Liquid separator and air conditioner

Abstract

The utility model relates to the technical field of air conditioners, in particular to a liquid separator and an air conditioner, the liquid separator comprises an outer pipe body, an inner pipe body and a branch pipe body, the outer pipe body is sleeved on the outer side of the inner pipe body, the outer pipe body and the inner pipe body are connected to define a liquid separation cavity, the inner pipe body is provided with spray holes communicated with the liquid separation cavity, the pipe wall of the outer pipe body is provided with through holes, and the through holes are communicated with the branch pipe body. The branch pipe body is inserted into the through hole and communicated with the liquid separation cavity, the outer diameter of the outer pipe body ranges from 12.2 mm to 13.2 mm, and the hole diameter of the through hole ranges from 4.7 mm to 5.1 mm. The outer diameter range of the outer pipe body and the aperture range of the through hole can meet the liquid separation requirement of the liquid separator, meanwhile, the refrigerant circulation requirement of a heat exchanger is met, the liquid separator is adaptive to various air conditioner types to the maximum extent, the fewest materials are used when the liquid separator is machined, and the manufacturing cost is reduced.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and in particular to a liquid dispenser and an air conditioner. Background Technology

[0002] In an air conditioning circulation system, a distributor allocates the two-phase refrigerant (gas and liquid) to the various pipes of the evaporator for heat exchange. If the distributor's distribution is uneven, the refrigerant in the high-flow-rate branches will not evaporate completely, while the refrigerant in the low-flow-rate branches will evaporate prematurely, resulting in wasted heat exchange area. Therefore, the uniformity of the distributor's distribution directly affects the evaporator's heat exchange capacity, and thus the air conditioning performance. The heat exchanger capacity reduction due to uneven distribution can reach up to 25%.

[0003] Currently, the Venturi dispenser is a widely used type of dispenser. However, the Venturi dispenser requires a large number of dispensing capillaries, which results in high cost and large size. Furthermore, in order to achieve better dispensing results, the length of each capillary needs to be adjusted, which is a complicated process and product consistency cannot be guaranteed. Utility Model Content

[0004] This utility model provides a liquid distributor and an air conditioner to solve one of the defects in the prior art. The outer diameter range of the outer tube and the orifice diameter range meet the liquid distribution requirements of the liquid distributor and the refrigerant flow requirements of the heat exchanger. It can be adapted to a variety of air conditioner models to the greatest extent and ensures that the material used in the processing of the liquid distributor is minimized, thereby reducing manufacturing costs.

[0005] This utility model provides a liquid separator, including an outer tube, an inner tube, and a branch tube. The outer tube is sleeved on the outside of the inner tube and connected to the inner tube to form a liquid separation chamber. The inner tube has a spray hole communicating with the liquid separation chamber. The outer tube has a through hole in its wall. The branch tube is inserted into the through hole and communicates with the liquid separation chamber. The outer diameter of the outer tube is between 12.2 mm and 13.2 mm, and the diameter of the through hole is between 4.7 mm and 5.1 mm.

[0006] According to the present invention, the outer diameter of the branch tube is between 4.56 mm and 4.96 mm.

[0007] According to the present invention, the wall thickness of the outer tube is between 0.5 mm and 0.9 mm.

[0008] According to the present invention, the outer diameter of the inner tube is between 6.15 mm and 6.55 mm.

[0009] According to the present invention, the diameter of the spray nozzle is between 1.5 mm and 2.8 mm.

[0010] According to the present invention, the distance between two adjacent spray holes is between 5 mm and 20 mm.

[0011] According to the present invention, a liquid separator is provided in which the outer wall of the branch tube is provided with a first positioning part, the first positioning part abutting against the outer wall of the outer tube, and the distance between the end face of the branch tube inserted into the outer tube and the inner wall of the outer tube is between 2mm and 3mm.

[0012] According to the present invention, a liquid separator is provided, wherein the spray hole is disposed on the side of the inner tube body opposite to the branch tube body; the spray hole is provided with a second positioning part, and the lower opening of the outer tube body is provided with a third positioning part, the second positioning part abuts against the third positioning part, and the angle between the projection of the line connecting the second positioning part and the center of the inner tube body and the line connecting the spray hole and the center of the inner tube body on the horizontal plane is a set angle.

[0013] According to the present invention, a liquid separator is provided, wherein the upper port of the inner tube is screw-sealed, and the lower port of the inner tube is adapted to be connected to the outlet of an expansion valve.

[0014] This utility model also provides an air conditioner, including the liquid dispenser as described above.

[0015] The liquid distributor provided by this utility model comprises an outer tube and an inner tube forming a main body. The outer tube is sleeved on the outside of the inner tube, and both the upper and lower openings of the outer tube are sealed to the outer wall of the inner tube. This creates a liquid distribution chamber between the outer wall of the inner tube and the inner wall of the outer tube. Multiple branch tubes are connected to the outer tube and communicate with the liquid distribution chamber. The outer tube wall has through holes communicating with the liquid distribution chamber, and the ends of the branch tubes pass through these holes and are inserted into the chamber. The refrigerant in the inner tube is injected into the liquid distribution chamber between the inner and outer tubes through nozzles. After being reflected by the inner wall of the outer tube, it is evenly dispersed within the chamber and then distributed to different flow paths of the heat exchanger through the branch tubes for heat exchange.

[0016] After repeated testing, debugging, and verification, the outer diameter of the outer tube was limited to between 12.2mm and 13.2mm, and the diameter of the through hole was limited to between 4.7mm and 5.1mm. This ensures that the outer diameter range of the outer tube and the diameter range of the through hole meet the liquid distribution requirements of the distributor, while also meeting the refrigerant flow requirements of the heat exchanger. This maximizes compatibility with various air conditioning models and ensures that the material used in the processing of the distributor is minimized, thus reducing manufacturing costs. Attached Figure Description

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

[0018] Figure 1 This is one of the structural schematic diagrams of the liquid dispenser provided in this embodiment of the utility model;

[0019] Figure 2 yes Figure 1 A magnified view of a portion of the image;

[0020] Figure 3 This is a schematic diagram of the inner tube of the liquid separator provided in this embodiment of the utility model;

[0021] Figure 4 This is the second schematic diagram of the liquid separator provided in this embodiment of the utility model;

[0022] Figure 5 This is the third schematic diagram of the liquid separator provided in this embodiment of the utility model;

[0023] Figure 6 This is the fourth schematic diagram of the liquid separator provided in this embodiment of the utility model;

[0024] Figure 7 This is the fifth schematic diagram of the liquid separator provided in this embodiment of the utility model.

[0025] Figure label:

[0026] 100. Outer tube body; 110. Through hole;

[0027] 200. Inner tube body; 210. Spray nozzle; 220. Second positioning part; 230. Pipe section;

[0028] 300. Separating chamber;

[0029] 400, branch pipe body; 410, first positioning part. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0031] like Figure 1 and Figure 2 As shown, the liquid separator provided in this embodiment of the present invention includes an outer tube 100, an inner tube 200, and a branch tube 400. The outer tube 100 is sleeved on the outside of the inner tube 200 and connected to the inner tube 200 to form a liquid separation chamber 300. The inner tube 200 is provided with a spray hole 210 that communicates with the liquid separation chamber 300. The tube wall of the outer tube 100 is provided with a through hole 110. The branch tube 400 is inserted into the through hole 110 and communicates with the liquid separation chamber 300. The outer diameter of the outer tube 100 is between 12.2 mm and 13.2 mm, and the diameter of the through hole 110 is between 4.7 mm and 5.1 mm.

[0032] In this embodiment of the liquid separator, the outer tube 100 and the inner tube 200 together form the main tube. The outer tube 100 is sleeved on the outside of the inner tube 200. The upper and lower openings of the outer tube 100 are both sealed to the outer wall of the inner tube 200. Thus, the space between the outer wall of the inner tube 200 and the inner wall of the outer tube 100 forms a liquid separation chamber 300. That is, the outer tube 100 surrounds the liquid separation chamber 300 on the outside of the inner tube 200. Multiple branch tubes 400 are connected to the outer tube 100 and communicate with the liquid separation chamber 300. The tube wall of the outer tube 100 is provided with a through hole 110 communicating with the liquid separation chamber 300. The ends of the branch tubes 400 pass through the through hole 110 and are inserted into the liquid separation chamber 300. Therefore, the refrigerant in the inner tube 200 is injected into the liquid distribution chamber 300 between the inner tube 200 and the outer tube 100 through the nozzle 210. After being reflected by the inner wall of the outer tube 100, it is evenly dispersed in the liquid distribution chamber 300 and then distributed to different flow paths of the heat exchanger through each branch tube 400 for heat exchange.

[0033] After repeated testing, debugging, and verification, the outer diameter of the outer tube 100 was limited to between 12.2mm and 13.2mm, and the diameter of the through hole 110 was limited to between 4.7mm and 5.1mm. This ensures that the outer diameter range of the outer tube 100 and the diameter range of the through hole 110 meet the liquid distribution requirements of the distributor, while also meeting the refrigerant flow requirements of the heat exchanger. This maximizes compatibility with various air conditioning models and minimizes the amount of material used in the processing of the distributor, thus reducing manufacturing costs.

[0034] In this embodiment, the outer diameter of the outer tube 100 can be selected as 12.7 mm, and the diameter of the through hole 110 can be selected as 4.9 mm.

[0035] According to one embodiment of the present invention, the outer diameter of the branch pipe body 400 is between 4.56 mm and 4.96 mm. In this embodiment, the diameter of the through hole 110 is between 4.7 mm and 5.1 mm, so the outer diameter of the corresponding branch pipe body 400 is limited to between 4.56 mm and 4.96 mm. When the diameter of the through hole 110 is 4.7 mm, the outer diameter of the branch pipe body 400 is 4.56 mm; when the diameter of the through hole 110 is 5.1 mm, the outer diameter of the branch pipe body 400 is 4.96 mm, ensuring an insertion gap of 0.14 mm between the through hole 110 and the branch pipe body 400.

[0036] In this embodiment, the diameter of the through hole 110 can be selected as 4.9 mm, and the outer diameter of the branch pipe body 400 can be selected as 4.76 mm.

[0037] According to one embodiment of the present invention, the length of the portion of the branch pipe 400 located between the outer wall of the outer pipe and the outer wall of the inner pipe 200 is greater than or equal to the wall thickness of the outer pipe 100 and less than one-third of a set length, wherein the set length is the difference between the outer diameter of the outer pipe 100 and the outer diameter of the inner pipe 200.

[0038] The inlet of the branch pipe 400 is located inside the liquid distribution chamber 300. The distance between the inlet and the orifice 110 on the outer wall of the outer pipe 100 is the insertion depth of the branch pipe 400 in the outer pipe 100. The insertion depth of the branch pipe 400 affects the liquid distribution effect. If it is inserted too deeply, the inlet of the branch pipe 400 will be too close to the inner pipe 200, and the flow cross-sectional area formed between the inner pipe 200 and the branch pipe 400 in the liquid distribution chamber 300 will be reduced, thereby reducing the amount of refrigerant entering the branch pipe 400. If it is inserted too shallowly, the connection between the branch pipe 400 and the through hole 110 of the outer pipe 100 will be weak and prone to breakage, causing refrigerant leakage. Therefore, the insertion depth of the branch pipe 400 is designed to be within the set range, i.e., δ≤ds<(D1-D2) / 3, where ds is the insertion depth of the branch pipe, δ is the wall thickness of the outer pipe 100, D1 is the outer diameter of the outer pipe 100, and D2 is the outer diameter of the inner pipe 200.

[0039] In this embodiment, the distance between the end face of the branch pipe 400 inserted into the outer pipe 100 and the inner wall of the outer pipe 100 is between 2mm and 3mm.

[0040] This utility model's separator, through the structural cooperation of the inner tube 200, outer tube 100, and branch tube 400, replaces the existing Venturi-type separator, fundamentally changing its structure. It solves the problems associated with existing Venturi-type separators, eliminating the need for capillary dispensing tubes and capillary length adjustments. Furthermore, the insertion depth design of the branch tube 400 further improves the dispensing effect and structural strength. This utility model's separator has a simple structure, is easy to install and adjust, has low cost, provides good dispensing effect, and its dimensions are easily controlled during manufacturing. Its shape can be flexibly adjusted according to the actual conditions of the heat exchanger.

[0041] According to one embodiment of the present invention, the outer wall of the branch pipe body 400 is provided with a first positioning part 410, which abuts against the outer wall of the outer pipe body 100. In this embodiment, during the manufacturing process of the branch pipe body 400, since the insertion depth of the branch pipe body 400 on the outer pipe body 100 is determined first, the first positioning part 410 is provided on the corresponding length of the outer wall of the branch pipe body 400.

[0042] When assembling the branch pipe body 400 with the outer pipe body 100, the branch pipe body 400 is inserted into the through hole 110 until the first positioning part 410 contacts the outer wall around the through hole 110 of the outer pipe body 100, at which point the insertion is stopped. The first positioning part 410 can be a positioning protrusion, which can block the process of the branch pipe body 400 being inserted into the through hole 110 when the branch pipe body 400 reaches the insertion depth.

[0043] According to one embodiment of the present invention, the nozzle 210 is disposed on the inner tube 200 on the side opposite to the branch tube 400. In this embodiment, multiple branch tubes 400 are arranged sequentially along the axial direction of the outer tube 100 and concentrated on one side of the outer tube 100. Multiple nozzles 210 are also arranged sequentially along the axial direction of the inner tube 200 and concentrated on one side of the inner tube 200. The side of the inner tube 200 where the nozzle 210 is located is opposite to the side of the inner tube 200 towards which the outlet of the branch tube 400 faces. That is, the direction in which the refrigerant is ejected at the nozzle 210 is opposite to the direction in which the refrigerant flows into the branch tube 400 from the outlet of the branch tube 400.

[0044] The refrigerant is sprayed from the nozzle 210 into one side of the liquid distribution chamber 300. Then, the refrigerant in the liquid distribution chamber 300 enters the branch pipe body 400 from the other side of the liquid distribution chamber 300. This increases the residence and mixing time of the refrigerant in the liquid distribution chamber 300, increases the flow path length of the refrigerant in the liquid distribution chamber 300, and increases the number of reflections and the path of the refrigerant between the inner walls of the outer pipe body 100, thereby further improving the liquid distribution effect.

[0045] like Figure 3 and Figure 4As shown, according to an embodiment of the present invention, the inner tube 200 is inserted into the outer tube 100 from bottom to top. The outer wall of the inner tube 200 is provided with a second positioning part 220. The second positioning part 220 abuts against the end face of the lower opening of the outer tube 100. The distance between the second positioning part 220 and the upper opening of the inner tube 200 is greater than the length of the outer tube 100.

[0046] In this embodiment, the inner tube 200 passes through the lower opening of the outer tube 100 to the upper opening of the outer tube 100, and the upper opening of the inner tube 200 extends out of the outer tube 100. During the assembly process of the inner tube 200 and the outer tube 100, the upper opening of the inner tube 200 first passes through the lower opening of the outer tube 100 and enters the interior of the outer tube 100, and then exits through the upper opening of the outer tube 100.

[0047] The position of the nozzle 210 on the inner tube 200 is fixed, and the relative position between the nozzle 210 of the inner tube 200 and each branch tube 400 plays a decisive role in the liquid distribution effect. During the actual assembly of the inner tube 200 and the outer tube 100, if the insertion depth cannot be accurately controlled, the relative position of the nozzle 210 of the inner tube 200 and the branch tube 400 will change, resulting in the actual refrigerant volume in each branch tube 400 not matching the expected value. Therefore, to ensure that the relative position of the nozzle 210 and the branch tube 400 remains consistent with the design value during manufacturing, a second positioning part 220 needs to be provided on the outer wall of the inner tube 200.

[0048] When the inner tube 200 penetrates the outer tube 100 from bottom to top, the insertion can be stopped when the second positioning part 220 contacts the end face of the lower opening of the outer tube 100. At this time, in order to ensure that the upper opening of the inner tube 200 can pass through the upper opening of the outer tube 100, the length of the inner tube 200 above the second positioning part 220 needs to be greater than the length of the outer tube 100, that is, a > L, where L is the total length of the outer tube 100 and a is the total length of the inner tube 200 above the second positioning part 220. Thus, when the inner tube 200 reaches the position of the second positioning part 220, the outer tube 100 can block the insertion process of the inner tube 200. At this time, the positioning is completed, and the next welding work can be carried out.

[0049] In this embodiment, the second positioning part 220 may be a positioning protrusion.

[0050] According to an embodiment of the present invention, the lower opening of the outer tube 100 is provided with a third positioning part 130, the second positioning part 220 abuts against the third positioning part 130, and the angle between the line connecting the second positioning part 220 and the center of the inner tube 200 and the projection of the line connecting the nozzle 210 and the center of the inner tube 200 on the horizontal plane is a set angle.

[0051] In this embodiment, the projections of the centers of the nozzle 210, the second positioning part 220, and the inner tube 200 onto the horizontal plane can form an angle, the angle of which can be determined according to actual needs. During assembly, the inner tube 200 is inserted into the outer tube 100, and the orientation of the nozzle 210 on the inner tube 200 cannot be known. Based on the position of the third positioning part 130 on the outer tube 100, the second positioning part 220 of the inner tube 200 is positioned at the third positioning part 130. The position of the third positioning part 130 can be pre-determined to match the through hole 110. Combined with the set angle, the orientation of the nozzle 210 can be determined, thereby adjusting the refrigerant spray direction of the nozzle 210 to ensure that the nozzle 210 is set away from the through hole 110.

[0052] In this embodiment, the angle can be set to 180° or 90°.

[0053] According to one embodiment of the present invention, the distance between the nozzle 210 and the second positioning part 220 is between a first set distance and a second set distance. The first set distance is the length of the lower contraction section of the outer tube 100, and the second set distance is the difference between the length of the outer tube 100 and the length of the lower contraction section of the outer tube 100.

[0054] In this embodiment, the arrangement of the nozzle 210 on the inner tube 200 must satisfy the requirement that after the inner tube 200 penetrates the outer tube 100 and is positioned by the second positioning part 220, the nozzle 210 can be entirely located within the space of the liquid distribution chamber 300. Therefore, during the manufacturing process of the inner tube 200, the position of the second positioning part 220 can be determined first. After the position of the second positioning part 220 is determined, the position and size of the nozzle 210 on the inner tube 200 are determined according to the actual situation, with the second positioning part 220 as the reference.

[0055] Understandably, the outer diameter of the inner tube 200 is much smaller than the inner diameter of the outer tube 100. Therefore, to ensure that a closed liquid-separating cavity 300 is formed between the outer tube 100 and the inner tube 200, the upper and lower openings of the outer tube 100 are tightened to form an upper contraction section and a lower contraction section, with the inner walls of both sections tightly adhering to the outer wall of the inner tube 200. Both the upper and lower contraction sections of the outer tube 100 have a certain length, which can be the same or different, depending on the specific circumstances.

[0056] In this embodiment, after the position of the second positioning part 220 is determined, the distance between the other nozzles 210 on the inner tube 200 and the second positioning part 220 is determined based on the actual situation, using the second positioning part 200 as a reference. Figure 3The distances from the lowest nozzle 210 to the second positioning part 220 should be greater than the length m of the lower contraction section of the outer tube 100. The positioning dimensions of the remaining nozzles 210 should satisfy m < e < d < c < b < a ≤ 2L.

[0057] According to one embodiment of the present invention, a plurality of nozzles 210 are arranged sequentially along the axial direction of the inner tube 200. The distance between two adjacent nozzles 210 is between the diameter of the nozzle 210 and a third predetermined distance. The third predetermined distance is the difference between the length of the outer tube 100 and the sum of the length of the upper contraction section of the outer tube 100, the length of the lower contraction section of the outer tube 100, and the diameter of the nozzle 210.

[0058] In this embodiment, the range of the nozzles 210 needs to be limited to the height range of the dispensing chamber 300, and the distance between adjacent nozzles 210 also plays a decisive role in the dispensing effect. The distance between any two adjacent nozzles 210... l i φ should satisfy < l i <L-2m-φ, where φ is the diameter of nozzle 210.

[0059] In this embodiment, the orifice diameter of the nozzle 210 is between 1.5mm and 2.8mm, and the distance between two adjacent nozzles 210 is between 5mm and 20mm. The actual orifice diameter and distance vary depending on the machine model and flow path.

[0060] In some cases, due to limited internal space in the air conditioner or interference between refrigerant pipes, the refrigerant needs to enter the distributor from top to bottom.

[0061] like Figure 7 As shown, according to one embodiment of this utility model, the lower end of the outer tube 100 is closed, and the inner tube 200 is inserted into the outer tube 100 from top to bottom through the upper opening of the outer tube 100. In this embodiment, the refrigerant enters the distributor through the upper opening of the inner tube 200, that is, it flows from top to bottom in the inner tube 200. Since the density of liquid refrigerant is much greater than that of gaseous refrigerant, the liquid refrigerant will accumulate at the bottom under the influence of gravity. To avoid this situation, the lower opening of the outer tube 100 is closed, that is, the inner tube 200 is inserted into the outer tube 100 but does not penetrate the outer tube 100, and the lower opening of the inner tube 200 is located inside the outer tube 100.

[0062] After the refrigerant enters the liquid distribution chamber 300, the flow rate of the refrigerant increases because the inner tube 200 does not penetrate the outer tube 100. Further improvements are made to the bottom of the liquid distributor to reduce the accumulation of liquid refrigerant at the bottom of the liquid distribution chamber 300.

[0063] According to one embodiment of this utility model, the lower end of the inner tube 200 is closed and abuts against the closed surface of the lower end of the outer tube 100. In this embodiment, the lower port of the inner tube 200 inside the outer tube 100 is also closed. To ensure that the inner tube 200 has sufficient length inside the outer tube 100 and that the refrigerant flow meets the requirements, the length of the inner tube 200 inserted into the outer tube 100 is controllable, facilitating the assembly operation of the inner tube 200 and the outer tube 100. The lower closed end of the inner tube 200 is abutted against the lower closed end of the outer tube 100, that is, the inner tube 200 is inserted to the bottom of the outer tube 100.

[0064] According to one embodiment of this utility model, the outer diameter of the inner tube 200 is greater than 4 mm, and the wall thickness of the outer tube 100 is greater than 0.5 mm. In this embodiment, the outer diameter D2 of the inner tube 200 should be greater than 4 mm, and the outer diameter D1 of the outer tube 100 should satisfy D1 > D2 + 2δ, wherein the wall thickness δ of the outer tube 100 should be greater than 0.5 mm to ensure the pressure resistance of the outer tube 100.

[0065] In this embodiment, the wall thickness of the outer tube 100 ranges from 0.5 mm to 0.9 mm, and can be selected as 0.7 mm. The outer diameter of the inner tube 200 ranges from 6.15 mm to 6.55 mm, and can be selected as 6.35 mm.

[0066] like Figure 5 As shown, according to one embodiment of the present invention, the refrigerant in the inner tube 200 flows from bottom to top, and the inner diameter of the inner tube 200 located inside the outer tube 100 gradually decreases along the flow direction of the refrigerant in the inner tube 200. In this embodiment, the inner tube 200 is inserted into the outer tube 100 from bottom to top, and the refrigerant also flows from bottom to top in the inner tube 200. After entering the outer tube 100 from the lower opening of the outer tube 100, the inner diameter of the inner tube 200 changes, and the inner diameter of the inner tube 200 gradually decreases along the flow direction of the refrigerant inside.

[0067] During the flow of refrigerant from the lower inlet to the upper inlet of the inner pipe body 200, the refrigerant flow rate decreases due to the continuous reduction in refrigerant volume and the influence of gravity. This results in a lower refrigerant flow rate at higher elevations, which hinders the refrigerant from being smoothly ejected from the nozzle 210 and entering the branch pipe body 400. Therefore, the inner diameter of the inner pipe body 200 needs to decrease along the refrigerant flow direction after entering the outer pipe body 100 to prevent the refrigerant flow rate from becoming too low. Specifically, 0 ≤ D21 < D22, where D21 is the inner diameter of the inner pipe body 200 after entering the outer pipe body 100, and D22 is the inner diameter of the inner pipe body 200 before entering the outer pipe body 100.

[0068] According to one embodiment of the present invention, the inner tube 200 passes through the lower opening of the outer tube 100 to the upper opening of the outer tube 100, and exits through the upper opening of the outer tube 100. In this embodiment, the upper opening of the inner tube 200 enters the interior of the outer tube 100 through the lower opening of the outer tube 100, and then exits through the upper opening of the outer tube 100, thus penetrating the outer tube 100. Before entering the outer tube 100, the inner diameter of the inner tube 200 remains unchanged. After entering the outer tube 100, the inner diameter of the inner tube 200 gradually decreases, and after exiting the outer tube 100, the inner diameter of the inner tube 200 remains the reduced inner diameter.

[0069] In other embodiments, the inner tube 200 may also be non-penetrating, meaning that both the upper opening of the inner tube 200 and the upper opening of the outer tube 100 may be closed. The upper opening of the inner tube 200 is screw-sealed, and the lower opening of the inner tube 200 is adapted to connect with the outlet of the expansion valve.

[0070] According to one embodiment of this utility model, the inner diameter of the upper opening of the inner tube 200 is larger than the orifice diameter of the nozzle 210. In this embodiment, to prevent excessive resistance caused by structural changes in the inner tube 200 when the refrigerant flows within the gradually narrowing inner tube 200, thus affecting the liquid discharge from the nozzle 210, and to ensure that the nozzle 210 can be formed normally in the inner tube 200, the inner diameter of the upper opening of the inner tube 200 must be larger than the orifice diameter of the nozzle 210, i.e., D21 > D20, where D21 is the inner diameter of the upper opening of the inner tube 200 and D20 is the orifice diameter of the inner tube 200.

[0071] In some embodiments, the diameter of the nozzle 210 closest to the top may be limited. Since the nozzle 210 closest to the upper opening of the inner tube 200 receives the greatest resistance, the diameter of the nozzle 210 closest to the upper opening of the inner tube 200 may be limited to be smaller than the inner diameter of the upper opening of the inner tube 200.

[0072] like Figure 6As shown, according to an embodiment of this utility model, the inner tube 200 located within the outer tube 100 includes multiple tube segments 230, the inner diameters of which decrease sequentially along the flow direction of the refrigerant in the inner tube 200. In this embodiment, the inner diameter of the inner tube 200 after entering the outer tube 100 can be a stepped change in addition to a gradually changing structure. In the stepped change, the inner tube 200 located inside the outer tube 100 is divided into multiple tube segments 230 along its axial direction, and the inner diameter of each tube segment 230 should decrease progressively from bottom to top. To prevent excessive resistance in the uppermost tube segment 230 from affecting the liquid discharge from the uppermost nozzle 210, and to ensure that the inner tube 200 can open normally, the inner diameter of the last tube segment 230 should ensure that D21 > D20. Here, D21 is the inner diameter of the last tube segment 230, and D20 is the diameter of the uppermost nozzle 210 of the inner tube 200.

[0073] According to one embodiment of this utility model, the number of pipe segments 230 is less than or equal to the number of nozzles 210, and each pipe segment 230 is provided with at least one nozzle 210. In this embodiment, when the diameter of the inner pipe body 200 decreases in a stepwise manner along the refrigerant flow direction, the diameter of each step of the pipe segment 230 along the refrigerant flow direction should decrease step by step. The number N of the stepwise changes of the inner pipe body 200 is determined by the number n of nozzles 210, and each pipe segment 230 should have at least one nozzle 210, i.e., 1≤N≤n.

[0074] According to one embodiment of this utility model, the difference in cross-sectional area between two adjacent pipe segments 230 is between the total area of ​​the nozzles 210 on the pipe segment 230 with the larger cross-sectional area and half of the cross-sectional area of ​​the pipe segment 230 with the larger cross-sectional area. In this embodiment, the two adjacent pipe segments 230, as two pipe segments 230 in the stepped reduction process of the inner pipe body 200, necessarily have one with a larger cross-sectional area and the other with a smaller cross-sectional area. The larger cross-sectional area S i With a smaller cross-sectional area S i+1 The difference between them should satisfy A≤S i - S i+1 ≤0.5S i , where A is the total area of ​​the nozzles 210 on the pipe section 230 with the larger cross-sectional area.

[0075] The air conditioner provided by this utility model is described below. The air conditioner described below and the liquid separator described above can be referred to in correspondence.

[0076] This utility model embodiment also provides an air conditioner, including a liquid distributor as described in the above embodiment.

[0077] The air conditioner of this embodiment features a distributor. In the air conditioning circulation system, the distributor distributes the gas-liquid two-phase refrigerant to the various pipes of the evaporator for heat exchange. Using the distributor of this embodiment ensures uniform distribution, guaranteeing complete evaporation of the refrigerant in the high-flow-rate branches and preventing premature evaporation of the refrigerant in the low-flow-rate branches, thus avoiding wasted heat exchange area. Therefore, the uniform distribution of the refrigerant in this embodiment directly affects the heat exchange capacity of the evaporator, improving air conditioning performance and avoiding the problem of reduced heat exchanger capacity caused by uneven distribution.

[0078] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, and not to limit it. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this utility model.

Claims

1. A liquid dispenser, characterized in that, The device includes an outer tube (100), an inner tube (200), and a branch tube (400). The outer tube (100) is fitted over the outer side of the inner tube (200) and connected to the inner tube (200) to form a liquid distribution chamber (300). The inner tube (200) has a spray hole (210) that communicates with the liquid distribution chamber (300). The outer tube (100) has a through hole (110) in its wall. The branch tube (400) is inserted into the through hole (110) and communicates with the liquid distribution chamber (300). The outer diameter of the outer tube (100) is between 12.2 mm and 13.2 mm, and the diameter of the through hole (110) is between 4.7 mm and 5.1 mm.

2. The dispenser according to claim 1, characterized in that, The outer diameter of the branch pipe (400) is between 4.56 mm and 4.96 mm.

3. The dispenser according to claim 1, characterized in that, The wall thickness of the outer tube (100) is between 0.5 mm and 0.9 mm.

4. The dispenser according to claim 1, characterized in that, The outer diameter of the inner tube (200) is between 6.15 mm and 6.55 mm.

5. The dispenser according to claim 1, characterized in that, The diameter of the nozzle (210) is between 1.5 mm and 2.8 mm.

6. The dispenser according to claim 1, characterized in that, The distance between two adjacent nozzles is between 5 mm and 20 mm.

7. The dispenser according to claim 1, characterized in that, The outer wall of the branch pipe body (400) is provided with a first positioning part (410), the first positioning part (410) abuts against the outer wall of the outer pipe body (100), and the distance between the end face of the branch pipe body (400) inserted into the outer pipe body (100) and the inner wall of the outer pipe body (100) is between 2mm and 3mm.

8. The dispenser according to claim 1, characterized in that, The nozzle (210) is located on the inner tube (200) on the side opposite to the branch tube (400); the nozzle is provided with a second positioning part (220), and the lower opening of the outer tube (100) is provided with a third positioning part (130). The second positioning part (220) abuts against the third positioning part (130), and the angle between the line connecting the second positioning part (220) and the center of the inner tube (200) and the line connecting the nozzle (210) and the center of the inner tube (200) on the horizontal plane is a set angle.

9. The dispenser according to any one of claims 1 to 8, characterized in that, The upper port of the inner tube (200) is spun sealed, and the lower port of the inner tube (200) is adapted to communicate with the outlet of the expansion valve.

10. An air conditioner, characterized in that, Includes the dispenser as described in any one of claims 1 to 9.

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