Liquid distributor and air conditioner

Abstract

The application relates to the air conditioning technical field, in particular to a distributor and an air conditioner, the distributor comprises an outer pipe body and an inner pipe body, the outer pipe body is sleeved outside the inner pipe body and is connected with the inner pipe body to enclose a distribution cavity, the inner pipe body is provided with a spray hole communicated with the distribution cavity, and the inner wall of the inner pipe body is provided with a protruding turbulence part. The adverse effects of different flow states such as gas-liquid separation and annular flow generated in the upward flowing process of refrigerant on the distribution effect of the integrated distributor can be overcome, and the distribution uniformity is improved.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more particularly to a liquid distributor 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] Since the refrigerant entering the distributor is in a gas-liquid mixed state, when there is a bend or other structure in front of the distributor, the gas and liquid refrigerant will separate under the influence of centrifugal force and gravity. In addition, even if there is no bend in front of the distributor, when the distributor is relatively high, due to the high density and low flow velocity of the liquid refrigerant, the liquid refrigerant will gradually converge on the wall and form a ring flow during the upward flow.

[0004] When the refrigerant flow becomes annular or stratified, if the nozzles of the distributor's inner tube are vertically aligned in the same direction, only a small amount of liquid refrigerant near the nozzles will be successfully ejected, while the liquid refrigerant further away from the nozzles will not be ejected in time. This un-ejected portion of refrigerant will continue to flow forward along the flow direction, eventually converging at the end or middle, resulting in a significant increase in the amount of liquid refrigerant ejected from the nozzles near the convergence point, thus causing uneven refrigerant distribution. Summary of the Invention

[0005] This invention provides a liquid distributor and an air conditioner to address one of the shortcomings of the prior art. It can overcome the adverse effects of different flow states, such as gas-liquid separation caused by pipe bends and annular flow generated during the upward flow of refrigerant, on the liquid distribution effect of the integrated liquid distributor, thereby improving the uniformity of liquid distribution.

[0006] This invention provides a liquid dispenser, comprising an outer tube and an inner tube. The outer tube is sleeved on the outside of the inner tube and connected to it to form a liquid dispensing chamber. The inner tube has a spray hole communicating with the liquid dispensing chamber, and the inner wall of the inner tube has a protruding turbulence-inducing portion. According to a liquid separator provided by the present invention, the turbulence section includes a first protrusion that extends spirally along the axial direction of the inner tube.

[0007] According to a liquid dispenser provided by the present invention, the first protrusion is a helical spring, or the first protrusion is integrally formed with the inner tube body.

[0008] According to a liquid separator provided by the present invention, the flow-dispersing part includes a second protrusion, the second protrusion extending circumferentially along the inner tube in an annular shape, and the second protrusion being offset from the spray hole.

[0009] According to a liquid separator provided by the present invention, the cross-sectional area of ​​the inner wall of the second protrusion gradually decreases along the refrigerant flow direction in the inner tube.

[0010] According to a liquid separator provided by the present invention, the inner wall of the inner tube is provided with a plurality of second protrusions in sequence along its axial direction, and the interval between two adjacent second protrusions is less than or equal to 15 times the inner diameter of the inner tube.

[0011] According to a liquid separator provided by the present invention, the inner tube body is provided with at least two rows of spray holes, each row of spray holes is distributed sequentially along the axial direction of the inner tube body, and the orientation of each spray hole on the inner tube body between two adjacent spray holes in each row of spray holes is different.

[0012] According to a liquid separator provided by the present invention, a flow rectifying component is provided at the liquid inlet of the inner tube.

[0013] According to a liquid separator provided by the present invention, the rectifier component includes at least one of a filter screen and a guide vane.

[0014] The present invention also provides an air conditioner, including the liquid dispenser as described above.

[0015] In this embodiment of the liquid separator, the outer tube and the inner tube together form the main tube. The outer tube is sleeved on the outside of the inner tube, and both the upper and lower ends of the outer tube are sealed to the outer wall of the inner tube. Thus, the space between the outer wall of the inner tube and the inner wall of the outer tube forms a liquid-dispensing cavity. In other words, the outer tube surrounds the liquid-dispensing cavity on the outside of the inner tube. Multiple branch tubes are connected to the outer tube and communicate with the liquid-dispensing cavity. The inner tube has spray holes within the liquid-dispensing cavity that communicate with it, and the inner tube has protrusions extending from its inner wall into the tube as flow-tightening parts.

[0016] Because the characteristic of annular flow is that the liquid refrigerant flows upward along the inner wall of the inner tube, a turbulence section is provided on the inner wall of the inner tube. When the liquid refrigerant flowing on the inner wall of the inner tube encounters the turbulence section, its flow direction is changed under the action of the turbulence section, disrupting the original vertical upward flow of the refrigerant liquid along the axial direction of the inner tube. Under the turbulence effect of the turbulence section, the gas-liquid separation of the refrigerant in the distributor can be disrupted, causing some of the refrigerant to remix. This invention can overcome the adverse effects of different flow states, such as gas-liquid separation caused by pipe bends and annular flow generated during the upward flow of refrigerant, on the liquid distribution effect of the integrated distributor, thus improving the uniformity of liquid distribution. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in this invention 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 invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the liquid dispenser provided in an embodiment of the present invention; Figure 2 This is one of the cross-sectional views of the liquid separator provided in the embodiments of the present invention; Figure 3 This is one of the structural schematic diagrams of the inner tube of the liquid separator provided in the embodiments of the present invention; Figure 4 This is a second cross-sectional view of the liquid separator provided in the embodiment of the present invention; Figure 5 This is a second schematic diagram of the inner tube of the liquid separator provided in this embodiment of the invention; Figure 6 This is the third schematic diagram of the inner tube of the liquid separator provided in this embodiment of the invention; Figure 7 This is the fourth schematic diagram of the inner tube of the liquid separator provided in this embodiment of the invention; Figure 8 This is the fifth schematic diagram of the inner tube of the liquid separator provided in this embodiment of the invention; Figure 9 This is the third cross-sectional view of the liquid separator provided in the embodiment of the present invention; Figure 10 This is the sixth schematic diagram of the inner tube of the liquid separator provided in this embodiment of the invention; Figure 11 yes Figure 9 A magnified view of part A in the middle.

[0019] Figure label: 100. Outer tube body; 200. Inner tube body; 210. Exhaust port; 220. Spray nozzle; 230. One-way flow channel; 231. Main flow channel; 232. Resistance flow channel; 240. Third protrusion; 250. First protrusion; 260. Second protrusion; 300, Separating chamber; 400, Branch tube body; 500, Filter screen; 600, Guide vane. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0021] The integrated distributor consists of three main parts: an inner tube, an outer tube, and a branch tube. The outer tube has multiple openings in its wall for inserting the branch tube. The inner tube has several nozzles for the refrigerant to enter the dispensing chamber. Compared to traditional Venturi distributors, the integrated distributor has advantages such as smaller size and lower cost.

[0022] However, since the refrigerant entering the distributor is in a gas-liquid mixed state, when there is a bend or other structure in front of the distributor, the gas and liquid refrigerant will separate under the influence of centrifugal force and gravity. In addition, even if there is no bend in front of the distributor, when the distributor is high, due to the high density and low flow velocity of the liquid refrigerant, the liquid refrigerant will gradually converge on the wall and form a ring flow during the upward flow.

[0023] When the refrigerant flow becomes annular or stratified, if the nozzles of the inner tube are vertically aligned in the same direction, only a small amount of liquid refrigerant near the nozzles can be successfully ejected, while the liquid refrigerant farther away cannot be ejected in time. This un-ejected portion of refrigerant will continue to flow forward along the flow direction, eventually converging at the end or middle, resulting in a significant increase in the amount of liquid refrigerant ejected from the nozzles near the convergence point, thus causing uneven refrigerant distribution.

[0024] like Figure 1 and Figure 2 As shown, the liquid dispenser provided in this embodiment of the invention includes an outer tube 100 and an inner tube 200. 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 dispensing chamber 300. The inner tube 200 is provided with a spray hole 220 communicating with the liquid dispensing chamber 300, and the inner wall of the inner tube 200 is provided with a protruding turbulence portion.

[0025] In this embodiment of the liquid separator, an outer tube 100 and an inner tube 200 together form a main tube. The outer tube 100 is sleeved on the outside of the inner tube 200, and both the upper and lower ends of the outer tube 100 are closedly connected 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-dispensing cavity 300. In other words, the outer tube 100 surrounds the liquid-dispensing cavity 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-dispensing cavity 300. The inner tube 200 has spray holes 220 within the liquid-dispensing cavity 300 that communicate with it. The inner tube 200 also has protrusions extending from its inner wall into the tube as flow-tightening parts.

[0026] Because the characteristic of annular flow is that the liquid refrigerant flows upward along the inner wall of the inner tube 200, a flow-tampering section is provided on the inner wall of the inner tube 200. When the liquid refrigerant flowing on the inner wall of the inner tube 200 encounters the flow-tampering section, its flow direction will change under the action of the flow-tampering section, disrupting the original vertical upward flow of the refrigerant liquid along the axial direction of the inner tube 200. Under the turbulence effect of the flow-tampering section, the gas-liquid separation of the refrigerant in the distributor can be disrupted, causing some of the refrigerant to be remixed. This invention can overcome the adverse effects of different flow states, such as gas-liquid separation caused by pipe bends and annular flow generated during the upward flow of refrigerant, on the distribution effect of the integrated distributor, and improve the uniformity of distribution.

[0027] According to one embodiment of the present invention, the flow-dispersing portion includes a first protrusion 250 that extends helically along the axial direction of the inner tube 200. In this embodiment, the flow-dispersing portion is configured as a first protrusion 250 extending helically along the axial direction on the inner wall of the inner tube 200.

[0028] Because the characteristic of annular flow is that the liquid refrigerant flows upward along the inner wall of the inner tube 200, a first protrusion 250 is provided on the inner wall of the inner tube 200. When the liquid refrigerant flowing on the inner wall of the inner tube 200 encounters the first protrusion 250, because the first protrusion 250 is a bolt structure extending along the axial direction of the inner tube 200, the liquid refrigerant will change its flow direction under the guiding effect of the first protrusion 250, changing from the original vertical upward flow along the axial direction of the inner tube 200 to a spiral upward flow. When it rotates to the vicinity of the nozzle 220, it will be discharged from the nozzle 220 into the liquid distribution chamber 300, thereby reducing the problem of liquid refrigerant accumulation at the top of the liquid distribution chamber 300. In addition, the turbulence caused by the first protrusion 250 can also disrupt the gas-liquid separation of the refrigerant in the distributor, causing some of the refrigerant to be remixed. This invention can overcome the adverse effects of different flow states, such as gas-liquid separation caused by pipe bends and annular flow generated during the upward flow of refrigerant, on the liquid distribution effect of the integrated distributor, and improve the uniformity of liquid distribution.

[0029] According to one embodiment of the present invention, the first protrusion 250 is a helical spring, or the first protrusion 250 is integrally formed with the inner tube 200. In this embodiment, the first protrusion 250 and the inner tube 200 are independent structures. The first protrusion 250 is a helical spring. A helical spring is inserted into the interior of the inner tube 200, extending axially along the inner tube 200. The helical spring is in close contact with the inner wall of the inner tube 200. The position of the helical spring in the inner tube 200 is adjustable, thereby avoiding the nozzle 220.

[0030] In other embodiments, the first protrusion 250 may also be an integral structure with the inner tube 200, formed in a spiral shape on the inner wall of the inner tube 200.

[0031] like Figure 3 As shown, according to an embodiment of the present invention, the flow-disrupting part includes a second protrusion 260, which extends circumferentially along the inner tube 200 in an annular shape and is offset from the nozzle 220. In this embodiment, by adding a second protrusion 260 as a flow-disrupting part on the inner wall of the inner tube 200, the accumulation of liquid refrigerant that has been layered inside the inner tube 200 is disrupted, allowing the liquid refrigerant to remix with the gaseous refrigerant. To ensure that the refrigerant inside the inner tube 200 flows smoothly into the dispensing chamber 300, the position of the second protrusion 260 must avoid the nozzle 220. In this embodiment, the second protrusion 260 is positioned between any two adjacent nozzles 220 along the axial direction of the inner tube 200.

[0032] The second protrusion 260 is ring-shaped and is set on the inner wall of the inner tube 200 along the circumference of the inner tube 200. It can turbulent all the refrigerant in the circumference of the inner tube 200, without any omissions or dead angles.

[0033] According to one embodiment of the present invention, the cross-sectional area of ​​the inner wall of the second protrusion 260 gradually decreases along the refrigerant flow direction within the inner tube 200. In this embodiment, the second protrusion 260 is a turbulence-causing structure in the form of a tapering opening along the refrigerant flow direction. The tapering structure can reduce refrigerant impact and reduce noise during refrigerant flow within the inner tube 200.

[0034] In other embodiments, the second protrusion 260 may also adopt other tapered structures, such as annular or conical annular structures.

[0035] According to one embodiment of the present invention, the inner wall of the inner tube 200 is provided with a plurality of second protrusions 260 sequentially along its axial direction, and the interval between two adjacent second protrusions 260 is less than or equal to 15 times the inner diameter of the inner tube 200. In this embodiment, due to the relatively long length of the inner tube 200, the mixed refrigerant will continuously undergo gas-liquid separation during its ascent. Therefore, second protrusions 260 are provided along the entire length of the inner tube 200 corresponding to the liquid distribution chamber 300. However, in order to ensure that the multiple second protrusions 260 can stably achieve turbulence as a turbulence-causing structure, a second protrusion 260 should be provided at certain intervals, and the distance d between adjacent second protrusions 260 should satisfy d≤15Din, where Din is the inner diameter of the inner tube 200.

[0036] In other embodiments, the distance between adjacent second protrusions 260 can be adjusted according to the type of inner tube 200 and the refrigerant flow rate.

[0037] like Figure 4 As shown, according to an embodiment of the present invention, the inner tube 200 is provided with at least two rows of nozzles 220. Each row of nozzles 220 is distributed sequentially along the axial direction of the inner tube 200. The orientation of each nozzle 220 on the inner tube 200 between two adjacent nozzles 220 in each row of nozzles 220 is different.

[0038] In this embodiment, the inner tube 200 is provided with a row of nozzles 220 in the same vertical direction along the axial direction. Each row of nozzles 220 may include multiple nozzles 220 that are evenly or regularly distributed. This allows the inner tube 200 to have nozzles 220 with different orientations in its circumference, which can effectively avoid the problem of uneven liquid distribution caused by the nozzles 220 being distributed only on one side of the inner tube 200 when the refrigerant undergoes gas-liquid separation.

[0039] In one embodiment, the inner tube 200 has two rows of nozzles 220. The two rows of nozzles 220 are symmetrically oriented, forming a bi-directional symmetry. That is, holes are drilled on opposite sides of the inner tube 200, and the drilling direction is not on the same straight line as the axis of the branch tube 400. The angle between the axis of the nozzles 220 and the axis of the branch tube 400 is α, and the nozzles 220 on both sides are symmetrical about the plane containing the axis of the branch tube 400. The arrows in the figure indicate the direction of refrigerant flow. In this embodiment, the angle α is in the range of 45° ≤ α < 180°.

[0040] like Figure 5 As shown, in one embodiment, the inner tube 200 is provided with two rows of nozzles 220. The difference from the above embodiment is that the two rows of nozzles 220 are arranged alternately at intervals.

[0041] like Figure 6As shown, in one embodiment, the inner tube 200 is provided with at least four rows of nozzles 220, each row of nozzles 220 facing a different direction, and the nozzles 220 in each row are staggered, with no two nozzles 220 on the same cross-section of the inner tube 200, forming a spiral-upward distribution of nozzles 220. In other embodiments, the nozzles 220 may face more directions.

[0042] According to one embodiment of the present invention, a flow rectifying component is provided at the liquid inlet of the inner tube 200. In this embodiment, in order to solve the problem of flow deviation caused by the bend in the pipeline before the distributor, the refrigerant is rectified before entering the distributor to keep the refrigerant entering the inner tube 200 as mixed as possible. Therefore, a flow rectifying component is provided at the liquid inlet of the inner tube 200.

[0043] like Figure 7 As shown, according to an embodiment of the present invention, a flow guiding component is provided at the liquid inlet of the inner tube 200. In this embodiment, a filter screen 500 is provided at the liquid inlet of the inner tube 200, that is, the refrigerant passes through the filter screen 500 before entering the inner tube 200 from the bend. The filter screen 500 is a common component in air conditioning circulation systems, and its function is to filter impurities in the pipeline, prevent impurities from clogging the electronic expansion valve, and prevent impurities from entering the compressor and damaging the compressor. In addition to filtering impurities, adding a filter screen 500 before the distributor also has a rectifying effect. When the refrigerant undergoes gas-liquid separation and passes through the filter screen 500, the liquid refrigerant is dispersed by the small holes on the filter screen and remixed with the gaseous refrigerant, thereby achieving a rectifying effect.

[0044] like Figure 8 As shown, according to an embodiment of the present invention, the flow guiding component is a flow guiding blade 600. In this embodiment, the flow guiding blade 600 is provided at the liquid inlet of the inner tube 200, that is, the refrigerant passes through the flow guiding blade 600 before entering the inner tube 200 from the bend. The flow guiding blade 600 has a series of inclined blades. When the refrigerant passes through, the flow direction of the refrigerant changes under the guiding action of the inclined blades, changing from the original straight flow to a rotating flow. During the rotation process, the gas and liquid two-phase refrigerant will mix, thereby disrupting the gas-liquid separation.

[0045] In other embodiments, the shape, number of blades, and tilt angle of the guide vane 600 may be different.

[0046] like Figure 9 , Figure 10 and Figure 11 As shown, according to an embodiment of the present invention, the inner tube 200 is provided with a one-way flow channel 230 communicating with the liquid distribution chamber 300. The one-way flow channel 230 is located below the nozzle 220 so that the refrigerant flows from the liquid distribution chamber 300 into the lumen of the inner tube 200. The outer tube 100 is provided with a plurality of branch tubes 400 communicating with the liquid distribution chamber 300.

[0047] In this embodiment, the inner tube 200 is provided with a one-way flow channel 230 and a nozzle 220 within the liquid distribution chamber 300. The lumen of the inner tube 200 is connected to the liquid distribution chamber 300 through the one-way flow channel 230, and the nozzle 220 is located above the one-way flow channel 230.

[0048] When the heat exchanger functions as an evaporator, the refrigerant enters the cavity of the inner tube 200 and can be ejected from the nozzle 220 into the distribution chamber 300, but it cannot enter the distribution chamber 300 from the inner tube 200 through the one-way flow channel 230. The refrigerant in the distribution chamber 300 can flow back into the cavity of the inner tube 200 through the one-way flow channel 230 and re-enter the distribution chamber 300 along with the refrigerant in the inner tube 200, thereby achieving the circulation of the refrigerant between the distribution chamber 300 and the inner tube 200.

[0049] When the air conditioning system reverses direction and the heat exchanger acts as a condenser, the liquid refrigerant flows back to the branch pipe body 400 through different flow paths of the heat exchanger. It then enters the liquid distribution chamber 300 between the inner pipe body 200 and the outer pipe body 100 through the branch pipe body 400. As the liquid refrigerant flows downward, it gradually converges in the liquid distribution chamber 300. It can first flow into the cavity of the inner pipe body 200 through the one-way flow channel 230 located below the nozzle 220, and then flow out of the distributor from the lower port of the inner pipe body 200.

[0050] The one-way flow channel 230 is a special flow channel structure that enables unidirectional flow, allowing refrigerant to flow from the liquid distribution chamber 300 into the inner tube body 200. Additionally, the one-way flow channel 230 facilitates smooth oil return, allowing compressor oil to be discharged promptly and preventing oil accumulation. Without this channel, compressor oil would accumulate in the liquid distribution chamber 300 between the inner tube body 200 and the outer tube body 100 and would not be able to drain.

[0051] According to one embodiment of the present invention, the unidirectional flow channel 230 is located at the bottom of the liquid distribution chamber 300. In this embodiment, the upper port of the inner tube 200 is inserted into the interior of the outer tube 100 from the lower port of the outer tube 100. The lower port of the outer tube 100 is closedly connected to the outer wall of the inner tube 200. The upper port of the inner tube 200 is located outside the outer tube 100, and the bottom of the liquid distribution chamber 300 is located at the lower end of the outer tube 100. The unidirectional flow channel 230 is positioned in the inner tube 200 at the lower end of the outer tube 100, i.e., at the bottom of the liquid distribution chamber 300.

[0052] The one-way flow channel 230 is located at the bottom of the liquid distribution chamber 300. After the liquid refrigerant enters the liquid distribution chamber 300 through the branch pipe 400, it ensures that the liquid refrigerant first accumulates at the bottom of the liquid distribution chamber 300 and then flows out of the inner pipe 200 in the shortest possible time after entering the liquid distribution chamber 300. Furthermore, because the one-way flow channel 230 is located at the bottom of the liquid distribution chamber 300, almost no refrigerant accumulates inside the liquid distribution chamber 300, minimizing the amount of refrigerant remaining in the distributor.

[0053] According to one embodiment of the present invention, the outer wall of the inner tube 200 is provided with a third protrusion 240, and a one-way flow channel 230 is provided inside the third protrusion 240. In this embodiment, the outer wall of the inner tube 200 is provided with a radially outward protrusion to form the third protrusion 240, and the one-way flow channel 230 is provided inside the third protrusion 240. The arrangement of the third protrusion 240 makes the bottom space of the liquid distribution chamber 300 the outer wall of the third protrusion 240 and the inner wall of the outer tube 100, thereby reducing the bottom space of the liquid distribution chamber 300 and further reducing the amount of refrigerant remaining in the distributor.

[0054] In this embodiment, the third protrusion 240 is a columnar structure, and the diameter d1 of the third protrusion 240 should be within a certain range: 1.1Din≤d1≤0.9Dout. Wherein, Din is the outer diameter of the inner tube 200, and Dout is the inner diameter of the outer tube 100.

[0055] In other embodiments, the one-way flow channel 230 can also be directly formed on the inner tube 200 without the need for the third protrusion 240. The third protrusion 240 can be integrally formed with the inner tube 200 or separately formed from the inner tube 200. The third protrusion 240 is sleeved on the inner tube 200, and the inner tube 200 is provided with corresponding holes that communicate with the one-way flow channel 230.

[0056] According to one embodiment of the present invention, the cross-sectional area of ​​the unidirectional flow channel 230 is greater than or equal to the cross-sectional area of ​​the nozzle 220. In this embodiment, by increasing the cross-sectional area of ​​the unidirectional flow channel 230, compared with the capillary tube of the prior art, the liquid refrigerant flows through a larger cross-sectional area of ​​the unidirectional flow channel 230 when flowing from the dispensing chamber 300 to the cavity of the inner tube 200, allowing it to flow in smoothly and effectively reducing the flow resistance of the refrigerant, thereby minimizing resistance during the switching between cooling and heating.

[0057] It is understood that the cross-sectional area of ​​the unidirectional flow channel 230 can be determined according to actual design needs, and the shape of the cross-section can also be set according to actual needs. In this embodiment, the opening of the unidirectional flow channel 230 on the outer wall of the third protrusion 240 is a strip with a certain length.

[0058] like Figure 4As shown, according to an embodiment of the present invention, the unidirectional flow channel 230 includes a main flow channel 231 and at least one resistance flow channel 232. Both ends of the resistance flow channel 232 are connected to the main flow channel 231. The main flow channel 231 gradually slopes upwards from the bottom towards the outer tube body 100 along the axial direction of the inner tube body 200. In this embodiment, the unidirectional flow channel 230 is composed of the main flow channel 231 and at least one resistance flow channel 232. The main flow channel 231 is a flow channel inclined at a certain angle, and the main flow channel 231 gradually moves away from the inner tube body 200 from the bottom towards the top along the axial direction of the inner tube body 200. The resistance flow channel 232 is curved, and both ends of the resistance flow channel 232 are connected to the main flow channel 231. Thus, the main flow channel 231 and the resistance flow channel 232 cooperate to form a flow channel with a Tesla valve structure, thereby achieving the effect of controlling the unidirectional flow of refrigerant at the unidirectional flow channel 230.

[0059] In this embodiment, the unidirectional flow channel 230 consists of a main flow channel 231 and a resistance flow channel 232, with the resistance flow channel 232 located above the main flow channel 231. In other embodiments, the unidirectional flow channel 230 may also consist of a main flow channel 231 and multiple resistance flow channels 232, with the multiple resistance flow channels 232 arranged sequentially on the main flow channel 231, and the multiple resistance flow channels 232 arranged alternately vertically on the main flow channel 231, forming multiple series of bends, which can also achieve the purpose of controlling the unidirectional flow of refrigerant.

[0060] In this embodiment, the lower end of the outer tube 100 is formed into a tapered slope, that is, the cross-sectional area of ​​the lower port of the outer tube 100 gradually decreases from top to bottom along the axial direction of the outer tube 100. Therefore, the cross-sectional area of ​​the bottom of the liquid distribution chamber 300 also gradually decreases. The third protrusion 240 is located at this tapered position, and the shape of the third protrusion 240 matches the shape of the liquid distribution chamber 300 at this location. That is, the third protrusion 240 also has a tapered portion that gradually tapes from top to bottom. The extension trend of the main flow channel 231 and the resistance flow channel 232 of the unidirectional flow channel 230 matches the shape of the protrusion.

[0061] According to one embodiment of the present invention, a plurality of unidirectional flow channels 230 are uniformly distributed axially around the inner tube 200 within the third protrusion 240. In this embodiment, there are multiple unidirectional flow channels 230, which are uniformly arranged circumferentially around the inner tube 200. That is, the openings of the unidirectional flow channels 230 on the third protrusion 240 face the bottom of the liquid distribution chamber 300 at various angles. On the one hand, this can further increase the inlet area of ​​the unidirectional flow channels 230 and reduce the refrigerant flow resistance; on the other hand, it can fully discharge the refrigerant at the bottom of the liquid distribution chamber 300 and reduce the accumulation of refrigerant at the bottom of the liquid distribution chamber 300.

[0062] According to one embodiment of the present invention, in addition to being configured as a Tesla valve structure, the one-way flow channel 230 can also be configured to have a one-way valve in the main flow channel 231. When the heat exchanger is an evaporator, the refrigerant cannot pass through the main flow channel 231, and when the heat exchanger is a condenser, the liquid refrigerant passes through the main flow channel 231, achieving the same effect as using a Tesla valve.

[0063] According to one embodiment of the present invention, the inner tube 200 is further provided with an exhaust port 210 communicating with the liquid distribution chamber 300, and the spray hole 220 is located between the exhaust port 210 and the one-way flow channel 230. In this embodiment, the inner tube 200 is also provided with an exhaust port 210, which can also communicate the interior of the inner tube 200 with the liquid distribution chamber 300. The inner tube 200 is provided with an exhaust port 210 and a spray hole 220 within the range of the liquid distribution chamber 300. The exhaust port 210 is located above the spray hole 220. The inner tube 200 is provided with the one-way flow channel 230, the spray hole 220 and the exhaust port 210 in sequence from bottom to top along its axial direction.

[0064] When the heat exchanger functions as an evaporator, the two-phase refrigerant enters the inner tube 200 from its lower port. The refrigerant in the inner tube 200 is then sprayed through the nozzle 220 into the distribution chamber 300 between the inner tube 200 and the outer tube 100, where it is evenly dispersed. It is then distributed to different flow paths within the heat exchanger via the branch tubes 400 for heat exchange. Due to gravity, some of the gaseous refrigerant in the inner tube 200 rises to the exhaust port 210 and can enter the distribution chamber 300 through it. As the gaseous refrigerant flows downwards after exiting the exhaust port 210, it also turbulently distributes the refrigerant within the distribution chamber 300, contributing to a more uniform refrigerant distribution.

[0065] The distributor of this invention, through the structural cooperation of the inner tube 200 and the outer tube 100, replaces the existing Venturi-type distributor, fundamentally changing the distributor structure and solving the problems caused by the existing Venturi-type distributor. It eliminates the need for capillary dispensing tubes and capillary length adjustments, offering advantages such as low cost, simple structure, small size, and easy adjustment. Furthermore, the vent 210 design of the inner tube 200 further improves the uniformity of refrigerant dispersion in the distributor.

[0066] According to one embodiment of the present invention, the vent 210 is located at the top of the liquid distribution chamber 300. In this embodiment, the upper port of the inner tube 200 is inserted into the outer tube 100 from the lower port of the outer tube 100. The upper end of the outer tube 100 is closedly connected to the upper port of the inner tube 200. The top of the liquid distribution chamber 300 is located at the upper end of the inner tube 200 and the outer tube 100. The vent 210 is provided at the upper end of the inner tube 200, corresponding to the top of the liquid distribution chamber 300.

[0067] The exhaust port 210 is located at the top of the main pipe. After the gas-liquid two-phase refrigerant enters the inner pipe 200 through the lower port of the inner pipe 200, it ensures that some of the gaseous refrigerant accumulates at the top of the liquid distribution chamber 300. At the same time, it can ensure the distribution range of the nozzle 220 on the inner pipe 200 and the spatial volume of the liquid distribution chamber 300, thereby maximizing the dispersion range of the refrigerant.

[0068] According to one embodiment of the present invention, a plurality of vent holes 210 are uniformly distributed around the axial direction of the inner tube 200. In this embodiment, there are multiple vent holes 210, which are uniformly arranged circumferentially at the upper end of the inner tube 200. That is, the vent holes 210 are arranged at various angles on the inner tube 200 facing the top of the liquid distribution chamber 300, which can further increase the coverage of the vent holes 210, reduce the exhaust resistance of some gaseous refrigerant, and fully turbulent the refrigerant within the circumferential range of the liquid distribution chamber 300, thereby improving the turbulence effect.

[0069] According to one embodiment of the present invention, the end of the branch pipe 400 is inserted into the liquid distribution chamber 300. In this embodiment, the outer pipe 100 has openings on its wall corresponding to the branch pipes 400 for inserting the branch pipes 400. Multiple branch pipes 400 are evenly distributed along the axial direction of the outer pipe 100, meaning that the branch pipes transport the refrigerant in each position of the liquid distribution chamber 300 to the heat exchanger. One end of the branch pipe 400 is inserted into the liquid distribution chamber 300 through the opening of the outer pipe 100, and there is a certain distance between it and the outer wall of the inner pipe 200. The design of the branch pipe 400 can reduce flow resistance, ensuring that the refrigerant gas-liquid two-phase flow can smoothly flow into the branch pipe 400 within the liquid distribution chamber 300.

[0070] The air conditioner provided by the present invention is described below. The air conditioner described below and the liquid separator described above can be referred to in correspondence.

[0071] This invention also provides an air conditioner, including a liquid distributor as described in the above embodiments.

[0072] In this embodiment of the air conditioner, the aforementioned distributor is provided. Within the air conditioning circulation system, the distributor distributes the gas-liquid two-phase refrigerant to various pipes of the evaporator for heat exchange. Using this distributor ensures uniform distribution, guaranteeing complete evaporation of refrigerant in high-flow-rate branches and preventing premature evaporation in low-flow-rate branches, thus avoiding wasted heat exchange area. Therefore, the uniform distribution of refrigerant in this embodiment directly affects the heat exchange capacity of the evaporator, improving air conditioning performance and preventing a decrease in heat exchanger capacity caused by uneven distribution.

[0073] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention 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; and these 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 the present invention.

Claims

1. A liquid dispenser, characterized in that, It includes an outer tube (100) and an inner tube (200). 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 distribution chamber (300). The inner tube (200) is provided with a spray hole (220) communicating with the liquid distribution chamber (300). The inner wall of the inner tube (200) is provided with a protruding turbulence part.

2. The dispenser according to claim 1, characterized in that, The turbulence section includes a first protrusion (250) that extends spirally along the axial direction of the inner tube (200).

3. The dispenser according to claim 2, characterized in that, The first protrusion (250) is a helical spring, or the first protrusion (250) is integrally formed with the inner tube body (200).

4. The dispenser according to claim 1, characterized in that, The turbulence section includes a second protrusion (260) that extends circumferentially along the inner tube (200) in an annular shape and is offset from the nozzle (220).

5. The dispenser according to claim 4, characterized in that, The cross-sectional area of ​​the inner wall of the second protrusion (260) gradually decreases along the refrigerant flow direction inside the inner tube (200).

6. The dispenser according to claim 4, characterized in that, The inner wall of the inner tube (200) is provided with a plurality of second protrusions (260) in sequence along its axial direction, and the interval between two adjacent second protrusions (206) is less than or equal to 15 times the inner diameter of the inner tube (200).

7. The dispenser according to any one of claims 1 to 6, characterized in that, The inner tube (200) is provided with at least two rows of nozzles (220). Each row of nozzles (220) is distributed sequentially along the axial direction of the inner tube (200). The orientation of each nozzle (220) on the inner tube (200) between two adjacent nozzles (220) in each row is different.

8. The dispenser according to claims 1 to 6, characterized in that, The inner tube (200) is equipped with a flow straightening component at the liquid inlet.

9. The dispenser according to claim 7, characterized in that, The rectifier includes at least one of a filter screen (500) and a guide vane (600).

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

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