Liquid separator, heat exchange device and heat pump unit

Abstract

The invention relates to the technical field of air conditioners, in particular to a liquid separator, a heat exchange device and a heat pump unit, the liquid separator comprises an outer pipe body, an inner pipe body and a branch pipe body, the outer pipe body is arranged on the outer side of the inner pipe body in a sleeving mode, the outer pipe body and the inner pipe body are connected to define a liquid separation cavity, and at least one partition plate is arranged in the outer pipe body; the liquid separation cavity is at least divided into two cavities through a partition plate in the flowing direction of refrigerants in the liquid separation cavity, the partition plate is provided with a flow guide channel, every two adjacent cavities are communicated through the flow guide channel, the branch pipe body is arranged on the outer pipe body, when the liquid separator is applied to a condensation state, the branch pipe body comprises first branch pipes and second branch pipes, each cavity is communicated with at least one first branch pipe, and each second branch pipe is communicated with at least one second branch pipe. The first branch pipe is suitable for inputting refrigerants into the cavities, except the cavity communicated with the outlet of the inner pipe body, the other cavities are all communicated with at least one second branch pipe, and the second branch pipes are suitable for outputting the refrigerants from the cavities. Gas-liquid separation in the condensation process is achieved, the purpose of improving the condensation effect of the heat exchanger is achieved, and the performance of the heat exchanger is exerted to the maximum.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pumps, and particularly to a liquid distributor, a heat exchange device and a heat pump unit. Background Art

[0002] The performance of a heat exchanger depends to a large extent on the design of its flow path. For heat pumps that need to handle both heating and cooling, the heat exchanger is not simply used as a condenser or an evaporator. This results in the problem that the flow path of the heat exchanger designed in the early stage is either biased towards refrigeration or towards heating, and it is impossible to achieve the optimal effect for both heating and cooling.

[0003] For the top - discharge air - cooled heat pump units currently on the market, there is a serious unevenness in the air flow field. This causes a low utilization rate of the heat exchange tubes at the lower part of the heat exchanger, resulting in serious waste. For the outdoor heat exchanger with top - discharge air, due to the uneven air flow field, when its condensation capacity requirement is met, there is still a large room for improvement in its evaporation capacity. Summary of the Invention

[0004] The present invention provides a liquid distributor, a heat exchange device and a heat pump unit to solve one of the defects in the prior art. By designing a partition with a diversion channel in the liquid distribution cavity and cooperating with the refrigerant flow direction in the liquid distribution cavity and the refrigerant inlet and outlet flow paths of the branch pipe group, gas - liquid separation during the condensation process is achieved, and the condensation heat is fully utilized to improve the condensation effect of the heat exchanger, so as to maximize the performance of the heat exchanger.

[0005] The present invention provides a liquid distributor, which includes an outer pipe body, an inner pipe body and a branch pipe body. The outer pipe body is sleeved outside the inner pipe body and connected to the inner pipe body to enclose a liquid distribution cavity. At least one partition is provided in the outer pipe body. The liquid distribution cavity is divided into at least two chambers by the partition along the refrigerant flow direction therein. The partition is provided with a diversion channel, and adjacent two chambers are communicated through the diversion channel. The branch pipe body is arranged on the outer pipe body. When the liquid distributor is applied in the condensation state, the branch pipe body includes a first branch pipe and a second branch pipe. Each chamber is communicated with at least one first branch pipe, and the first branch pipe is adapted to input refrigerant into the chamber. Except for the chamber communicated with the outlet of the inner pipe body, the remaining chambers are all communicated with at least one second branch pipe, and the second branch pipe is adapted to output refrigerant from the chamber.

[0006] According to the liquid distributor provided by the present invention, a plurality of partitions are provided in the outer pipe body, and the total cross - sectional area of the diversion channels on the plurality of partitions gradually increases along the refrigerant flow direction in the liquid distribution cavity.

[0007] According to the liquid distributor provided by the present invention, the number of branch pipe bodies corresponding to each chamber gradually decreases along the refrigerant flow direction in the liquid distribution cavity.

[0008] According to a liquid distributor provided by the present invention, the number of the second branch pipes corresponding to each of the chambers and communicating therewith gradually decreases along the flow direction of the refrigerant in the liquid distribution chamber.

[0009] According to a liquid distributor provided by the present invention, the number of the first branch pipes corresponding to each of the chambers and communicating therewith gradually decreases along the flow direction of the refrigerant in the liquid distribution chamber.

[0010] According to a liquid distributor provided by the present invention, the inner pipe body is provided with spray holes, and each of the chambers communicates with at least one of the spray holes.

[0011] According to a liquid distributor provided by the present invention, the liquid outlet direction of the spray holes is arranged opposite to the liquid inlet direction of the pipe orifices of the branch pipe body located in the liquid distribution chamber.

[0012] The present invention further provides a heat exchange device, including a heat exchanger, a main pipeline, and a liquid distribution pipe as described above. The heat exchanger includes a first heat exchange pipe and a second heat exchange pipe. The first heat exchange pipe is in one-to-one correspondence and communication with the first branch pipes, the second heat exchange pipe is in one-to-one correspondence and communication with the second branch pipes, and the main pipeline is in communication with both the first heat exchange pipe and the second heat exchange pipe.

[0013] According to a heat exchange device provided by the present invention, a one-way flow member is arranged in the main pipeline, and the one-way flow member is located between the communication positions of the first heat exchange pipe and the second heat exchange pipe corresponding to each of the chambers, so as to block the flow of the refrigerant in the main pipeline from the communication position of the first heat exchange pipe to the communication position of the second heat exchange pipe.

[0014] The present invention further provides a heat pump unit, including the heat exchange device as described above.

[0015] For the liquid distributor provided by the present invention, the outer pipe body and the inner pipe body jointly form a main pipe body. The outer pipe body is sleeved outside the inner pipe body. The upper pipe orifice and the lower pipe orifice of the outer pipe body are both hermetically connected to the outer wall of the inner pipe body. Thus, the space between the outer wall of the inner pipe body and the inner wall of the outer pipe body forms a liquid distribution chamber, that is, the outer pipe body encloses a liquid distribution chamber outside the inner pipe body. A plurality of branch pipe bodies are connected to the outer pipe body and communicate with the liquid distribution chamber. At least one partition is arranged in the liquid distribution chamber, and the liquid distribution chamber can be sequentially divided into a plurality of chambers along the direction from the upper pipe orifice to the lower pipe orifice of the outer pipe body. A diversion channel is arranged on the partition, and the diversion channel communicates the adjacent chambers. The branch pipe bodies communicated with each chamber form a branch pipe group corresponding to the chamber. The branch pipe bodies are divided into two types: first branch pipes and second branch pipes. The refrigerant mixed with gas and liquid enters the chamber through the first branch pipes, and the gaseous refrigerant in the chamber is discharged from the chamber through the second branch pipes. The branch pipe group communicated with the chamber at the lowermost end of the liquid distributor is only composed of first branch pipes, and the branch pipe groups communicated with the remaining chambers are all composed of both first branch pipes and second branch pipes.

[0016] When the heat exchanger is used as a condenser, the condensed refrigerant is partially liquefied to form a gas-liquid two-phase state. The gas-liquid mixed refrigerant enters the upper chamber through the first branch pipe. Part of the liquid refrigerant after condensation in this chamber enters the adjacent lower chamber through the flow guide holes of the partition due to gravity, and the gaseous refrigerant returns to the condenser through the second branch pipe for condensation heat exchange. Each chamber corresponds to a branch pipe group. The gas-liquid mixed refrigerant enters a chamber from the condenser, and the gaseous refrigerant in this chamber then returns to the condenser, which is one heat exchange process. In one heat exchange process, most of the liquid refrigerant in the chamber directly enters the chamber of the next heat exchange process, and the gaseous refrigerant is re-condensed to form a gas-liquid mixed refrigerant through this heat exchange process, and enters the chamber corresponding to this branch pipe group through the first branch pipe of the next heat exchange process, and so on until the last heat exchange process is reached. The refrigerant flowing out of the condenser all enters the chamber at the bottom end of the liquid distributor, and then is discharged from the outlet of the inner pipe body.

[0017] The liquid distributor of the present invention, through the structural cooperation of the inner pipe body, the outer pipe body and the branch pipe body, replaces the existing Venturi type liquid distributor, fundamentally changes the type of the liquid distributor structure, can solve the problems generated by the existing Venturi type liquid distributor, does not need to set up capillary liquid dividing pipes, and does not need to adjust the capillary length. Moreover, by designing a partition with a flow guide channel in the liquid distribution chamber, and cooperating with the flow direction of the refrigerant in the liquid distribution chamber and the refrigerant flow path of the inlet and outlet of the branch pipe group, the gas-liquid separation during the condensation process is realized, the condensation heat is fully utilized, and the purpose of improving the condensation effect of the heat exchanger is achieved, and the performance of the heat exchanger can be maximized. When applied to the top-out fan group, it can solve the problem of low utilization rate of the heat exchange pipes at the lower part of the heat exchanger caused by serious unevenness in the wind field, and avoid waste of cold energy. The liquid distributor of the present invention has a simple structure, is easy to install and debug, has a low cost, good liquid distribution effect, easy control of dimensions during the production and manufacturing process, and can be flexibly adjusted according to the actual situation of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0019] Figure 1 is one of the structural schematic diagrams of the liquid distributor provided by the embodiment of the present invention; Figure 2 is the structural schematic diagram of the partition of the liquid distributor provided by the embodiment of the present invention; Figure 3 is the second structural schematic diagram of the liquid distributor provided by the embodiment of the present invention; Figure 4 is a schematic structural diagram of a heat exchange device provided by an embodiment of the present invention; Figure 5 is the third schematic structural diagram of a liquid distributor provided by an embodiment of the present invention; Figure 6 is Figure 5 partial enlarged view A of Figure 7 is a schematic structural diagram of an inner tube body of a liquid distributor provided by an embodiment of the present invention; Figure 8 is the fourth schematic structural diagram of a liquid distributor provided by an embodiment of the present invention; Figure 9 is the fifth schematic structural diagram of a liquid distributor provided by an embodiment of the present invention; Figure 10 is the sixth schematic structural diagram of a liquid distributor provided by an embodiment of the present invention; Figure 11 is the seventh schematic structural diagram of a liquid distributor provided by an embodiment of the present invention.

[0020] Reference numerals: 100, outer tube body; 110, through hole; 200, inner tube body; 210, spray hole; 220, second positioning portion; 230, pipe section; 300, liquid separation cavity; 310, first chamber; 320, second chamber; 330, third chamber; 400, branch pipe body; 410, first positioning portion; 421, first branch pipe; 422, second branch pipe; 430, first branch pipe group; 440, second branch pipe group; 450, third branch pipe group; 500, partition; 510, diversion channel; 511, diversion hole; 520, first partition; 530; second partition; 600, heat exchanger; 610, heat exchange tube; 611, first heat exchange tube; 612, second heat exchange tube; 620, first heat exchange tube group; 630, second heat exchange tube group; 640, third heat exchange tube group; 700, main pipeline; 710, one-way flow component. Detailed implementation manners

[0021] To make the objectives, technical solutions and advantages of the present invention clearer, the technical solutions in the present invention will be clearly and completely described below with reference to the accompanying drawings in the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present invention without making creative efforts shall fall within the protection scope of the present invention.

[0022] As Figures 1 to 3As shown in the figure, a liquid distributor provided by an embodiment of the present invention includes an outer tube body 100, an inner tube body 200, and a branch tube body 400. The outer tube body 100 is sleeved outside the inner tube body 200 and is connected to the inner tube body 200 to enclose a liquid separation cavity 300. At least one partition 500 is provided in the outer tube body 100. The liquid separation cavity 300 is at least divided into two chambers along the flow direction of the refrigerant therein by the partition 500. The partition 500 is provided with a diversion channel 510, and adjacent two chambers are communicated through the diversion channel 510. The branch tube body 400 is arranged on the outer tube body 100. When the liquid distributor is applied in a condensation state, the branch tube body 400 includes a first branch tube 421 and a second branch tube 422. Each chamber is communicated with at least one first branch tube 421, and the first branch tube 421 is adapted to input refrigerant into the chamber. Except for the chamber communicated with the outlet of the inner tube body 200, the remaining chambers are all communicated with at least one second branch tube 422, and the second branch tube 422 is adapted to output refrigerant from the chamber.

[0023] In the liquid distributor of the embodiment of the present invention, the outer tube body 100 and the inner tube body 200 together form a main tube body. The outer tube body 100 is sleeved outside the inner tube body 200. The upper and lower tube openings of the outer tube body 100 are both hermetically connected to the outer wall of the inner tube body 200. Thus, the space between the outer wall of the inner tube body 200 and the inner wall of the outer tube body 100 forms the liquid separation cavity 300, that is, the outer tube body 100 encloses the liquid separation cavity 300 outside the inner tube body 200. A plurality of branch tube bodies 400 are connected to the outer tube body 100 and are communicated with the liquid separation cavity 300. At least one partition 500 is arranged in the liquid separation cavity 300, and the liquid separation cavity 300 can be sequentially divided into a plurality of chambers along the direction from the upper tube opening to the lower tube opening of the outer tube body 100. A diversion channel 510 is arranged on the partition 500, and the diversion channel 510 communicates the adjacent chambers. The branch tube bodies communicated with each chamber form a branch tube group corresponding to the chamber. The branch tube bodies are divided into two types: a first branch tube 421 and a second branch tube 422. The refrigerant mixed with gas and liquid enters the chamber through the first branch tube 421, and the gaseous refrigerant in the chamber is discharged from the chamber through the second branch tube 422. The branch tube group communicated with the chamber at the lowermost end of the liquid distributor is only composed of the first branch tube 421, and the branch tube groups communicated with the remaining chambers are all composed of the first branch tube 421 and the second branch tube 422.

[0024] When the heat exchanger 600 is used as a condenser, the condensed refrigerant is partially liquefied to form a gas-liquid two-phase state. The gas-liquid two-phase mixed refrigerant enters the upper chamber through the first branch pipe 421. Part of the liquid refrigerant after condensation in this chamber enters the adjacent lower chamber through the flow guiding through hole 510 of the partition plate 500 due to gravity, while the gaseous refrigerant returns to the condenser through the second branch pipe 422 for condensation heat exchange. Each chamber corresponds to a branch pipe group. The gas-liquid two-phase mixed refrigerant enters a chamber from the condenser, and the gaseous refrigerant in this chamber then returns to the condenser, which is one heat exchange process. In one heat exchange process, most of the liquid refrigerant in the chamber directly enters the chamber of the next heat exchange process, while the gaseous refrigerant forms a gas-liquid two-phase mixed refrigerant after being condensed again in this heat exchange process and enters the chamber corresponding to this branch pipe group through the first branch pipe 421 of the next heat exchange process, and so on until the last heat exchange process. The refrigerant flowing out of the condenser all enters the chamber at the bottommost part of the liquid distributor, and then is discharged from the outlet of the inner pipe body 200.

[0025] The liquid distributor of the present invention replaces the existing Venturi-type liquid distributor through the structural cooperation of the inner pipe body 200, the outer pipe body 100 and the branch pipe body 400, fundamentally changes the type of the liquid distributor structure, can solve the problems generated by the existing Venturi-type liquid distributor, does not need to set capillary liquid distribution pipes, and even less need to debug the length of the capillary tubes. Moreover, by designing a partition plate 500 with a flow guiding channel 510 in the liquid distribution chamber 300 and cooperating with the refrigerant flow direction in the liquid distribution chamber 300 and the refrigerant flow paths of the inlet and outlet of the branch pipe group, the gas-liquid separation during the condensation process is realized, the condensation heat is fully utilized, and the purpose of improving the condensation effect of the heat exchanger 600 is achieved, and the performance of the heat exchanger 600 can be maximized. When applied to the ejector fan group, it can solve the problem of low utilization rate of the heat exchange tubes 610 at the lower part of the heat exchanger 600 caused by serious unevenness in the wind field and avoid waste of cold energy. The liquid distributor of the present invention has a simple structure, is easy to install and debug, has a low cost, good liquid distribution effect, is easy to control the size during the production and manufacturing process, and can be flexibly adjusted according to the actual situation of the heat exchanger 600.

[0026] When the heat exchanger 600 is used as an evaporator, the gas-liquid two-phase mixed refrigerant enters the liquid distributor from the inlet of the inner pipe body 200, is evenly dispersed in the liquid distribution chamber 300, and enters the evaporator through the branch pipe body 400 corresponding to each chamber, and is vaporized to form gaseous refrigerant and discharged in the evaporator. Therefore, when the liquid distributor is applied to the evaporation state, there is no difference in the functions of the first branch pipe 421 and the second branch pipe 422 for all the branch pipe bodies, but all are suitable for outputting refrigerant from the chamber.

[0027] According to an embodiment provided by the present invention, a plurality of partition plates 500 are arranged inside the outer tube body 100, and the total cross-sectional area of the flow guiding channels 510 on the plurality of partition plates 500 gradually increases along the flow direction of the refrigerant in the liquid separation chamber 300. In this embodiment, a plurality of partition plates 500 are arranged in the liquid separation chamber 300, and the liquid separation chamber 300 is divided into at least three chambers from top to bottom. The refrigerant in the liquid separation chamber 300 flows from top to bottom. Therefore, the flow area of the flow guiding channels 510 on the partition plates 500 from top to bottom gradually increases.

[0028] To ensure that as much gaseous refrigerant as possible in each chamber can enter the second branch pipe 422 corresponding to this chamber and then enter the condenser for heat exchange and condensation again, the chamber must ensure the corresponding pressure to prevent the gaseous refrigerant from entering the chamber in the next heat exchange process through the flow guiding channel 510 of the partition plate 500. Since the content of gaseous refrigerant in the refrigerant mixture of gas-liquid two-phase decreases gradually as the heat exchange process proceeds, the chambers from top to bottom should also ensure that the internal pressure gradually decreases. Therefore, it is necessary to control the cross-sectional area of the flow guiding channel 510 of the partition plate 500 corresponding to each chamber according to the pressure change.

[0029] In this embodiment, a first partition plate 520 and a second partition plate 530 are sequentially arranged inside the outer tube body 100 from top to bottom. The liquid separation chamber 300 is sequentially divided into a first chamber 310, a second chamber 320, and a third chamber 330 from top to bottom, which respectively correspond to the first heat exchange process, the second heat exchange process, and the third heat exchange process. The content of gaseous refrigerant entering the first chamber 310 is the largest. The gas-liquid two-phase mixed refrigerant entering the second chamber 320 is formed by the condensation of the gaseous refrigerant in the first chamber 310 during the first heat exchange process, and the content of gaseous refrigerant is relatively low. The gas-liquid two-phase mixed refrigerant entering the third chamber 330 is formed by the condensation of the gaseous refrigerant in the second chamber 320 during the second heat exchange process, and the content of gaseous refrigerant is the lowest. Therefore, the first chamber 310 should ensure the maximum pressure, and the second chamber 320 and the third chamber 330 gradually decrease, so that the cross-sectional area of the flow guiding channel 510 of the first partition plate 520 is smaller than the cross-sectional area of the flow guiding channel 510 of the second partition plate 530.

[0030] It can be understood that in a group of branch pipes, the first branch pipe 421 is located above the second branch pipe 422, that is, the second branch pipe 422 is closer to the partition plate 500 than the first branch pipe 421. The gaseous refrigerant flows downward near the partition plate 500 following the liquid refrigerant under the influence of gravity. The liquid refrigerant enters the flow guiding channel 510 and flows to the next chamber, while the gaseous refrigerant enters the heat exchanger 600 again for condensation at the branch pipe body 400 closest to the partition plate 500.

[0031] According to an embodiment provided by the present invention, the number of branch pipe bodies 400 corresponding to each chamber and communicating therewith gradually decreases along the refrigerant flow direction in the liquid separation chamber 300. In this embodiment, since the gas-liquid two-phase mixed refrigerant entering the next heat exchange process is the refrigerant formed by the condensation heat exchange of the gaseous refrigerant in the previous heat exchange process, the amount of refrigerant in the next heat exchange process is less than that in the previous heat exchange process. Therefore, the number of branch pipes in each branch pipe group gradually decreases along the refrigerant heat exchange process.

[0032] In some embodiments, each branch pipe group may keep the number of the first branch pipes 421 consistent, and the number of the second branch pipes 422 gradually decreases. It is also possible to gradually decrease the number of the first branch pipes 421 and keep the number of the second branch pipes 422 consistent. It is also possible to gradually decrease the number of both the first branch pipes 421 and the second branch pipes 422.

[0033] According to an embodiment provided by the present invention, the number of the second branch pipes 422 corresponding to each chamber and communicating therewith gradually decreases along the refrigerant flow direction in the liquid separation chamber 300. In this embodiment, since the gas-liquid two-phase mixed refrigerant entering the next heat exchange process is the refrigerant formed by the condensation heat exchange of the gaseous refrigerant in the previous heat exchange process, the amount of refrigerant in the next heat exchange process is less than that in the previous heat exchange process. Moreover, in one heat exchange process, the amount of gaseous refrigerant re-entering the condenser is less than the amount of gas-liquid two-phase mixed refrigerant condensed in the condenser. Therefore, the number of the second branch pipes 422 in each branch pipe group can gradually decrease along the refrigerant heat exchange process.

[0034] According to an embodiment provided by the present invention, the number of the first branch pipes 421 corresponding to each chamber and communicating therewith gradually decreases along the refrigerant flow direction in the liquid separation chamber 300. In this embodiment, since the gas-liquid two-phase mixed refrigerant entering the next heat exchange process is the refrigerant formed by the condensation heat exchange of the gaseous refrigerant in the previous heat exchange process, the amount of refrigerant in the next heat exchange process is less than that in the previous heat exchange process. Moreover, in one heat exchange process, the amount of gas-liquid two-phase mixed refrigerant entering the condenser is less than the amount of gas-liquid two-phase mixed refrigerant in the previous heat exchange process. Therefore, the number of the first branch pipes 421 in each branch pipe group can gradually decrease along the refrigerant heat exchange process.

[0035] According to an embodiment provided by the present invention, the inner pipe body 200 is provided with spray holes 210, and each chamber communicates with at least one spray hole 210. In this embodiment, when the heat exchanger 600 is used as an evaporator, the gas-liquid two-phase refrigerant flows through the inside of the inner pipe body 200. The inner pipe body 200 is provided with spray holes 210 within the range of the liquid separation chamber 300. Thus, the refrigerant in the inner pipe body 200 will be sprayed into the liquid separation chamber 300 between the inner pipe body 200 and the outer pipe body 100 through the spray holes 210. After being reflected by the inner wall of the outer pipe body 100 and dispersed evenly in the liquid separation chamber 300, through impact mixing, uniform mixing of the two-phase refrigerant is achieved, and it is distributed to different flow paths of the heat exchanger 600 through each branch pipe body 400 for heat exchange, thereby achieving the purpose of uniform liquid separation.

[0036] In this embodiment, all the branch pipes of the branch pipe body 400 are used to convey the gas-liquid two-phase mixed refrigerant to the heat exchanger 600. There is no heat exchange process, and variable flow splitting is achieved. The number of flow paths and channels of the heat exchanger 600 during the evaporation and condensation processes is different. Instead of the venturi + capillary liquid splitting method in the prior art, the structures of the inner pipe body 200, the outer pipe body 100, the branch pipe body 400, and the partition plate 500 are used to achieve uniform liquid splitting of the two phases during the evaporation process. When the two-phase refrigerant enters the system for heat exchange, the heat exchange efficiency can be improved, and unnecessary overheating can be avoided. For the outdoor unit heat exchanger 600 with top air discharge, in the case of uneven air flow field, it can not only meet the requirements of condensation capacity, but also improve its evaporation capacity.

[0037] The problem that it is difficult to achieve uniform flow splitting of the two-phase refrigerant due to the differences in gravity and the back pressure at the outlets of each branch of the heat exchange is solved. The liquid splitting cavity 300 formed by the cooperation of the inner pipe body 200 and the outer pipe body 100, and the partition plate 500 with the flow guiding through holes 110 can cooperate to achieve the purpose of noise reduction and reduce the refrigerant flow noise caused by the flow of the two-phase refrigerant in the heat exchange and the inlet pipe group.

[0038] According to an embodiment provided by the present invention, the liquid outlet direction of the spray hole 210 is set opposite to the liquid inlet direction of the pipe orifice of the branch pipe body 400 located in the liquid splitting cavity 300. In this embodiment, a plurality of branch pipe bodies 400 are arranged in sequence along the axial direction of the outer pipe body 100 and concentrated on one side of the outer pipe body 100. A plurality of spray holes 210 are also arranged in sequence along the axial direction of the inner pipe body 200 and concentrated on one side of the inner pipe body 200. The side of the inner pipe body 200 where the spray holes 210 are located is opposite to the side of the inner pipe body 200 towards the pipe orifice of the branch pipe body 400, that is, the spraying direction of the refrigerant at the spray hole 210 is opposite to the flowing direction of the refrigerant flowing into the branch pipe body 400 from the pipe orifice of the branch pipe body 400.

[0039] The refrigerant is sprayed from the spray hole 210 into the space on one side of the liquid splitting cavity 300, and then the refrigerant in the liquid splitting cavity 300 enters the branch pipe body 400 from the space on the other side of the liquid splitting cavity 300, so as to increase the residence and mixing time of the refrigerant in the liquid splitting cavity 300, increase the length of the flow path of the refrigerant in the liquid splitting cavity 300, increase the number of reflections and paths of the refrigerant between the inner walls of the outer pipe body 100, and further improve the mixing and liquid splitting effects.

[0040] In this embodiment, the opposite directions include the cases where the axis of the spray hole 210 is parallel to or has an included angle with the axis of the branch pipe body 400.

[0041] The heat exchange device provided by the present invention will be described below. The heat exchange device described below can be mutually corresponded and referred to the liquid splitter described above.

[0042] As Figure 4As shown in the figure, the embodiment of the present invention further provides a heat exchange device, which includes a heat exchanger 600, a main pipeline 700, and a liquid distribution pipe as described in the above embodiment. The heat exchanger 600 includes a first heat exchange pipe 611 and a second heat exchange pipe 612. The first heat exchange pipe 611 is in one-to-one correspondence and communication with the first branch pipe 421, and the second heat exchange pipe 612 is in one-to-one correspondence and communication with the second branch pipe 422. The main pipeline 700 is in communication with both the first heat exchange pipe 611 and the second heat exchange pipe 612.

[0043] The heat exchange device of the embodiment of the present invention mainly consists of a liquid distributor, a heat exchanger 600, and a main pipeline 700. The branch pipe body 400 of the liquid distributor is in one-to-one correspondence and communication with one end of the heat exchange pipe 610 on the heat exchanger 600, and the other end of the heat exchange pipe 610 is in communication with the main pipeline 700. The heat exchange pipe 610 is also divided into multiple heat exchange pipe groups from top to bottom, that is, the first heat exchange pipe group 620, the second heat exchange pipe group 630, and the third heat exchange pipe group 640 corresponding to the first heat exchange process, the second heat exchange process, and the third heat exchange process respectively. The heat exchange pipe 610 is also divided into two types: the first heat exchange pipe 611 and the second heat exchange pipe 612. The first heat exchange pipe 611 is in communication with the first branch pipe 421, and the second heat exchange pipe 612 is in communication with the second branch pipe 422.

[0044] In this embodiment, when the heat exchanger 600 is used as a condenser, the gaseous refrigerant enters from the upper pipe orifice of the main pipeline 700, first passes through the first heat exchange pipe 611 of the first heat exchange pipe group 620, is condensed into a gas-liquid two-phase mixed refrigerant, and then enters the first chamber 310 through the first branch pipe 421 of the first branch pipe group 430. The liquid refrigerant in the first chamber 310 enters the second chamber 320 through the flow guiding through hole 510 of the first partition plate 500. The gaseous refrigerant in the first chamber 310 enters the second heat exchange pipe 612 of the first heat exchange pipe group 620 through the second branch pipe 422 of the first branch pipe group 430, is condensed into a gas-liquid two-phase mixed refrigerant, and then enters the main pipeline 700, and then enters the second chamber 320 through the first heat exchange pipe 611 of the second heat exchange pipe group 630. The liquid refrigerant in the second chamber 320 enters the third chamber 330 through the flow guiding through hole 510 of the second partition plate 500. The gaseous refrigerant in the second chamber 320 enters the second heat exchange pipe 612 of the second heat exchange pipe group 630 through the second branch pipe 422 of the second branch pipe group 440, is condensed into a gas-liquid two-phase mixed refrigerant, and then enters the main pipeline 700, and then enters the third chamber 330 through the first heat exchange pipe 611 of the third heat exchange pipe group 640. By analogy, the number of heat exchange pipe groups is not limited to three groups, and the heat exchange process of the refrigerant circulates according to the above logic.

[0045] When the heat exchanger 600 serves as an evaporator, the gas-liquid two-phase mixed refrigerant enters the distributor from the inlet of the inner pipe body 200, enters the liquid distribution cavity 300 through the spray holes and is evenly dispersed, and then enters the evaporator through the branch pipe bodies 400 corresponding to each cavity. In the evaporator, heat exchange is carried out through the heat exchange pipes 610, and the gasified gaseous refrigerant is discharged from the heat exchange pipes 610 to the main pipeline 700. Therefore, when the distributor is applied in the evaporation state, there is no longer a difference in the functions of the first heat exchange pipe 611 and the second heat exchange pipe 612 for all the heat exchange pipes 610.

[0046] According to an embodiment provided by the present invention, a one-way flow component 710 is provided in the main pipeline 700. The one-way flow component 710 is located between the communication positions of the first heat exchange pipe 611 and the second heat exchange pipe 612 of each branch pipe group, so as to unidirectionally block the flow of the refrigerant in the main pipeline 700 from the communication position of the first heat exchange pipe 611 to the communication position of the second heat exchange pipe 612 of each heat exchange pipe group.

[0047] In this embodiment, a one-way flow component 710, such as a one-way valve, etc., is provided in the main pipeline 700. The flow directions allowed by each one-way flow component 710 are the same, and the number of the one-way flow components 710 corresponds to the number of the partitions 500 in the distributor. At the position where each heat exchange pipe group is correspondingly connected to the main pipeline 700, a one-way flow component 710 is provided, and the main pipeline 700 between two adjacent one-way flow components 710 is the main pipeline 700 where the second heat exchange pipe 612 of the previous heat exchange pipe group is communicated with the first heat exchange pipe 611 of the next heat exchange pipe group.

[0048] The one-way flow component 710 blocks the flow path where the first heat exchange pipe 611 and the second heat exchange pipe 612 of a heat exchange pipe group are communicated in the main pipeline 700. That is, the gaseous refrigerant flowing into the main pipeline 700 is restricted by the one-way flow component 710 and can only enter the distributor through the first heat exchange pipe 611, and cannot enter the subsequent main pipeline 700 through the one-way flow component 710. Moreover, the gas-liquid two-phase mixed refrigerant entering the main pipeline 700 through the second heat exchange pipe 612 is restricted by the one-way flow component 710 to prevent it from flowing back to the first heat exchange pipe 611.

[0049] The heat pump unit provided by the present invention will be described below. The heat pump unit described below can be mutually referred to with the heat exchange device described above.

[0050] An embodiment of the present invention further provides a heat pump unit, including the heat exchange device as described in the above embodiment.

[0051] According to an embodiment provided by the present invention, the diversion channel 510 includes a plurality of diversion holes 511, and the plurality of diversion holes 511 are uniformly distributed along the axial direction perpendicular to the inner tube body 200. In this embodiment, the diversion channel 510 is composed of a plurality of diversion holes 511, and the areas of all the diversion holes 511 constitute the total area of the diversion channel 510. The plurality of diversion holes 511 are arranged on the partition plate 500 along the axial direction perpendicular to the inner tube body 200. Therefore, the number of the diversion holes 511 determines the distribution density at this position.

[0052] It can be understood that the shape of the diversion holes 511 of the diversion channel 510 is not limited to a rectangle, and can also be circular, diamond-shaped or other shapes. The distribution of all the diversion holes 511 on the partition plate 500 is not limited to a specific position, and can also be a globally uniform distribution. The diversion holes 511 do not necessarily need to be uniformly distributed, and the distribution of the diversion holes 510 can also be adjusted according to the distribution position of the liquid refrigerant on the partition plate 500.

[0053] As Figure 5 and Figure 6 shown, according to an embodiment provided by the present invention, the tube wall of the outer tube body 100 is provided with a through hole 110, and the branch tube body 400 is inserted into the through hole 110 and communicated with the liquid distribution cavity 300. The length of the part of the branch tube body 400 located between the outer wall of the outer tube and the outer wall of the inner tube body 200 is greater than or equal to the tube wall thickness of the outer tube body 100 and less than one-third of the set length, and the set length is the difference between the outer diameter of the outer tube body 100 and the outer diameter of the inner tube body 200.

[0054] In this embodiment, the tube wall of the outer tube body 100 is provided with a through hole 110 communicating with the liquid distribution cavity 300, and the end of the branch tube body 400 passes through the through hole 110 and is inserted into the liquid distribution cavity 300, that is, the tube orifice of the branch tube body 400 is located in the liquid distribution cavity 300, and the distance between the tube orifice and the orifice of the through hole 110 on the outer wall of the outer tube body 100 is the insertion depth of the branch tube body 400 in the outer tube body 100. The insertion depth of the branch tube body 400 will affect the liquid distribution effect. If the insertion is too deep, the tube orifice of the branch tube body 400 will be too close to the inner tube body 200, and the flow cross-sectional area formed by the liquid distribution cavity 300 between the inner tube body 200 and the branch tube body 400 will be reduced, thereby reducing the refrigerant entering the branch tube body 400. If the insertion is too shallow, the strength of the connection between the branch tube body 400 and the through hole 110 of the outer tube body 100 will be insufficient, and it is easy to break and cause refrigerant leakage. Therefore, the insertion depth of the branch tube body 400 is designed within a set range, that is, δ ≤ ds < (D1 - D2) / 3, where ds is the insertion depth of the branch tube, δ is the tube wall thickness of the outer tube body 100, D1 is the outer diameter of the outer tube body 100, and D2 is the outer diameter of the inner tube body 200.

[0055] The liquid distributor of the present invention replaces the existing Venturi liquid distributor through the structural cooperation of the inner tube body 200, the outer tube body 100 and the branch tube body 400, fundamentally changing the type of the liquid distributor structure, and can solve the problems generated by the existing Venturi liquid distributor. There is no need to set up capillary liquid dividing tubes, let alone debug the length of the capillary tubes. Moreover, the design of the insertion depth of the branch tube body 400 can further improve the liquid dividing effect and structural strength of the liquid distributor. The liquid distributor of the present invention has a simple structure, is easy to install and debug, has a low cost, a good liquid dividing effect, and is easy to control the size during the production and manufacturing process, and can be flexibly adjusted according to the actual situation of the heat exchanger and so on.

[0056] According to an embodiment provided by the present invention, a first positioning portion 410 is provided on the outer wall of the branch tube body 400, and the first positioning portion 410 abuts against the outer wall of the outer tube body 100. In this embodiment, during the manufacturing process of the branch tube body 400, since the insertion depth of the branch tube body 400 on the outer tube body 100 is determined first, the first positioning portion 410 is provided on the corresponding length of the outer wall of the branch tube body 400.

[0057] When assembling the branch tube body 400 and the outer tube body 100, insert the branch tube body 400 into the through hole 110 until the first positioning portion 410 contacts the outer wall around the through hole 110 of the outer tube body 100, and then stop inserting. The first positioning portion 410 can adopt a positioning protrusion, and when the branch tube body 400 reaches the insertion depth, it can block the process of the branch tube body 400 inserting into the through hole 110.

[0058] As Figure 7 and Figure 8 shown, according to an embodiment provided by the present invention, the inner tube body 200 is disposed inside the outer tube body 100 from bottom to top. A second positioning portion 220 is provided on the outer wall of the inner tube body 200, and the second positioning portion 220 abuts against the end face of the lower nozzle of the outer tube body 100. The distance between the second positioning portion 220 and the upper nozzle of the inner tube body 200 is greater than the length of the outer tube body 100.

[0059] In this embodiment, the inner tube body 200 penetrates from the lower nozzle of the outer tube body 100 to the upper nozzle of the outer tube body 100, and the upper nozzle of the inner tube body 200 extends out of the outer tube body 100. During the assembly process of the inner tube body 200 and the outer tube body 100, the upper nozzle of the inner tube body 200 first passes through the lower nozzle of the outer tube body 100 and enters the inside of the outer tube body 100, and then passes out through the upper nozzle of the outer tube body 100.

[0060] The position of the spray holes 210 on the inner tube body 200 is fixed, and the relative positions between the spray holes 210 of the inner tube body 200 and each branch tube body 400 play a decisive role in the liquid separation effect. In the actual assembly of the inner tube body 200 and the outer tube body 100, if the insertion depth cannot be accurately controlled, the relative positions between the spray holes 210 of the inner tube body 200 and the branch tube bodies 400 will change, resulting in the actual refrigerant amounts of the respective branch tube bodies 400 not conforming to the expectations. Therefore, in order to ensure that the relative positions between the spray holes 210 and the branch tube bodies 400 are consistent with the design values during manufacturing, a second positioning portion 220 needs to be provided on the outer wall of the inner tube body 200.

[0061] When the inner tube body 200 penetrates the outer tube body 100 from bottom to top, the insertion can be stopped when the second positioning portion 220 contacts the end face of the lower nozzle of the outer tube body 100. At this time, in order to ensure that the upper nozzle of the inner tube body 200 penetrates out of the upper nozzle of the outer tube body 100, the length of the inner tube body 200 above the second positioning portion 220 needs to be greater than the length of the outer tube body 100, that is, a > L, where L is the total length of the outer tube body 100 and a is the total length of the inner tube body 200 above the second positioning portion 220. Thus, when the inner tube body 200 reaches the position where the second positioning portion 220 is located, the outer tube body 100 can block the insertion process of the inner tube body 200. At this time, the positioning is completed, and the next welding work can be carried out.

[0062] In this embodiment, the second positioning portion 220 can adopt a positioning protrusion.

[0063] According to an embodiment provided by the present invention, the distance between the spray holes 210 and the second positioning portion 220 is between a first set distance and a second set distance. The first set distance is the length of the lower contraction tube section of the outer tube body 100, and the second set distance is the difference between the length of the outer tube body 100 and the length of the lower contraction tube section of the outer tube body 100.

[0064] In this embodiment, the arrangement of the spray holes 210 on the inner tube body 200 should satisfy that after the inner tube body 200 penetrates the outer tube body 100 and is positioned by the second positioning portion 220, all the spray holes 210 can be located within the space of the liquid separation cavity 300. Therefore, during the manufacturing process of the inner tube body 200, the position of the second positioning portion 220 can be determined first. After determining the position of the second positioning portion 220, based on the second positioning portion 220 as a reference, the position dimensions of the spray holes 210 on the inner tube body 200 can be determined according to the actual situation.

[0065] It is understandable that the outer diameter of the inner tube body 200 is much smaller than the inner diameter of the outer tube body 100. Therefore, to ensure that a closed liquid separation cavity 300 is formed between the outer tube body 100 and the inner tube body 200, the upper and lower nozzle openings of the outer tube body 100 are tightened to form an upper contraction pipe section and a lower contraction pipe section, and the inner walls of the upper contraction pipe section and the lower contraction pipe section are in a state of closely adhering to the outer wall of the inner tube body 200. The upper contraction pipe section and the lower contraction pipe section of the outer tube body 100 both have a certain length, and the lengths can be the same or different, which is determined according to the actual situation.

[0066] In this embodiment, after the position of the second positioning portion is determined, based on the second positioning portion, the distances between other spray holes 210 on the inner tube body 200 and the second positioning portion 220 are determined according to the actual situation, that is Figure 7 as shown in b~e in the figure, and the lengths of the upper contraction pipe section and the lower contraction pipe section of the outer tube body 100 are the same. Therefore, e > m, that is, the distance e from the lowermost spray hole 210 to the second positioning portion 220 should be greater than the length m of the lower contraction pipe section of the outer tube body 100; b < L - m, that is, the distance b from the uppermost spray hole 210 to the second positioning portion 220 should be less than the difference between the length L of the outer tube body 100 and the length m of the upper contraction pipe section of the outer tube body 100. The positioning dimensions of the remaining spray holes 210 should satisfy m < e < d < c < b < a ≤ 2L According to an embodiment provided by the present invention, a plurality of spray holes 210 are sequentially arranged along the axial direction of the inner tube body 200, and the distance between two adjacent spray holes 210 is between the aperture of the spray hole 210 and a third set distance. The third set distance is the difference between the length of the outer tube body 100 and the sum of the lengths of the upper contraction pipe section of the outer tube body 100, the lower contraction pipe section of the outer tube body 100, and the aperture of the spray hole 210.

[0067] In this embodiment, the setting range of the spray holes 210 needs to be limited within the height range of the liquid separation cavity 300, and the distance between adjacent spray holes 210 also plays a decisive role in the liquid separation effect. The distance between any two adjacent spray holes 210 l i should satisfy φ < l i < L - 2m - φ, where φ is the aperture of the spray hole 210.

[0068] In some cases, due to limited space inside the air conditioner and interference between refrigerant pipelines, etc., the refrigerant needs to enter the liquid distributor from top to bottom.

[0069] Such as Figure 11As shown, according to an embodiment provided by the present invention, the lower end of the outer tube body 100 is closed, and the inner tube body 200 is inserted into the outer tube body 100 from the upper opening of the outer tube body 100 from top to bottom. In this embodiment, the refrigerant enters the liquid distributor from the upper opening of the inner tube body 200, that is, it flows from top to bottom in the inner tube body 200. Since the density of the liquid refrigerant is much greater than that of the gas, the liquid refrigerant will accumulate at the bottom under the influence of gravity. To avoid this situation, the lower opening of the outer tube body 100 is closed, that is, the inner tube body 200 is inserted into the outer tube body 100 without penetrating the outer tube body 100, and the lower opening of the inner tube body 200 is located inside the outer tube body 100.

[0070] After the refrigerant enters the liquid separation chamber 300, since the inner tube body 200 does not penetrate the outer tube body 100, the flow rate of the refrigerant increases after entering. By further improving the bottom of the liquid distributor, the accumulation of liquid refrigerant at the bottom of the liquid separation chamber 300 can be reduced.

[0071] According to an embodiment provided by the present invention, the lower end of the inner tube body 200 is closed and abuts against the closed surface of the lower end of the outer tube body 100. In this embodiment, the lower port of the inner tube body 200 inside the outer tube body 100 is also in a closed state. And to ensure that the length of the inner tube body 200 inside the outer tube body 100 is sufficient and the refrigerant flow rate meets the requirements, the length of the inner tube body 200 inserted into the outer tube body 100 is controllable, which is convenient for the assembly operation of the inner tube body 200 and the outer tube body 100. The lower closed end of the inner tube body 200 is abutted against the lower closed end of the outer tube body 100, that is, the inner tube body 200 is inserted to the bottom of the outer tube body 100.

[0072] In other embodiments, a clamping corresponding structure can be provided at the bottom of the outer tube body 100 to ensure the closed connection between the inner tube body 200 and the outer tube body 100 and prevent the refrigerant from leaking from the interface between the end of the inner tube body 200 and the outer tube body 100; or the end of the inner tube body 200 can be closed first and then fixed in cooperation with the positioning structure at the bottom of the outer tube body 100.

[0073] According to an embodiment provided by the present invention, the outer diameter of the inner tube body 200 is greater than 4 mm, and the wall thickness of the outer tube body 100 is greater than 0.5 mm. In this embodiment, the outer diameter D2 of the inner tube body 200 should be greater than 4 mm, and the outer diameter D1 of the outer tube body 100 should satisfy D1 > D2 + 2δ, where the wall thickness δ of the outer tube body 100 should be greater than 0.5 mm to ensure the pressure resistance of the outer tube body 100.

[0074] As Figure 9As shown, according to an embodiment provided by 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 within 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 inner part of the outer tube 100 from bottom to top, and the refrigerant also flows through the inner tube 200 from bottom to top. After entering the inner part of the outer tube 100 from the lower nozzle 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 it.

[0075] During the process of the refrigerant flowing from the lower nozzle of the inner tube 200 to the upper nozzle of the inner tube 200, since the refrigerant will continuously decrease and be affected by gravity, the flow rate of the refrigerant will become smaller and smaller as it goes up. An overly small flow rate is not conducive to the smooth ejection of the refrigerant from the spray holes 210 and its smooth entry into the branch tube 400. Therefore, the inner diameter of the inner tube 200 needs to decrease along the flow direction of the refrigerant after entering the outer tube 100, so that the flow rate of the refrigerant in the inner tube 200 is not too low, that is, it is required that 0≤D21<D22, where D21 is the inner diameter of the inner tube 200 after entering the outer tube 100, and D22 is the inner diameter of the inner tube 200 before entering the outer tube 100 before the taper.

[0076] According to an embodiment provided by the present invention, the inner tube 200 penetrates from the lower nozzle of the outer tube 100 to the upper nozzle of the outer tube 100 and passes through the upper nozzle of the outer tube 100. In this embodiment, the upper nozzle of the inner tube 200 enters the inner part of the outer tube 100 from the lower nozzle of the outer tube 100, and then passes through the upper nozzle of the outer tube 100, penetrating the outer tube 100. Before entering the outer tube 100, the inner diameter of the inner tube 200 does not change. After entering the outer tube 100, the inner diameter of the inner tube 200 gradually decreases, and after passing through the outer tube 100, the inner diameter of the inner tube 200 remains the reduced inner diameter.

[0077] In other embodiments, the inner tube 200 can also be non-penetrating, that is, both the upper nozzle of the inner tube 200 and the upper nozzle of the outer tube 100 can be closed.

[0078] According to an embodiment provided by the present invention, the inner diameter of the upper nozzle of the inner tube 200 is greater than the aperture diameter of the spray holes 210. In this embodiment, to prevent the resistance caused by the structural change of the inner tube 200 from being too large when the refrigerant flows in the gradually tapering inner tube 200, which affects the liquid discharge from the spray holes 210 of the inner tube 200, and to ensure that the inner tube 200 can be normally manufactured to form the spray holes 210, the inner diameter of the upper nozzle of the inner tube 200 needs to be greater than the aperture diameter of the spray holes 210, that is, D21>D20, where D21 is the inner diameter of the upper nozzle of the inner tube 200, and D20 is the aperture diameter of the inner tube 200.

[0079] In some embodiments, only the aperture diameter of the nozzle 210 closest to the upper part may be defined. Since the nozzle 210 closest to the upper nozzle of the inner tube 200 is subject to the greatest resistance, the aperture diameter of the nozzle 210 closest to the upper nozzle of the inner tube 200 may be defined to be smaller than the inner diameter of the upper nozzle of the inner tube 200.

[0080] As Figure 10 shown, according to an embodiment provided by the present invention, the inner tube 200 located in the outer tube 100 includes a plurality of tube segments 230, and the inner diameters of the plurality of tube segments 230 decrease sequentially along the flow direction of the refrigerant in the inner tube 200. In this embodiment, in addition to the gradually changing structural form, the inner diameter of the inner tube 200 may also adopt a stepped change structural form after entering the outer tube 100. When changing in steps, the inner tube 200 located inside the outer tube 100 is axially divided into a plurality of tube segments 230, and the inner diameter of each tube segment 230 should decrease step by step from bottom to top. To prevent the resistance of the uppermost tube segment 230 from being too large and affecting the liquid discharge of the uppermost nozzle 210, and at the same time to ensure that the inner tube 200 can be normally opened, the inner diameter of the last-stage tube segment 230 should ensure that D21 > D20. Wherein, D21 is the inner diameter of the last tube segment 230, and D20 is the aperture diameter of the uppermost nozzle 210 of the inner tube 200.

[0081] According to an embodiment provided by the present invention, the number of tube segments 230 is less than or equal to the number of nozzles 210, and at least one nozzle 210 is provided on each tube segment 230. In this embodiment, when the pipe diameter of the inner tube 200 decreases step by step along the refrigerant flow direction, the diameter of each stage of the tube segment 230 along the refrigerant flow direction should decrease step by step. The number of steps N of the step change of the inner tube 200 is determined by the number n of nozzles 210. There should be at least one nozzle 210 on each tube segment 230, that is, 1 ≤ N ≤ n.

[0082] According to an embodiment provided by the present invention, the difference between the cross-sectional areas of two adjacent tube segments 230 is between the total area of the nozzles 210 on the tube segment 230 with a larger cross-sectional area and half of the cross-sectional area of the tube segment 230 with a larger cross-sectional area. In this embodiment, as two tube segments 230 during the stepwise reduction of the inner tube 200, one of them must have a larger cross-sectional area and the other has a smaller cross-sectional area. The larger cross-sectional area S i and the smaller cross-sectional area S i+1 should satisfy A ≤ S i - S i+1 ≤ 0.5S i , where A is the total area of the nozzles 210 on the tube segment 230 with a larger cross-sectional area.

[0083] The air conditioner provided by the present invention will be described below. The air conditioner described below can be mutually referred to the liquid distributor described above.

[0084] An embodiment of the present invention further provides an air conditioner, which includes a liquid distributor as described in the above embodiment.

[0085] For the air conditioner of the embodiment of the present invention, with the above-mentioned liquid distributor provided, in the air conditioner circulation system, the liquid distributor distributes the gas-liquid two-phase refrigerant into each pipeline of the evaporator for heat exchange. By using the liquid distributor of the embodiment of the present invention, it can ensure uniform liquid distribution, ensure that the refrigerant in the branch with a large flow rate is completely evaporated, and the refrigerant in the branch with a small flow rate will not be evaporated prematurely, thus avoiding the problem of waste of heat exchange area. Therefore, the uniform liquid distribution of the liquid distributor in the embodiment of the present invention can directly affect the heat exchange capacity of the evaporator, improve the performance of the air conditioner, and avoid the problem of the reduction of the heat exchanger capacity caused by uneven liquid distribution of the liquid distributor.

[0086] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements for some of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions 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 pipe body (100), an inner pipe body (200) and a branch pipe body (400). The outer pipe body (100) is sleeved outside the inner pipe body (200) and is connected to the inner pipe body (200) to enclose a liquid separation cavity (300). At least one partition (500) is provided in the outer pipe body (100). The liquid separation cavity (300) is at least divided into two chambers along the flow direction of the refrigerant therein by the partition (500). The partition (500) is provided with a diversion channel (510), and adjacent two chambers are communicated through the diversion channel (510). The branch pipe body (400) is arranged on the outer pipe body (100). When the liquid separator is applied in the condensation state, the branch pipe body includes a first branch pipe (421) and a second branch pipe (422). Each chamber is communicated with at least one of the first branch pipes (421). The first branch pipe (421) is adapted to input refrigerant into the chamber. Except for the chamber communicated with the outlet of the inner pipe body (200), the remaining chambers are all communicated with at least one of the second branch pipes (422). The second branch pipe (422) is adapted to output refrigerant from the chamber.

2. The dispenser according to claim 1, wherein, A plurality of the partitions (500) are provided in the outer pipe body (100), and the total cross-sectional area of the diversion channels (510) on the plurality of partitions (500) gradually increases along the flow direction of the refrigerant in the liquid separation cavity (300).

3. The dispenser according to claim 1, wherein, The number of the branch pipe bodies (400) corresponding to each chamber is gradually reduced along the flow direction of the refrigerant in the liquid separation cavity (300).

4. The dispenser according to claim 1, wherein The number of the second branch pipes (422) corresponding to each chamber is gradually reduced along the flow direction of the refrigerant in the liquid separation cavity (300).

5. The dispenser according to claim 1, characterized in that, The number of the first branch pipes (421) corresponding to each chamber is gradually reduced along the flow direction of the refrigerant in the liquid separation cavity (300).

6. The dispenser according to any one of claims 1 to 5, characterized in that The inner pipe body (200) is provided with spray holes (210), and each chamber is communicated with at least one of the spray holes (210).

7. The dispenser according to any one of claims 1 to 6, characterized in that, The liquid outlet direction of the spray holes (210) is arranged opposite to the liquid inlet direction of the pipe orifice of the branch pipe body (400) located in the liquid separation cavity (300).

8. A heat exchange device, characterized in that, It includes a heat exchanger (600), a main pipeline (700) and a liquid separation pipe as described in any one of claims 1 to 7. The heat exchanger (600) includes a first heat exchange pipe (611) and a second heat exchange pipe (612). The first heat exchange pipe (611) is in one-to-one correspondence and communication with the first branch pipe (421). The second heat exchange pipe (612) is in one-to-one correspondence and communication with the second branch pipe (422). The main pipeline (700) is communicated with both the first heat exchange pipe (611) and the second heat exchange pipe (612).

9. The heat exchange device according to claim 8, characterized in that A one-way flow member (710) is provided in the main pipeline (700). The one-way flow member (710) is located between the communication positions of the first heat exchange pipe (611) and the second heat exchange pipe (612) corresponding to each chamber to block the flow of the refrigerant in the main pipeline (700) from the communication position of the first heat exchange pipe (611) to the communication position of the second heat exchange pipe (612).

10. A heat pump unit, characterized in that, Comprising the heat exchange device as described in claim 8 or 9 above.

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