficient anti-jet mixing. However, the present invention does not limit this in any way. In other embodiments, the connecting column may also be a cylinder. Specifically, as shown in the figure... Figure 37 As shown, the connecting column 1 is a cylinder with an open cavity 11. The input refrigerant is reflected and mixed within the open cavity 11 before entering the liquid separator 20 for reflective mixing. Preferably, the connecting column 1 can be a stretched cylinder and the open cavity 11 can be cylindrical. However, the present invention does not limit this in any way. In other embodiments, the shape of the open cavity 11 can also be one or more combinations of frustum, cone, and sphere. In other embodiments, the connecting column can also be a circular tube with open ends, the lower end of which abuts against the inner end wall of the liquid outlet side of the distributor body. The inner end wall of the liquid outlet side of the distributor body and the circular tube form an open cavity for reflective mixing of the refrigerant.

[0191] Correspondingly, such as Figure 38 As shown, this embodiment also provides a dispenser, which includes a dispenser body 10 and a dispenser body 10. Figure 34 The liquid separation baffle 20 is shown. The liquid separation baffle 20 is disposed inside the distributor body 10 and the edge of each baffle is substantially in contact with the inner peripheral wall of the distributor body 10.

[0192] Figures 39 to 43 The diagram shows the structure of a dispenser provided in another embodiment of the present invention. All five dispenser structures include... Figure 37 The liquid separator 20 in the middle. Specifically, in Figure 39In this configuration, liquid separators 20 are disposed within the distributor body 10, and the edge of each separator substantially abuts against the inner peripheral wall of the distributor body 10. Figure 40 The distributor body 10 also includes a jet plate 70 and a reflective mixing guide plate 80 located sequentially downstream of the liquid separating baffle 20. A jet hole 701 is formed on the jet plate 70. The refrigerant mixed by the liquid separating baffle 20 is collected in the jet hole 701 and jetted at high speed to the reflective mixing guide plate 80. The reflective mixing zone 801 on the reflective mixing guide plate 80 reflects and mixes the refrigerant injected through the jet hole 701, and then evenly distributes it into multiple branch pipes 30 through multiple guide holes 802 on the reflective mixing guide plate 80.

[0193] Figure 41 and Figure 40 They are basically the same, the difference is: Figure 41 In this design, the liquid separation baffle 20 includes four baffles: a first baffle 21, a second baffle 22, a third baffle 23, and a fourth baffle 24. The first baffle 21 and the second baffle 22 form a jet unit 2_1, with multiple sets of jet channels between them; the third baffle 23 and the fourth baffle 24 form another jet unit 2_2. No jet channels are formed between adjacent baffles (i.e., the second baffle 22 and the third baffle 23) in the two jet units 2_1 and 2_2. However, this invention does not limit this. In other embodiments, a three-stage jet mixing can be formed between the four baffles by controlling the axial spacing of the solid portions between the second and third baffles.

[0194] Figure 42 Then in Figure 40 Based on the above, a spacer 60 is added to further control the volume of the chamber before the refrigerant is distributed to each branch pipe 30 to avoid excessive expansion of the refrigerant.

[0195] exist Figure 43 In this invention, the distributor body 10 contains two liquid-distributing baffles 20 and a jetting element 70 located between the two baffles 20. After being mixed by the opposing jets through the first baffle 20, the refrigerant collects at the jetting holes 701 on the jetting element 70 and is then injected at high speed into the second baffle 20, where it undergoes further reflection and opposing jet mixing. However, this invention does not limit the scope of the invention. The liquid-distributing baffles provided by this invention can also be combined with other distributor accessories to achieve uniform refrigerant distribution.

[0196] Example 3

[0197] This embodiment is basically the same as Embodiment 2 and its variations, except that in this embodiment, the adjacent partitions are spaced apart.

[0198] Specifically, in this embodiment, the first partition 21 and the second partition 22 are axially spaced on the connecting post 1, so that a flow channel gap 210 is formed between the first partition solid portion 212 and the second partition solid portion 222. 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 partitions during assembly, such as... Figure 44 and Figure 45 As shown, the liquid separator 20 also includes a limiting sleeve 25, which is fitted over the connecting column 1. The first partition 21 and the second partition 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 liquid separator includes three or more intermittently distributed partitions, the number of limiting sleeves is also multiple. In this embodiment, the limiting sleeve 25 and the two adjacent partitions 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 partitions. For example, it can be integrally formed with the first partition or the second partition using a stamping and flanging process.

[0199] Figure 46 In another embodiment of the present invention, a liquid-separating partition is provided, in which the connecting column 1 is a cylindrical stretched cylinder with an open cavity 11, and the first partition 21 and the second partition 22 are spaced apart on the outer peripheral wall of the connecting column 1 by spacers 25. However, the present invention does not limit this in any way. In other embodiments, the most upstream partition (i.e., the first partition 21) may be integrally formed with the connecting column 1, while other partitions (such as the second partition 22) are welded to the outer peripheral wall of the connecting column 1, such as... Figure 47 and Figure 48 As shown.

[0200] Example 4

[0201] This embodiment is basically the same as Embodiment 1 and its variations, except that the connection method of the assembly pipe section 33 on the branch pipe 30 is different.

[0202] like Figure 49 As shown, in this embodiment, the assembly pipe segment 33 is integrally formed on the downstream end of the transmission pipe segment 31. The upstream end face of the assembly pipe segment 33 refers to the connection between the assembly pipe segment 33 and the transmission pipe segment 31. Figure 49 The middle section is where the assembly pipe section 33 begins to flare. The jetting part 32 is embedded and welded to the downstream end of the transmission pipe section 31 or within the assembly pipe section 33. Specifically, the jetting part 32 is a jetting pipe embedded in the assembly pipe section 33 and welded to the downstream end of the transmission pipe section 31. The jetting pipe is a straight pipe with a basically uniform inner diameter, and any point on it serves as the jetting throat 321. However, the present invention does not impose any limitations on this. In other embodiments, the jetting pipe may also be a variable diameter pipe, with the smallest inner diameter forming the jetting throat.

[0203] The present invention does not limit the connection method of the jet tube (jet section 32). In other embodiments, the jet section 32 may also be welded to the assembly pipe section 33. Specifically, as shown... Figure 50 As shown, the jet section 32 is a jet pipe with a basically uniform inner diameter, and the outer diameter of the jet pipe is basically close to the inner diameter of the assembly pipe section 33, and the two are welded together. Alternatively, as... Figure 51 As shown, the outer diameter of the jet pipe is also close to the inner diameter of the assembly pipe section 33, but the inner diameter of the jet pipe decreases along the refrigerant transmission direction. The jet pipe (jet section 32) includes an inlet guide pipe section 322' with a larger inner diameter and a jet throat 321. The guide pipe section 322' with a relatively larger inner diameter quickly guides the refrigerant into the jet pipe to reduce the flow resistance.

[0204] Although this embodiment uses the jet section 32 as an example of a jet tube, the present invention does not limit this. In other embodiments, when the assembly pipe section 33 is integrally formed at the downstream end of the transmission pipe section 31, the jet section 32 can also be provided as a jet orifice plate. The jet orifice plate (jet section 32) is embedded and welded inside the assembly pipe section 33, and jet holes 323 are formed on the jet orifice plate (jet section 32), with a jet throat 321 formed at the minimum inner diameter of the jet holes 323. Specifically, in Figure 52 and Figure 53 In this embodiment, the jet orifice 323 is a flanged hole extending from the hole wall towards the downstream end of the assembly pipe section 33, and a jet throat 321 with the smallest inner diameter is formed at the downstream end of the flanged hole. In other embodiments, the jet orifice 323 may also be a through hole formed based on the axial thickness of the jet orifice plate (jet section 32). Specifically, the jet orifice 323 is a constant diameter hole with a substantially unchanged diameter, and a jet throat 321 is formed at any point on the jet orifice 323, such as... Figure 54 As shown. Alternatively, the jet orifice 323 includes a guide orifice section 322 with a larger inner diameter and a jet throat 321, as shown. Figure 55 As shown. In other embodiments, the jet orifice can also be a smooth-lined Venturi orifice to reduce jet resistance. The Venturi orifice includes a guide orifice section, a jet throat, and a diffuser orifice section distributed sequentially along the refrigerant flow direction. The diameters of the guide orifice section and the diffuser orifice section are both larger than the diameter at the jet throat.

[0205] Figure 56 This is a schematic diagram of a branch pipe end jet structure provided in another embodiment of the present invention. In this structure, the jet section 32 is also a jet orifice plate, and the jet orifice plate is embedded and welded near the downstream end of the transmission pipe section 31. Preferably, the downstream end face of the jet orifice plate (jet section 32) is substantially flush with the beginning of the flare of the assembly pipe section 33.

[0206] Example 5

[0207] This embodiment is basically the same as Embodiment 1 and its variations, except that: the jet section 32 is a jet pipe, the upstream end of the jet section 32 is connected to the transmission pipe section 31, and its downstream end is connected to the assembly pipe section 33.

[0208] In this embodiment, as Figure 57 As shown, the jet section 32 is a variable-diameter pipe integrally formed on the upstream end of the transmission pipe section 31, with its inner diameter gradually decreasing along the refrigerant transmission direction. A jet throat 321 is formed at the end of the jet section 32 and inserted and welded into the assembly pipe section 33. However, this invention does not limit this. In other embodiments, the upstream end of the jet pipe (jet section 32) may be welded to the transmission pipe section 31, while its downstream end is integrally formed with the assembly pipe section 33, such as... Figure 58 As shown. Alternatively, the two ends of the jet pipe (jet section 32) are welded to the transmission pipe section 31 and the assembly pipe section 33, respectively, as shown. Figure 59 As shown. Alternatively, the transmission pipe section 31, the jet section 32, and the assembly pipe section 33 are sequentially distributed along the refrigerant transmission direction and integrally formed, as shown. Figure 60 As shown.

[0209] Example 6

[0210] This embodiment is basically the same as Embodiment 1 and its variations, except that the position of the jet section 32 is different, and the outer diameter of the assembly pipe section 33 is not limited, it only needs to meet the assembly requirements. Figure 61 The diagram shown is a partial schematic of the branch pipe 30 provided in this embodiment. Figure 62 As shown Figure 61 A schematic diagram of the jet structure 3 at the end of the branch pipe. This embodiment also provides a branch pipe 30, which includes a branch pipe body 3a and... Figure 62 The branch pipe end jet structure 3 is shown. The transmission pipe segment 31 within the branch pipe end jet structure 3 is sleeved and connected to the branch pipe body 3a. The branch pipe body 3a is a stainless steel pipe, while the integral branch pipe end jet structure 3 is a non-ferrous metal pipe, such as a copper or aluminum pipe. However, the present invention does not impose any limitations on this. In other embodiments, the transmission pipe segment 31 may also be integrally formed into the branch pipe body 3a; in other words, the transmission pipe segment 31 is the end portion of the branch pipe body 3a, such as... Figure 68 As shown. In Figure 68 In the middle, the branch pipe 30 of the distributor is an integral molded pipe fitting, such as an integral aluminum pipe or an integral copper pipe, and the upstream end of the branch pipe body 3a is connected to the distributor body.

[0211] like Figure 61 and Figure 62As shown, the branch pipe end jet structure provided in this embodiment includes a transmission pipe section 31, an assembly pipe section 33, and a jet section 32. The transmission pipe section 31 is located downstream of the branch pipe body 3a, and the assembly pipe section 33 is located downstream of the transmission pipe section 31 to match the welding of external pipelines. The jet section 32 is located downstream of the assembly pipe section 33 or embedded in the assembly pipe section 33. A jet throat 321 is formed at the minimum inner diameter of the jet section 32. The inner diameter d2 of the jet throat 321 is smaller than the inner diameter d1 at the downstream end of the transmission pipe section and the inner diameter of the assembly section 332 on the assembly pipe section 33, and the difference Δd (Δd = d1 - d2) between the inner diameter of the jet throat 321 and the inner diameter at the downstream end of the transmission pipe section 31 satisfies: 0.03mm ≤ Δd ≤ 1.65mm, and the axial length L1 of the jet section 32 ≤ 350mm.

[0212] In this embodiment, the transmission pipe section 31, the assembly pipe section 33, and the jet section 32 are sequentially arranged and integrally formed along the refrigerant transmission direction. For ease of description, in Figure 62 The downstream end of the transmission pipe section 31 is marked with a dashed line (which is also the upstream end of the assembly pipe section 33). However, in the actual pipe fitting, the assembly pipe section 33 and the transmission pipe section 31 are integrally formed, and there is no transition boundary or transition line at the connection between the two. Figure 62 The dashed line in the middle.

[0213] Although this embodiment uses the transmission pipe section, assembly pipe section, and jet section as an example of integral molding, the present invention does not limit this in any way. In other embodiments, such as Figure 63 and Figure 64 As shown, the assembly pipe section 33 and the jet section 32 can also be integrally formed, with the upstream end of the assembly pipe section 33 then welded to the downstream end of the transmission pipe section 31. Alternatively, the assembly pipe section can be integrally formed into the transmission pipe section, while the jet section is welded to the downstream end of the assembly pipe section.

[0214] Furthermore, the present invention does not limit the specific structure of the jet section. In other embodiments, such as Figure 64 As shown, a jet nozzle can also be formed at the downstream end of the assembly pipe section 33; specifically, the downstream end of the assembly pipe section 33 can be sealed and then stamped to form a jet nozzle as the jet section 32. Alternatively, as... Figure 65 As shown, the jet section 32 is a jet tube embedded within the assembly pipe section 33. Alternatively, the jet section is a jet orifice plate embedded within the assembly pipe section, with jet holes formed on the orifice plate, and a jet throat formed at the minimum inner diameter of the jet holes. The specific structure of the jet orifice plate is basically the same as the structure and its variations given in Embodiment 4, and will not be described again here.

[0215] like Figure 62As shown, in the branch pipe end jet structure 3 provided in this embodiment, the jet section 32 is located downstream of the assembly pipe section 33. When assembled with the external heat exchange components, the jet section 32 extends into the heat exchange tube of the rear heat exchange component along with the assembly pipe section 33. Similar to Embodiment 1, the jet section 32 increases the refrigerant flow velocity at the very end of the branch pipe, injecting the refrigerant into the rear heat exchange tube at high speed. At the same time, the cooling capacity generated by the flash evaporation of the liquid refrigerant during the depressurization and acceleration process can also be absorbed by the heat exchange tube, avoiding the loss of cooling capacity during the jetting process, thereby greatly improving the heat exchange efficiency.

[0216] Furthermore, since the jet section 32 is located downstream of the assembly pipe section 33, the refrigerant, after expanding and slowing down within the assembly pipe section 33, can also be converted into high-speed refrigerant to form a jet after flowing through the jet section 32. In other words, in the branch pipe end jet structure provided in this embodiment, the arrangement of the assembly pipe section 33 does not need to consider the refrigerant flow rate requirements, but only the assembly requirements with the heat exchange tubes in the downstream heat exchange assembly. Therefore, the overall outer diameter of the assembly pipe section 33 (including the outer diameter of the assembly section 332) can be as described in this embodiment. Figure 62 As shown, it is approximately the outer diameter of the downstream end of transmission pipe section 31. Alternatively, as... Figure 66 As shown, the outer diameter of the mounting portion 332 on the assembly pipe section 33 is increased by a flaring process, so that the outer diameter of the mounting portion 332 is larger than the outer diameter at the downstream end of the transmission pipe section 31. Alternatively, as... Figure 67 As shown, the outer diameter of the assembly part 332 on the assembly pipe section 33 is reduced by a necking process so that the outer diameter of the assembly part 332 is smaller than the outer diameter at the downstream end of the transmission pipe section 31.

[0217] In summary, the liquid distribution baffle provided by this invention comprises multiple baffles staggered along the axial direction of the distributor. Adjacent baffles are configured such that each solid portion of the upper baffle not only covers the corresponding refrigerant port on the lower baffle but also overlaps with the projected solid portions on both sides of the refrigerant port, thereby forming a set of opposing jet flow channels in the two overlapping areas. The refrigerant, after being throttled and accelerated through the refrigerant port of the upper baffle, enters the multiple sets of opposing jet flow channels between adjacent baffles. Within each set of opposing jet flow channels, the high-speed refrigerant flowing in opposite directions collides and forms turbulence, enhancing the turbulence of the two-phase flow and allowing it to develop into a stable, diffused mist flow, thereby significantly improving the uniformity and stability of the two-phase refrigerant distribution. Furthermore, by controlling the axial spacing between the solid portions of adjacent baffles, a collision and mixing space is provided for the refrigerant within the opposing jet flow channels while preventing refrigerant expansion due to excessively large flow channels, ensuring continuous high-speed convection of the refrigerant and improving the effect of opposing jet mixing.

[0218] Furthermore, for the distributor branch pipe, a branch pipe end jet structure is installed at its downstream end. The high-speed jet from the narrower inner diameter jet section effectively eliminates the gas-liquid two-phase separation phenomenon caused by local resistance loss, friction loss, and refrigerant expansion during refrigerant transmission through the branch pipe. This ensures the refrigerant is output to the downstream heat exchange components in a fully mixed, dispersed flow pattern, thereby improving heat exchange efficiency. Simultaneously, the jet section significantly increases the kinetic energy of the gas-liquid two-phase refrigerant to overcome the flow resistance generated by the refrigerant's volume expansion due to phase change in the downstream heat exchange tubes. This ensures the uniformity of refrigerant distribution is unaffected by differences in downstream heat exchange capacity, ensuring a consistently uniform distribution to all heat exchange tubes, thus improving system heat exchange efficiency. Additionally, since the downstream end of the branch pipe is connected to the downstream heat exchange components, the cooling capacity generated by some liquid refrigerant flash evaporation during the jet section's pressure reduction and acceleration process can also be utilized by the heat exchange components, further improving heat exchange efficiency. By setting a larger outer diameter assembly pipe section at the downstream end of the transmission pipe section or on the jet section, the design of the transmission pipe section and the jet section only needs to meet the requirements of the downstream heat exchange components for refrigerant transmission performance without having to consider assembly issues, ensuring that the distributor branch pipe can simultaneously meet the dual requirements of refrigerant transmission performance and welding assembly.

[0219] Although the present invention has been disclosed above by way of preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art may make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope of protection claimed in the claims.

[0220] Table 1

[0221]

[0222] Table 2

[0223]

[0224] Table 3

[0225]

[0226] Table 4

[0227]

Claims

1. A liquid separation baffle, characterized by, A distributor is provided and comprises: a plurality of partition plates arranged in axial staggered distribution along the distributor, each partition plate comprising a plurality of refrigerant ports arranged in circumferential distribution and a solid portion between adjacent refrigerant ports; when two adjacent partition plates are projected in the axial direction of the distributor, each solid portion of the upper partition plate covers the corresponding refrigerant port of the lower partition plate and overlaps the solid portions on both sides of the corresponding refrigerant port of the lower partition plate to form a group of counterjet channels in which the refrigerant flows in opposite directions and is mixed in each group of counterjet channels.

2. The liquid separation baffle according to claim 1, characterized by The minimum width L0 of each overlap region formed by the projection overlap of the solid portion of the upper partition plate and the solid portions on both sides of the corresponding refrigerant port of the lower partition plate satisfies 0.5mm≤L0≤3.5mm.

3. The liquid separation baffle according to claim 1, wherein The plurality of partition plates are arranged in sequential partial abutment so that the solid portions of two adjacent partition plates have flow channel gaps therebetween.

4. The liquid separation baffle according to claim 3, wherein The partition plates further comprise intermediate portions, and the plurality of solid portions are arranged in circumferential distribution around the intermediate portions; and at least one intermediate portion of the plurality of partition plates is raised and connected to the intermediate portion of an adjacent partition plate so that the solid portions of two adjacent partition plates are arranged in spaced distribution.

5. The liquid separation baffle according to claim 1, wherein The distributor further comprises connecting columns, and the plurality of partition plates are arranged in axial sequence on the connecting columns, and two adjacent partition plates are arranged in partial abutment so that flow channel gaps are formed between the corresponding solid portions. Alternatively, two adjacent partition plates are arranged in spaced distribution so that flow channel gaps are formed between the corresponding solid portions.

6. The liquid separation baffle according to claim 5, wherein The partition plates are of integral structure, and the intermediate portion of each partition plate is formed with a connecting hole that is sleeved on the connecting column. Alternatively, the partition plates comprise a plurality of independent solid portions, and the plurality of solid portions are arranged in spaced distribution in the circumferential direction of the connecting column and are fixed to the connecting column.

7. The liquid separation baffle according to claim 5, wherein The distributor further comprises a limiting spacer sleeve that is sleeved on the connecting column, and two adjacent partition plates abut the two ends of the limiting spacer sleeve to be arranged in spaced distribution.

8. The liquid dividing baffle according to claim 1, wherein The axial spacing H0 between the solid portions of two adjacent partition plates satisfies 0<H0≤3mm.

9. The liquid dividing baffle according to claim 1, wherein The refrigerant ports are notch grooves that extend continuously in the radial direction of the partition plate to the edge of the partition plate, and the notch grooves are scallop-shaped, rectangular, or have a curved groove wall.

10. The liquid separation baffle according to claim 1, wherein The refrigerant ports are one or more combinations of through holes, flanged holes, or arc bubble holes.

11. The liquid dividing baffle according to claim 1, wherein The distributor comprises three or more partition plates, and a plurality of groups of counterjet channels are formed between two adjacent partition plates, and the refrigerant is mixed in two or more stages of counterjet mixing in the distributor.

12. The liquid dividing baffle according to claim 1, wherein The distributor comprises a plurality of counterjet units, each counterjet unit comprises two or more partition plates, and a plurality of groups of counterjet channels are formed between two adjacent partition plates of each counterjet unit; and no counterjet channels are formed between adjacent counterjet units.

13. A dispenser characterized in that, A distributor is provided and comprises: a distributor body; the distributor further comprises a plurality of partition plates arranged in axial staggered distribution along the distributor body, each partition plate comprising a plurality of refrigerant ports arranged in circumferential distribution and a solid portion between adjacent refrigerant ports; when two adjacent partition plates are projected in the axial direction of the distributor body, each solid portion of the upper partition plate covers the corresponding refrigerant port of the lower partition plate and overlaps the solid portions on both sides of the corresponding refrigerant port of the lower partition plate to form a group of counterjet channels in which the refrigerant flows in opposite directions and is mixed in each group of counterjet channels; the minimum width L0 of each overlap region formed by the projection overlap of the solid portion of the upper partition plate and the solid portions on both sides of the corresponding refrigerant port of the lower partition plate satisfies 0.5mm≤L0≤3.5mm; the plurality of partition plates are arranged in sequential partial abutment so that the solid portions of two adjacent partition plates have flow channel gaps therebetween; the partition plates further comprise intermediate portions, and the plurality of solid portions are arranged in circumferential distribution around the intermediate portions; at least one intermediate portion of the plurality of partition plates is raised and connected to the intermediate portion of an adjacent partition plate so that the solid portions of two adjacent partition plates are arranged in spaced distribution; the distributor further comprises connecting columns, and the plurality of partition plates are arranged in axial sequence on the connecting columns, and two adjacent partition plates are arranged in partial abutment so that flow channel gaps are formed between the corresponding solid portions; alternatively, two adjacent partition plates are arranged in spaced distribution so that flow channel gaps are formed between the corresponding solid portions; the partition plates are of integral structure, and the intermediate portion of each partition plate is formed with a connecting hole that is sleeved on the connecting column; alternatively, the partition plates comprise a plurality of independent solid portions, and the plurality of solid portions are arranged in spaced distribution in the circumferential direction of the connecting column and are fixed to the connecting column; the distributor further comprises a limiting spacer sleeve that is sleeved on the connecting column, and two adjacent partition plates abut the two ends of the limiting spacer sleeve to be arranged in spaced distribution; the axial spacing H0 between the solid portions of two adjacent partition plates satisfies 0<H0≤3mm; the refrigerant ports are notch grooves that extend continuously in the radial direction of the partition plate to the edge of the partition plate, and the notch grooves are scallop-shaped, rectangular, or have a curved groove wall; the refrigerant ports are one or more combinations of through holes, flanged holes, or arc bubble holes; the distributor comprises three or more partition plates, and a plurality of groups of counterjet channels are formed between two adjacent partition plates, and the refrigerant is mixed in two or more stages of counterjet mixing in the distributor; the distributor comprises a plurality of counterjet units, each counterjet unit comprises two or more partition plates, and a plurality of groups of counterjet channels are formed between two adjacent partition plates of each counterjet unit; and no counterjet channels are formed between adjacent counterjet units.

14. The dispenser of claim 13, wherein, The distributor further comprises a plurality of branch pipes welded to the liquid outlet end of the distributor body, at least one of the branch pipes comprising a branch pipe body and a branch pipe end jet structure arranged downstream of the branch pipe body, the branch pipe end jet structure comprising a transmission pipe section, a fitting pipe section, and a jet portion, the transmission pipe section being arranged downstream of the branch pipe body, the jet portion being arranged near or downstream of the downstream end of the transmission pipe section to accelerate the refrigerant, the jet portion having a jet throat formed at the smallest inner diameter thereof, the inner diameter of the jet throat being smaller than the inner diameter of the downstream end of the transmission pipe section, and the difference Δd between the inner diameters of the jet throat and the downstream end of the transmission pipe section satisfying 0.03mm≤Δd≤1.65mm, the axial length L1 of the jet portion being ≤350mm, the upstream end of the fitting pipe section being connected to the transmission pipe section or the jet portion, the downstream end of the fitting pipe section having an outer diameter larger than the outer diameter of the transmission pipe section to match the external pipe welding.

15. The dispenser of claim 14, wherein, The axial length L2 of the fitting pipe section is ≤35mm, which refers to the total axial length from the upstream end face to the downstream end face of the fitting pipe section.

16. The dispenser of claim 14, wherein, The fitting pipe section is integrally formed at the downstream end of the transmission pipe section, and the jet portion is embeddedly welded at the downstream end of the transmission pipe section or in the fitting pipe section.

17. The dispenser of claim 16, wherein, The jet portion is a jet pipe embedded in the fitting pipe section and welded to the downstream end of the transmission pipe section. Alternatively, the jet portion is a jet orifice plate embeddedly welded near the downstream end of the transmission pipe section or in the fitting pipe section, the jet orifice plate having jet orifices formed thereon and a jet throat formed at the smallest inner diameter of the jet orifices.

18. The dispenser of claim 14, wherein, The fitting pipe section is welded to the downstream end of the transmission pipe section, and the jet portion is arranged at the downstream end of the transmission pipe section or embedded in the fitting pipe section.

19. The dispenser of claim 18, wherein, The jet portion is a jet nozzle integrally formed or welded to the downstream end of the transmission pipe section, the jet nozzle extending into the fitting pipe section and having a jet throat formed at the downstream end thereof.

20. The dispenser of claim 18, wherein, The jet portion is embedded near the downstream end of the transmission pipe section or in the fitting pipe section, the jet portion being a jet pipe or a jet orifice plate, the jet orifice plate having jet orifices formed thereon and a jet throat formed at the smallest inner diameter of the jet orifices.

21. The dispenser of claim 17 or 20, wherein, The jet orifice is a flanged orifice having a hole wall extending towards the downstream end of the fitting pipe section, the downstream end of the flanged orifice having a jet throat formed thereat.

22. The dispenser of claim 17 or 20, wherein, The jet orifice is a through hole formed based on the axial thickness of the jet orifice plate, the jet orifice being an equal-diameter hole having a substantially constant hole diameter. Alternatively, the jet orifice comprises a jet throat and a guide hole section, the guide hole section being upstream of the jet throat and having a hole diameter larger than that of the jet throat. Alternatively, the jet orifice is a Venturi orifice comprising a guide hole section, a jet throat, and a diffusion hole section arranged in sequence along the refrigerant flow direction, the hole diameters of the guide hole section and the diffusion hole section being larger than that of the jet throat.

23. The dispenser of claim 13, wherein, The jet portion is a jet pipe, the upstream end of the jet portion being connected to the transmission pipe section and the downstream end thereof being connected to the fitting pipe section.

24. The dispenser of claim 13, wherein, The transmission pipe section, the jet portion, and the fitting pipe section are arranged in sequence along the refrigerant transmission direction and integrally formed.

25. The dispenser of claim 13, wherein, The branch pipe end jet structure further comprises an outer sleeve pipe welded to the fitting pipe section, the outer sleeve pipe being configured to increase the outer diameter of the fitting pipe section to match the external pipe welding.

26. The dispenser of claim 13, wherein, The distributor further comprises a plurality of branch pipes welded to the liquid outlet end of the distributor body, at least one of the branch pipes comprising a branch pipe body and a branch pipe end jet structure arranged downstream of the branch pipe body, the branch pipe end jet structure comprising a transmission pipe section, a fitting pipe section and a jet portion, the transmission pipe section being arranged downstream of the branch pipe body, the fitting pipe section being arranged downstream of the transmission pipe section to match the external pipeline welding, the jet portion being arranged downstream of the fitting pipe section or being embedded in the fitting pipe section, a jet throat being formed at the smallest inner diameter of the jet portion, the inner diameter of the jet throat being smaller than the inner diameter of the downstream end of the transmission pipe section and the inner diameter of the upper fitting portion of the fitting pipe section respectively, and the inner diameter difference △d between the jet throat and the downstream end of the transmission pipe section satisfying: 0.03mm≤△d≤1.65mm, and the axial length L1 of the jet portion being ≤350mm.

27. The dispenser of claim 26, wherein, The transmission pipe section, the fitting pipe section and the jet portion are sequentially arranged in the transmission direction of the refrigerant and are integrally formed.

Images