WO2020006992A1 - 布液器、降膜蒸发器以及空调 - Google Patents

布液器、降膜蒸发器以及空调 Download PDF

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Publication number
WO2020006992A1
WO2020006992A1 PCT/CN2018/121883 CN2018121883W WO2020006992A1 WO 2020006992 A1 WO2020006992 A1 WO 2020006992A1 CN 2018121883 W CN2018121883 W CN 2018121883W WO 2020006992 A1 WO2020006992 A1 WO 2020006992A1
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WO
WIPO (PCT)
Prior art keywords
liquid
tank
refrigerant
equalizing
air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2018/121883
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English (en)
French (fr)
Inventor
张治平
马严
胡东兵
胡海利
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Publication of WO2020006992A1 publication Critical patent/WO2020006992A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F25/00—Component parts of trickle coolers
    • F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid

Definitions

  • the present application relates to the technical field of heat exchange equipment, and in particular, to a liquid distributor, a falling film evaporator, and an air conditioner.
  • the refrigerant in the gas-liquid mixed state enters the liquid distributor in the falling film evaporator from the top.
  • the refrigerant is evenly distributed by the liquid distributor and drips onto the heat exchange tube to transfer the cooling capacity to user.
  • the liquid refrigerant After the liquid refrigerant is evaporated, it enters the suction port of the compressor, is compressed, and is discharged into the condenser.
  • the formation of a uniform and stable liquid film covering the surface of the heat exchange tube is a necessary condition to ensure the full heat exchange of the falling film evaporator.
  • the refrigerant in the gas-liquid mixed state in the traditional falling film evaporator is not easy to separate.
  • the liquid refrigerant cannot form a uniform and stable liquid film on the surface of the heat exchange tube under the interference of the gaseous refrigerant.
  • the gaseous refrigerant will accelerate the flow of the refrigerant through the surface of the heat exchange tube. Speed greatly reduces the heat transfer efficiency of the falling film evaporator.
  • a liquid distributor includes:
  • a liquid homogenizing tank the bottom wall of the liquid homogenizing tank is provided with a plurality of liquid distribution holes, and the top space of the liquid homogenizing tank is in communication with the exhaust channel of the falling film evaporator;
  • the liquid-blocking tank is disposed above the bottom wall of the liquid-blocking tank.
  • the liquid-blocking tank includes two opposite side walls.
  • the overflow hole communicates with the top space of the liquid-tight tank and the exhaust passage, and the liquid-tight tank can be filled with refrigerant.
  • the liquid distributor further includes a liquid homogenizing tube, the liquid homogenizing tube is disposed in the liquid retaining tank, and a plurality of liquid homogenizing through holes are provided on a wall of the liquid homogenizing tube,
  • the liquid homogenizing pipe can communicate with the refrigerant liquid inlet.
  • the liquid distributor further includes an air baffle, and the air baffle cover is provided on the top of the liquid equalizing tank, the liquid blocking tank, and the liquid equalizing tube;
  • the top ends of the liquid equalization tank and the liquid blocking tank are respectively opened, and the top ends of the liquid equalization tank and the liquid blocking tank are respectively spaced from the inner wall of the air baffle; the liquid blocking tank and the The gap between the air baffles, the gap between the liquid equalization tank and the air baffle, and the inner wall of the air baffle form part of an exhaust passage.
  • the liquid distributor further includes two end baffles, and the liquid leveling tank, the liquid blocking tank, the liquid leveling tube, and the air baffle have the same horizontal extension direction, The two ends of the liquid leveling tank, the liquid blocking tank, the liquid leveling tube, and the air blocking plate in the horizontal extending direction are respectively opened, and the two end baffles close the liquid leveling tank and Two ends of the liquid retaining groove, the liquid homogenizing pipe, and the air blocking plate in a horizontally extending direction.
  • both sides of the air baffle plate in a horizontally extending direction further have side plates, and the bottom end of the side plate is lower than the bottom end of the homogenizing tank.
  • the tops of the two side walls of the liquid retaining tank are higher than the center of the liquid homogenizing tube, and the liquid homogenizing through-hole is opened in the wall of the tube below the horizontal level of the liquid homogenizing tube center.
  • the inner diameter of the homogeneous through hole is greater than or equal to the inner diameter of the overflow through hole, and the inner diameter of the overflow through hole is greater than or equal to the inner diameter of the liquid distribution through hole.
  • the liquid distributor further includes a liquid inlet pipe, and two ends of the liquid inlet pipe communicate with the liquid homogenizing pipe and the refrigerant liquid inlet respectively.
  • a falling film evaporator includes a casing, a liquid distributor, and a tube heat exchanger.
  • the liquid distributor is the liquid distributor according to any one of the above schemes; and the liquid distributor is disposed in the casing.
  • the tube heat exchanger is disposed below the liquid distributor; there is an air flow gap between the air baffle and the casing.
  • both sides of the air baffle plate in the horizontal extension direction further have side plates, the bottom end of the side plate is lower than the bottom end of the homogenizing tank, and the bottom end of the side plate extends Between the second row of tubes at the bottom of the falling film zone in the tube heat exchanger and the fifth row of tubes at the bottom.
  • the falling film evaporator further includes an air outlet pipe, the air outlet pipe is disposed on the top of the housing, and one end of the air outlet pipe is in communication with the interior of the housing. The other end can communicate with the suction circuit of the air-conditioning equipment.
  • An air conditioner includes an evaporator and a condensing structure connected to each other.
  • the evaporator is a falling film evaporator according to the foregoing solution.
  • the liquid blocking grooves whose overflow flow holes are provided on two opposite side walls can buffer the gas-liquid mixed refrigerant injected into the liquid blocking groove.
  • the gas-liquid mixed refrigerant injected into the liquid retaining tank first accumulates at the bottom of the liquid retaining tank.
  • the gaseous refrigerant overflows in the form of bubbles during the injection and accumulation process, and the liquid refrigerant accumulates in the retaining wall.
  • the gaseous refrigerant contained in the liquid refrigerant is reduced, and the primary gas-liquid separation of the gas-liquid mixed refrigerant is realized.
  • the gaseous refrigerant that overflowed in a single gas-liquid separation overshoot entered the exhaust channel of the falling film evaporator from the headspace of the liquid retaining tank and was discharged.
  • the liquid refrigerant containing a small amount of gaseous refrigerant accumulates to the height of the overflow flow hole, the liquid refrigerant flows from the overflow flow hole on the side wall of the liquid blocking tank into the liquid homogenizing tank.
  • the liquid refrigerant was impacted during the flow from the side wall of the liquid retaining tank to the liquid homogenizing tank, and the gaseous refrigerant contained in the liquid refrigerant further overflowed, thereby achieving the secondary gas-liquid separation of the gas-liquid mixed refrigerant.
  • the gaseous refrigerant that overflowed during the secondary gas-liquid separation process was discharged from the head space of the homogenizing tank into the exhaust channel of the falling film evaporator.
  • the liquid blocking tank and the homogenizing tank cooperate to realize the primary gas-liquid separation and the secondary gas-liquid separation, which effectively reduces the inclusion amount of the gaseous refrigerant in the liquid refrigerant flowing from the bottom wall of the homogenizing tank, thereby ensuring the liquid refrigerant in heat exchange.
  • a uniform and stable liquid film is formed on the surface of the tube, and the influence of the gaseous refrigerant on the average speed of the liquid refrigerant flowing through the surface of the heat exchange tube is eliminated, thereby improving the heat exchange efficiency of the falling film evaporator.
  • the overflowing gaseous refrigerant enters the exhaust channel of the falling film evaporator, which reduces the amount of liquid refrigerant liquid beads carried during the discharge of the gaseous refrigerant, thereby reducing the impact of the suction liquid on the air conditioning heat exchange cycle system and ensuring the air conditioning. Normal operation of the system.
  • FIG. 1 is a schematic diagram of a three-dimensional structure of a liquid distributor provided by an embodiment of the present application
  • FIG. 2 is a schematic diagram of a three-dimensional structure of a homogenizing tank provided by an embodiment of the present application
  • FIG. 3 is a schematic diagram of a three-dimensional structure of a liquid retaining tank provided by an embodiment of the present application.
  • FIG. 4 is a schematic diagram of a three-dimensional structure of a homogenizing pipe provided by an embodiment of the present application.
  • FIG. 5 is an enlarged structural schematic view of the A-A section in FIG. 4; FIG.
  • FIG. 6 is a schematic diagram of a three-dimensional structure of a liquid distributor provided by another embodiment of the present application.
  • FIG. 7 is a schematic diagram of a three-dimensional structure of a falling film evaporator according to an embodiment of the present application.
  • FIG. 8 is a schematic structural view of a falling film evaporator according to an embodiment of the present application.
  • FIG. 9 is a schematic cross-sectional structure view taken along B-B in FIG. 8; FIG.
  • Fig. 10 is a schematic cross-sectional structure taken along the line D-D in Fig. 8.
  • Liquid distributors include spray type and drip type.
  • the spray type liquid distributor can ideally spray refrigerant liquid into liquid beads or even smaller droplets and cover the outer surface of the heat exchange tube.
  • the beads are connected and accumulated to form a continuous and uniform liquid film for heat exchange with the heat exchange tubes.
  • it is difficult to control the pressure and flow rate during the spraying process. It is impossible to determine whether the refrigerant is evenly arranged on the surface of the heat exchange tube. After the refrigerant evaporates and vaporizes, it is easy to carry small droplets of the refrigerant, which causes a serious problem of liquid suction. .
  • the drip-type liquid distributor relies on the gravity and viscosity of the refrigerant itself, and forms a column of refrigerant liquid on the heat exchange tube with a porous plate structure to form a uniform and thin liquid film for heat exchange with the heat exchange tube. Since the refrigerant enters the evaporator as a gas-liquid two-phase mixture, the gas flow velocity affects the average flow velocity of the two-phase refrigerant, and greatly affects the state of the internal liquid refrigerant, thereby affecting the liquid distribution effect.
  • the liquid distributor structure directly affects the refrigerant liquid distribution and film formation quality of the falling film evaporator, and the uniformity of the refrigerant liquid film directly affects the heat transfer efficiency. Therefore, optimizing the structure of the liquid distributor is an effective means to improve the performance of the falling film evaporator.
  • the separation of the refrigerant gas and liquid entering the liquid distributor has become the focus of most air-conditioning industries.
  • the present application provides a liquid distributor 200 including a liquid equalizing tank 210 and a liquid blocking tank 220.
  • the bottom wall of the homogenization tank 210 is provided with a plurality of liquid distribution holes 211, which means that the bottom wall of the homogenization tank 210 is a perforated plate.
  • the top space of the homogenizing tank 210 is in communication with the exhaust passage 500 of the falling film evaporator 10, and the exhaust passage 500 is shown by an arrow in FIG. 10.
  • the liquid blocking tank 220 is disposed in the liquid equalizing tank 210.
  • the bottom wall of the liquid blocking tank 220 is spaced from the bottom wall of the liquid equalizing tank 210.
  • the liquid blocking tank 220 includes two opposite side walls, and the opposite sides of the liquid blocking tank 220 are opposite.
  • the wall is respectively provided with a plurality of overflow flow holes 221, the top space of the liquid blocking tank 220 is in communication with the exhaust passage 500 of the falling film evaporator 10, and the refrigerant can be injected into the liquid blocking tank 220.
  • the liquid blocking grooves 220 provided on the two opposite side walls of the overflow flow holes 221 can buffer the gas-liquid mixed refrigerant injected into the liquid blocking grooves 220.
  • the gas-liquid mixed refrigerant injected into the liquid retaining tank 220 first accumulates at the bottom of the liquid retaining tank 220.
  • the gaseous refrigerant overflows in the form of bubbles during the injection and accumulation process, and the liquid refrigerant accumulates.
  • the liquid blocking tank 220 the gaseous refrigerant contained in the liquid refrigerant is reduced, and a primary gas-liquid separation of the gas-liquid mixed refrigerant is achieved.
  • the gaseous refrigerant that has overflowed in the primary gas-liquid separation overshoot enters the exhaust passage 500 of the falling film evaporator 10 from the head space of the liquid retaining tank 220 and is discharged.
  • the liquid refrigerant containing a small amount of gaseous refrigerant accumulates to the height of the overflow flow hole 221, the liquid refrigerant flows into the liquid equalization tank 210 from the overflow flow hole 221 on the side wall of the liquid blocking tank 220.
  • the liquid refrigerant is impacted during the flow from the side wall of the liquid blocking tank 220 to the liquid homogenizing tank 210, and the gaseous refrigerant contained in the liquid refrigerant further overflows, thereby realizing the secondary gas-liquid separation of the gas-liquid mixed refrigerant.
  • the gaseous refrigerant that has overflowed during the secondary gas-liquid separation process enters the exhaust passage 500 of the falling film evaporator 10 from the head space of the homogenizing tank 210 and is discharged.
  • the above-mentioned liquid blocking tank 220 cooperates with the homogenizing tank 210 to realize the primary gas-liquid separation and the secondary gas-liquid separation, which effectively reduces the inclusion amount of the gaseous refrigerant in the liquid refrigerant flowing from the bottom wall of the homogenizing tank 210, thereby ensuring the liquid refrigerant.
  • a uniform and stable liquid film is formed on the surface of the heat exchange tube 310, and the influence of the gaseous refrigerant on the average speed of the liquid refrigerant flowing through the surface of the heat exchange tube 310 is eliminated, and the heat exchange efficiency of the falling film evaporator 10 is improved.
  • the overflowing gaseous refrigerant enters the exhaust channel 500 of the falling film evaporator 10, which reduces the amount of liquid refrigerant liquid beads carried during the discharge of the gaseous refrigerant, thereby reducing the impact of the suction liquid on the air-conditioning heat exchange cycle system, ensuring that The normal operation of the air conditioning system.
  • the liquid distributor 200 further includes a liquid equalizing tube 230, which is disposed in the liquid retaining tank 220, and a wall of the liquid equalizing tube 230 is provided.
  • the plurality of equalizing through holes 231 and the equalizing pipe 230 can communicate with the refrigerant liquid inlet of the falling film evaporator 10.
  • the liquid homogenizing tube 230 can distribute the gas-liquid mixed refrigerant injected into the liquid homogenizing tube 230 along its own extension direction. After the gas-liquid mixed refrigerant enters the homogenizing pipe 230, the homogeneous through-hole 231 opened in the pipe wall of the homogenizing pipe 230 flows out into the liquid retaining tank 220.
  • the gas-liquid mixed refrigerant is impacted during the flow from the pipe wall of the liquid equalizing pipe 230 to the liquid retaining tank 220, and the gaseous refrigerant overflows.
  • This process is an implementation method of the gas-liquid mixed refrigerant once the gas-liquid separation.
  • the bottom of the liquid equalizing tube 230 and the bottom wall of the liquid blocking tank 220 are abutted or spaced from each other.
  • the space between the bottom of the liquid equalizing pipe 230 and the bottom wall of the liquid retaining tank 220 is set, which can increase the path length and impact degree of the gas-liquid mixed refrigerant flowing to the liquid retaining tank 220, so as to facilitate more Gaseous refrigerant overflowed.
  • the overflowing gaseous refrigerant enters the exhaust passage 500 of the falling film evaporator 10 from the head space of the liquid retaining tank 220 and is discharged.
  • the top end of the liquid blocking tank 220 is an opening, and the liquid equalizing tube 230 is a circular tube.
  • the tops of the two side walls of the liquid blocking tank 220 are higher than the center of the liquid equalizing pipe 230, and the liquid equalizing through hole 231 is opened in the tube wall of the part below the horizontal level of the liquid equalizing pipe 230.
  • the liquid refrigerant is The spraying direction of the liquid equalization through hole 231 of the liquid pipe 230 is only vertical downward spraying, oblique downward spraying, or horizontal spraying, which can effectively prevent the liquid refrigerant from splashing into the liquid retaining tank 220 when it flows out of the liquid equalizing pipe 230. Outside the area.
  • the included angle is less than or equal to 90 °.
  • seven rows of equalizing through holes 231 are provided along the circumferential direction of the cross section of the equalizing pipe 230, and each row of the equalizing through holes 231 are respectively arrayed along the extending direction of the equalizing pipe 230.
  • the angle between the line between the center of the topmost homogeneous through-hole 231 and the center of the cross section of the liquid equalizing tube 230 and the vertical line passing through the center of the cross section of the homogenized tube 230 is equal to 90 °, which means that the The center is located on the horizontal plane of the center of the homogenizing pipe 230.
  • the liquid distributor 200 further includes a liquid inlet pipe 260.
  • the two ends of the liquid inlet pipe 260 communicate with the liquid inlet pipe 230 and the refrigerant inlet of the falling film evaporator 10 respectively.
  • the liquid equalizing pipe 230 can communicate with the refrigerant liquid inlet of the falling film evaporator 10 through the liquid inlet pipe 260.
  • the liquid inlet pipe 260 and the liquid equalizing pipe 230 are a detachable fixed connection or a non-detachable fixed connection.
  • a liquid inlet through hole adapted to the liquid inlet tube 260 is opened at the top of the tube wall of the liquid homogenization tube 230, and one end of the liquid inlet tube 260 is inserted into the liquid inlet through hole at the top of the tube wall of the liquid homogenization tube 230.
  • the liquid inlet pipe 260 and the liquid homogenizing pipe 230 are connected and sealed by welding.
  • the top end of the pipe wall of the homogenizing tube 230 is provided with an internally threaded through hole adapted to the liquid inlet pipe 260, and one end of the liquid inlet pipe 260 having an external thread is screwed into the top of the pipe wall of the homogenizing tube 230.
  • the internally threaded through-hole, the liquid inlet pipe 260 and the liquid equalizing pipe 230 are connected in a threaded manner and sealed.
  • the liquid distributor 200 further includes an air baffle 240.
  • the bottom end of the air baffle 240 is an opening, and the air baffle 240 is disposed in the liquid equalizing tank 210, The top of the liquid blocking tank 220 and the liquid equalizing tube 230.
  • the top ends of the liquid equalizing tank 210 and the liquid blocking tank 220 are respectively opened, and the top ends of the liquid equalizing tank 210 and the liquid blocking tank 220 are respectively spaced from the inner wall of the air baffle 240.
  • the gap between the liquid blocking tank 220 and the air blocking plate 240, the gap between the liquid equalizing tank 210 and the gas blocking plate 240, and the inner wall of the gas blocking plate 240 form a part of the exhaust passage 500 in the falling film evaporator 10.
  • the air baffle 240 can guide the gaseous refrigerant overflowing during the primary gas-liquid separation and the secondary gas-liquid separation to flow and be discharged according to the exhaust passage 500.
  • the overflowing gaseous refrigerant enters the exhaust channel 500 of the falling film evaporator 10, which reduces the amount of liquid refrigerant liquid beads carried during the discharge of the gaseous refrigerant, thereby reducing the impact of the suction liquid on the air-conditioning heat exchange cycle system, ensuring that The normal operation of the air conditioning system.
  • the liquid leveling tank 210, the liquid blocking tank 220, the liquid leveling tube 230, and the air baffle 240 are supported and connected through a common support structure, or the above-mentioned relative positional relationships are respectively achieved through separate support structures.
  • the liquid distributor 200 further includes two end baffles 250, a liquid equalizing tank 210, a liquid blocking tank 220, a liquid equalizing tube 230, and an air baffle.
  • the end baffle 250 can play a role of fixed support and closing both ends of the liquid extending tank 210, the liquid blocking tank 220, and the liquid equalizing pipe 230 in the horizontal extending direction at the same time. Further, the end baffle 250 closes both ends of the liquid equalizing tank 210, the liquid blocking tank 220, the liquid equalizing tube 230, and the air blocking plate 240 in the horizontal extending direction in a full-welding manner.
  • the liquid equalizing tank 210 and the liquid blocking tank 220 are stamped structural parts.
  • the plate of the set size is bent to obtain the liquid equalizing tank 210 or the barrier that is open at both ends in the horizontally extending direction and has sidewalls on both sides. ⁇ 220 ⁇ Liquid tank 220.
  • the liquid distribution through holes 211 arranged in an array are punched out from the bottom wall of the liquid equalization tank 210, and the overflow flow holes 221 arranged in an array are punched out at both side walls of the liquid blocking tank 220.
  • a liquid inlet through hole at the top and a liquid through hole 231 in the lower portion are punched out to obtain the liquid through tube 230 in this embodiment.
  • the liquid inlet pipe 260 is an ordinary round pipe.
  • an external thread is machined at one end of the liquid inlet pipe 260 and an inner wall of the liquid inlet through hole is processed.
  • a suitable internal thread is sufficient.
  • both sides of the air blocking plate 240 along the horizontal extending direction further have a side plate 241, and the bottom end of the side plate 241 is lower than the bottom end of the homogenizing tank 210.
  • the bottom end of the side plate 241 extends between the second row of tubes at the bottom of the falling film zone to the fifth row of tubes at the bottom of the tube heat exchanger 300, where "the second row of tubes at the bottom of the falling zone to the fifth row of tubes at the bottom” refers to It is "the second row to the fifth row from the bottom of the falling film zone.”
  • the side plate 241 can increase the length of the exhaust passage 500 to a certain extent, which facilitates separation of the gaseous refrigerant carrying a small amount of liquid refrigerant liquid beads from the liquid refrigerant liquid beads, and further reduces the amount of liquid refrigerant liquid beads carried during the discharge of the gaseous refrigerant.
  • the inner diameter a of the liquid equalization through hole 231 is greater than or equal to the inner diameter b of the overflow through hole 221, and the inner diameter b of the overflow through hole 221 is greater than or equal to the inner diameter of the liquid distribution through hole 211.
  • c that is, a ⁇ b ⁇ c.
  • the diameters of the liquid distribution through holes 211, the overflow flow holes 221, and the liquid equalization through holes 231 are sequentially reduced.
  • the liquid refrigerant is distributed after being blocked and buffered multiple times to ensure that the liquid refrigerant flow rate drops smoothly.
  • the present application also provides a falling film evaporator 10, as shown in FIGS. 7-10.
  • the falling film evaporator 10 includes a casing 100, a liquid distributor 200, and a tube heat exchanger 300.
  • the liquid distributor 200 is any of the above schemes. Item one of the liquid distributor 200.
  • the liquid distributor 200 is disposed on the top end of the casing 100, and the tube heat exchanger 300 is disposed on the bottom of the liquid distributor 200.
  • the air gap between the air baffle 240 and the casing 100 forms a part of the exhaust passage 500 in the falling film evaporator 10.
  • the falling film evaporator 10 further includes an air outlet pipe 400 provided at the top of the casing 100.
  • One end of the air outlet pipe 400 is in communication with the interior of the casing 100, and the other end of the air outlet pipe 400 can be connected to the air-intake circuit of the air conditioner. Connected.
  • the gaseous refrigerant can enter the air outlet pipe 400 along the air gap between the air baffle 240 and the housing 100 and finally enter the air-intake circuit.
  • the gaseous refrigerant formed by evaporation of the liquid refrigerant in the falling film evaporator 10 and the tube heat exchanger 300 after heat exchange is also discharged along the exhaust passage 500.
  • the existence of the air baffle 240 increases the length of the gaseous refrigerant discharge path, effectively reduces the amount of liquid refrigerant liquid beads carried in the gaseous refrigerant, and further reduces the influence of the air-intake liquid on the air-conditioning heat exchange cycle system, ensuring the air-conditioning system. Normal operation.
  • the present application also provides an air conditioner, which includes an evaporator and a condensing structure that are interconnected, and the evaporator is the falling film evaporator 10 in the above solution.
  • the liquid distributor 200 is a drip-type liquid distributor.
  • the gas-liquid separation is performed first, and then the liquid refrigerant is used for liquid distribution to reduce the average flow rate of the refrigerant, and it is easier to form a liquid column flow form.
  • the flow or wave laminar flow contacts the outer wall surface of the heat exchange tube 310, and then spreads along the circle of the heat exchange tube 310 to spread the liquid evenly, reducing the area on the heat exchange tube 310 that is not covered by the liquid film.
  • the gaseous refrigerant and the liquid refrigerant are separated into different channels, which prevents the gaseous refrigerant from interfering with the distribution of the liquid refrigerant and ensures the integrity and continuity of the refrigerant liquid column.
  • the exhaust passage 500 communicates with the interior of the housing 100 and the interior of the liquid distributor 200.
  • the exhaust channel 500 can balance the internal pressure of the liquid distributor 200 and the internal pressure of the casing 100.
  • the liquid refrigerant only distributes liquid by its own gravity, and finally achieves a more uniform liquid distribution effect.
  • the liquid distributor 200 there are two types of gas-liquid mixed refrigerant flows.
  • the first case when the gas-liquid mixed refrigerant enters the liquid inlet pipe 260, the flow rate is low. After flowing to the liquid equalizing pipe 230, the liquid phase refrigerant is axially distributed and settles at the bottom of the liquid equalizing pipe 230 under the action of gravity.
  • the liquid equalizing pipe 230 The liquid homogeneous through hole 231 on the pipe wall is not completely covered by the liquid refrigerant; the gaseous refrigerant flows out of the liquid homogeneous through hole 231 that is not covered and rises, and the liquid refrigerant flows from the liquid homogeneous through hole 231 covered by the liquid refrigerant at the bottom of the liquid homogenizer 230 Outflow, gas-liquid mixed refrigerant realizes the first gas-liquid separation.
  • the second case when the gas-liquid mixed refrigerant enters the liquid inlet pipe 260, the flow velocity is high. After flowing to the liquid equalizing pipe 230, all the liquid equalizing through holes 231 are covered.
  • the pressure in the liquid equalizing pipe 230 increases, and the liquid refrigerant passes from the liquid homogeneous through The hole 231 is pressed out; the liquid refrigerant carries the gaseous refrigerant to the liquid retaining tank 220.
  • the liquid refrigerant inflow in the liquid retaining tank 220 is greater than the outflow.
  • the liquid refrigerant continues to accumulate until the inflow and outflow reach a balance. At this time, the accumulated liquid refrigerant is submerged.
  • the lower half of the liquid equalizing pipe 230 when the gas-liquid mixed refrigerant flows into the liquid retaining tank 220, the gaseous refrigerant overflows in the form of bubbling, the liquid refrigerant flows into the liquid equalizing tank 210, and the gaseous refrigerant rises in the form of bubbles. Secondary gas-liquid separation.
  • the overflow hole 221 on the side wall of the liquid blocking tank 220 By controlling the arrangement of the overflow hole 221 on the side wall of the liquid blocking tank 220, the above-mentioned two situations may exist at the same time.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种布液器（200）、降膜蒸发器（10）及空调。布液器（200）包括均液槽（210）和挡液槽（220）。均液槽（210）的底壁开设有多个布液通孔（211），均液槽（210）的顶部空间与降膜蒸发器（10）的排气通道（500）连通。挡液槽（220）设置于均液槽（210）的底壁上方，挡液槽（220）包括相对的两侧壁，挡液槽（220）上相对的两侧壁分别开设有多个溢流通孔（221），挡液槽（220）的顶部空间与降膜蒸发器（10）的排气通道（500）连通，挡液槽（220）内能够注入冷媒。气液混合冷媒在进入挡液槽（220）以及均液槽（210）的过程中能够分别进行一次气液分离以及二次气液分离，有效降低了从均液槽（210）底壁流出的液态冷媒中气态冷媒的夹杂量，进而保证了液态冷媒在换热管（310）表面形成均匀、稳定的液膜，提高了降膜蒸发器（10）的换热效率。

Description

布液器、降膜蒸发器以及空调
相关申请
本申请要求2018年07月02日申请的，申请号为201810708069.8，名称为“布液器、降膜蒸发器以及空调”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本申请涉及换热设备技术领域，特别是涉及一种布液器、降膜蒸发器以及空调。
背景技术
降膜蒸发器的工作过程中，气液混合状态的冷媒从顶部进入降膜蒸发器中的布液器，冷媒经布液器分配均流后滴淋到换热管上，将冷量传递给用户。液态冷媒自身被蒸发后，进入压缩机的吸气口，进行压缩后排入冷凝器。液态冷媒形成均匀、稳定的液膜覆盖在换热管表面是保证降膜蒸发器充分换热的必要条件。传统降膜蒸发器中气液混合状态的冷媒不易分离，液态冷媒在气态冷媒的干扰下无法在换热管表面形成均匀、稳定的液膜，同时气态冷媒会加快流经换热管表面冷媒的速度，极大降低了降膜蒸发器的换热效率。
发明内容
基于此，有必要针对传统降膜蒸发器中因气液混合状态的冷媒不易分离导致的换热效率低的问题，提供一种能够有效分离气液混合状态的冷媒进而提高换热效率的布液器、降膜蒸发器以及空调。
一种布液器，包括：
均液槽，所述均液槽的底壁开设有多个布液通孔，所述均液槽的顶部空间与降膜蒸发器的排气通道连通；
挡液槽，设置于所述均液槽的底壁上方，挡液槽均液槽所述挡液槽包括相对的两侧壁，所述挡液槽上相对的两侧壁分别开设有多个溢流通孔，所述挡液槽的顶部空间与排气通道连通，所述挡液槽内能够注入冷媒。
在其中一个实施例中，所述布液器还包括均液管，所述均液管设置于所述挡液槽内，所述均液管的管壁上开设有多个均液通孔，所述均液管能够与冷媒进液口连通。
在其中一个实施例中，所述布液器还包括挡气板，挡气板所述挡气板罩设于所述均液 槽、所述挡液槽以及所述均液管的顶部；所述均液槽以及所述挡液槽的顶端分别为开口，且所述均液槽的顶端以及所述挡液槽的顶端分别与所述挡气板的内壁间隔设置；所述挡液槽与所述挡气板之间的间隙、所述均液槽与所述挡气板之间的间隙以及所述挡气板的内壁形成排气通道的一部分。
在其中一个实施例中，所述布液器还包括两个端挡板，所述均液槽、所述挡液槽、所述均液管以及所述挡气板具有相同的水平延伸方向，所述均液槽、所述挡液槽、所述均液管以及所述挡气板沿水平延伸方向的两端分别为开口，两个所述端挡板分别封闭所述均液槽、所述挡液槽、所述均液管以及所述挡气板沿水平延伸方向的两端。
在其中一个实施例中，所述挡气板沿水平延伸方向的两侧还具有侧板，所述侧板的底端低于所述均液槽的底端。
在其中一个实施例中，挡液槽所述挡液槽两侧壁的顶端高于所述均液管的中心，所述均液通孔开设于所述均液管中心水平面以下部分的管壁。
在其中一个实施例中，均液通孔的内径大于等于所述溢流通孔的内径，所述溢流通孔的内径大于等于所述布液通孔的内径。
在其中一个实施例中，所述布液器还包括进液管，所述进液管的两端分别连通所述均液管和冷媒进液口。
一种降膜蒸发器，包括壳体、布液器以及管式换热器，所述布液器为上述方案任一项所述的布液器；所述布液器设置于所述壳体内的顶端，所述管式换热器设置于所述布液器的下方；所述挡气板与所述壳体之间具有气流间隙。
在其中一个实施例中，所述挡气板沿水平延伸方向的两侧还具有侧板，所述侧板的底端低于所述均液槽的底端，所述侧板的底端延伸至所述管式换热器中降膜区底部第二排管至底部第五排管之间。
在其中一个实施例中，所述降膜蒸发器还包括出气管，所述出气管设置于所述壳体的顶部，所述出气管的一端与所述壳体内部连通，所述出气管的另一端能够与空调设备的吸气回路连通。
一种空调，包括相互连通的蒸发器和冷凝结构，所述蒸发器为上述方案所述的降膜蒸发器。
上述布液器、降膜蒸发器以及空调，溢流通孔开设在相对两侧壁上的挡液槽能够对注入挡液槽内的气液混合冷媒起到缓冲作用。随着气液混合冷媒的不断注入，注入挡液槽内的气液混合冷媒首先积聚在挡液槽的底部，气态冷媒在注入以及积聚的过程中以气泡的形式溢出，液态冷媒则积存在挡液槽内，液态冷媒中夹杂的气态冷媒减少，实现了气液混合 冷媒的一次气液分离。在一次气液分离过冲中溢出的气态冷媒从挡液槽的顶部空间进入降膜蒸发器的排气通道排出。当夹杂少量气态冷媒的液态冷媒积存至溢流通孔的高度时，液态冷媒从挡液槽侧壁上的溢流通孔流入均液槽。液态冷媒由挡液槽的侧壁流至均液槽的过程中受到冲击，夹杂在液态冷媒中的气态冷媒进一步溢出，实现了气液混合冷媒的二次气液分离。在二次气液分离过程中溢出的气态冷媒从均液槽的顶部空间进入降膜蒸发器的排气通道排出。上述挡液槽与均液槽配合实现了一次气液分离以及二次气液分离，有效降低了从均液槽底壁流出的液态冷媒中气态冷媒的夹杂量，进而保证了液态冷媒在换热管表面形成均匀、稳定的液膜，并消除了气态冷媒对液态冷媒流经换热管表面时平均速度的影响，提高了降膜蒸发器的换热效率。溢出的气态冷媒进入降膜蒸发器的排气通道，减少了气态冷媒在排出过程中液态冷媒液珠的携带量，进而减小了吸气带液对空调换热循环系统的影响，保证了空调系统的正常运行。
附图说明
以下将参照附图对根据本申请的布液器、降膜蒸发器以及空调的优选实施方式进行描述。图中：
图1为本申请一实施例提供的布液器立体结构示意图；
图2为本申请一实施例提供的均液槽立体结构示意图；
图3为本申请一实施例提供的挡液槽立体结构示意图；
图4为本申请一实施例提供的均液管立体结构示意图；
图5为图4中A-A截面放大结构示意图；
图6为本申请另一实施例提供的布液器立体结构示意图；
图7为本申请一实施例提供的降膜蒸发器立体结构示意图；
图8为本申请一实施例提供的降膜蒸发器主视结构示意图；
图9为图8中B-B截面结构示意图；
图10为图8中D-D截面结构示意图。
其中：
10-降膜蒸发器
100-壳体
200-布液器
210-均液槽
211-布液通孔
220-挡液槽
221-溢流通孔
230-均液管
231-均液通孔
240-挡气板
241-侧板
250-端挡板
260-进液管
300-管式换热器
310-换热管
400-出气管
500-排气通道
a-均液通孔的内径
b-溢流通孔的内径
c-布液通孔的内径
具体实施方式
为了使本申请的目的、技术方案及优点更加清楚明白，以下通过实施例，并结合附图，对本申请的一种布液器、降膜蒸发器以及空调进行进一步详细说明。
需要说明的是，当元件被称为“固定于”另一个元件，它可以直接在另一个元件上或者也可以存在居中的元件。当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件或者可能同时存在居中元件。相反，当元件被称作“直接在”另一元件“上”时，不存在中间元件。本文所使用的术语“垂直的”、“水平的”、“左”、“右”以及类似的表述只是为了说明的目的。实施例附图中各种不同对象按便于列举说明的比例绘制，而非按实际组件的比例绘制。
随着空调行业的发展，满液式蒸发器结构优化已趋于稳定，各空调行业都逐渐将结构创新转向降膜式蒸发器。影响降膜式蒸发器换热效率的主要因素是冷媒流量、布液器结构、换热管管束布置、出气口吸气带液等，其中又以布液器的影响程度为最。
布液器包括喷淋式和滴淋式，喷淋式布液器在理想状态下能将冷媒液体喷洒成液珠甚至更小的液滴后覆盖在换热管外表面上，液滴和液珠进行联结积聚，形成连续且均匀的液膜与换热管进行换热交换。但实际上喷淋过程中压强和流速难以把控，无法确定是否将冷 媒均匀布置于换热管表面，且冷媒蒸发气化后容易携带体积小的冷媒液滴，造成严重的吸气带液问题。滴淋式布液器是靠冷媒自身重力作用与黏度性质，并以多孔板结构形成冷媒液柱滴落至换热管上，形成均匀且薄的液膜，与换热管进行换热交换。由于冷媒进入蒸发器时是气液两相混合物，气相流速影响两相冷媒的平均流速，极大程度上影响内部液态冷媒状态，从而影响布液效果。
布液器结构直接影响降膜蒸发器冷媒液体分布及成膜质量，而冷媒液膜均匀程度直接影响换热效率。因此，对布液器结构进行优化是提高降膜蒸发器性能的有效手段。对于滴淋式布液器来说，将进入布液器的冷媒气液分离成了大多空调行业关注的焦点。
如图1-3及图10所示，本申请提供一种布液器200，包括均液槽210和挡液槽220。均液槽210的底壁开设有多个布液通孔211，意即均液槽210的底壁为多孔板。均液槽210的顶部空间与降膜蒸发器10的排气通道500连通，排气通道500如图10中箭头所示。挡液槽220设置于均液槽210内，挡液槽220的底壁与均液槽210的底壁间隔设置，挡液槽220包括相对的两侧壁，挡液槽220上相对的两侧壁分别开设有多个溢流通孔221，挡液槽220的顶部空间与降膜蒸发器10的排气通道500连通，挡液槽220内能够注入冷媒。
上述布液器200，溢流通孔221开设在相对两侧壁上的挡液槽220能够对注入挡液槽220内的气液混合冷媒起到缓冲作用。随着气液混合冷媒的不断注入，注入挡液槽220内的气液混合冷媒首先积聚在挡液槽220的底部，气态冷媒在注入以及积聚的过程中以气泡的形式溢出，液态冷媒则积存在挡液槽220内，液态冷媒中夹杂的气态冷媒减少，实现了气液混合冷媒的一次气液分离。在一次气液分离过冲中溢出的气态冷媒从挡液槽220的顶部空间进入降膜蒸发器10的排气通道500排出。当夹杂少量气态冷媒的液态冷媒积存至溢流通孔221的高度时，液态冷媒从挡液槽220侧壁上的溢流通孔221流入均液槽210。液态冷媒由挡液槽220的侧壁流至均液槽210的过程中受到冲击，夹杂在液态冷媒中的气态冷媒进一步溢出，实现了气液混合冷媒的二次气液分离。在二次气液分离过程中溢出的气态冷媒从均液槽210的顶部空间进入降膜蒸发器10的排气通道500排出。
上述挡液槽220与均液槽210配合实现了一次气液分离以及二次气液分离，有效降低了从均液槽210底壁流出的液态冷媒中气态冷媒的夹杂量，进而保证了液态冷媒在换热管310表面形成均匀、稳定的液膜，并消除了气态冷媒对液态冷媒流经换热管310表面时平均速度的影响，提高了降膜蒸发器10的换热效率。溢出的气态冷媒进入降膜蒸发器10的排气通道500，减少了气态冷媒在排出过程中液态冷媒液珠的携带量，进而减小了吸气带液对空调换热循环系统的影响，保证了空调系统的正常运行。
如图1及图4所示，在本申请一实施例中，布液器200还包括均液管230，均液管230 设置于挡液槽220内，均液管230的管壁上开设有多个均液通孔231，均液管230能够与降膜蒸发器10的冷媒进液口连通。均液管230能够将注入均液管230的气液混合冷媒沿自身的延伸方向进行分配。气液混合冷媒进入均液管230内后，由均液管230的管壁上开设的均液通孔231流出至挡液槽220内。气液混合冷媒由均液管230的管壁流至挡液槽220的过程中受到冲击，气态冷媒溢出，此过程为气液混合冷媒一次气液分离的一种实现方式。可选的，均液管230的底部与挡液槽220的底壁之间抵接或者间隔设置。在本实施例中，均液管230的底部与挡液槽220的底壁之间间隔设置，能够增加气液混合冷媒流至挡液槽220过程的路径长度以及冲击程度，以便于更多的气态冷媒溢出。溢出的气态冷媒从挡液槽220的顶部空间进入降膜蒸发器10的排气通道500排出。
进一步，如图4及图5所示，挡液槽220的顶端为开口，均液管230为圆形管。挡液槽220的两侧壁的顶端高于均液管230的中心，均液通孔231开设于均液管230中心水平面以下部分的管壁，即使在较大的压力下，液态冷媒由均液管230的均液通孔231喷出方向也仅是垂直向下喷出、倾斜向下喷出或者水平喷出，能够有效防止液态冷媒从均液管230流出时喷溅至挡液槽220以外的区域。作为一种可实现的方式，在均液管230的截面内，最顶端均液通孔231的中心与均液管230截面中心的连线和穿过均液管230截面中心的垂直线之间的夹角小于等于90°。在本实施例中，如图5所示，沿均液管230截面的圆周方向开设有7列均液通孔231，每列均液通孔231分别沿均液管230的延伸方向阵列开设。最顶端均液通孔231的中心与均液管230截面中心的连线和穿过均液管230截面中心的垂直线之间的夹角等于90°，意即最顶端均液通孔231的中心位于均液管230中心水平面。
在本申请一实施例中，如图6-8所示，布液器200还包括进液管260，进液管260的两端分别连通均液管230和降膜蒸发器10的冷媒进液口，均液管230能够通过进液管260与降膜蒸发器10的冷媒进液口连通。可选的，进液管260与均液管230之间为可拆卸的固定连接或者不可拆卸的固定连接。作为一种可实现的方式，均液管230的管壁顶端开设有与进液管260适配的进液通孔，进液管260的一端插入均液管230管壁顶端的进液通孔，并且进液管260与均液管230之间以焊接的方式进行连接并实现密封。作为一种可实现的方式，均液管230的管壁顶端开设有与进液管260适配的内螺纹通孔，进液管260具有外螺纹的一端旋入均液管230管壁顶端的内螺纹通孔，进液管260与均液管230之间以螺纹连接的方式进行连接并实现密封。
在本申请一实施例中，如图6及图10所示，布液器200还包括挡气板240，挡气板240的底端为开口，挡气板240罩设于均液槽210、挡液槽220以及均液管230的顶部。均液槽210以及挡液槽220的顶端分别为开口，且均液槽210的顶端以及挡液槽220的顶 端分别与挡气板240的内壁间隔设置。挡液槽220与挡气板240之间的间隙、均液槽210与挡气板240之间的间隙以及挡气板240的内壁形成降膜蒸发器10中排气通道500的一部分。挡气板240能够引导一次气液分离以及二次气液分离过程中溢出的气态冷媒按照排气通道500流动并排出。溢出的气态冷媒进入降膜蒸发器10的排气通道500，减少了气态冷媒在排出过程中液态冷媒液珠的携带量，进而减小了吸气带液对空调换热循环系统的影响，保证了空调系统的正常运行。
可选的，均液槽210、挡液槽220、均液管230以及挡气板240之间通过共同的支撑结构进行支撑连接，或者通过单独的支撑结构分别实现上述相对位置关系。在本申请一实施例中，如图1、图9及图10中，布液器200还包括两个端挡板250，均液槽210、挡液槽220、均液管230以及挡气板240具有相同的水平延伸方向，均液槽210、挡液槽220、均液管230以及挡气板240沿水平延伸方向的两端分别为开口，两个遮挡板分别封闭均液槽210、挡液槽220、均液管230以及挡气板240沿水平延伸方向的两端。端挡板250能够同时起到固定支撑以及封闭均液槽210、挡液槽220、均液管230水平延伸方向两端的作用。进一步，端挡板250以满焊焊接的方式封闭均液槽210、挡液槽220、均液管230以及挡气板240沿水平延伸方向的两端。
在上述实施例中，均液槽210、挡液槽220均为冲压结构件，设定尺寸的板材通过弯折得到沿水平延伸方向两端开口、两侧具有侧壁的均液槽210或挡液槽220。在均液槽210的底壁冲压出阵列排布的布液通孔211，在挡液槽220的两侧壁冲压出阵列排布的溢流通孔221。在原始管材的基础上冲压出顶端的进液通孔以及位于下部的均液通孔231以得到本实施例中的均液管230。进液管260为普通的圆管，当进液管260与均液管230通过螺纹连接的方式连接并密封时，在进液管260的一端加工出外螺纹并在进液通孔的内壁加工出适配的内螺纹即可。
在本申请一实施例中，如图6及图10所示，挡气板240沿水平延伸方向的两侧还具有侧板241，侧板241的底端低于均液槽210的底端，侧板241的底端延伸至管式换热器300中降膜区底部第二排管至底部第五排管之间，其中“降膜区底部第二排管至底部第五排管”指的是“从降膜区最下排管往上开始数的第二排管至第五排管”。侧板241能够在一定程度上增加排气通道500的长度，便于携带有少量液态冷媒液珠的气态冷媒与液态冷媒液珠分离，进一步减少气态冷媒在排出过程中液态冷媒液珠的携带量。
在本申请一实施例中，如图3-5所示，均液通孔231的内径a大于等于溢流通孔221的内径b，溢流通孔221的内径b大于等于布液通孔211的内径c,即a≥b≥c。布液通孔211、溢流通孔221、均液通孔231的孔径依次减小，液态冷媒在经过多次阻挡与缓冲后进 行布液，以保证液体冷媒流速平稳下降。
本申请还提供一种降膜蒸发器10，如图7-10所示，降膜蒸发器10包括壳体100、布液器200以及管式换热器300，布液器200为上述方案任一项所述的布液器200。布液器200设置于壳体100内的顶端，管式换热器300设置于布液器200的底部。挡气板240与壳体100之间具有气流间隙。挡气板240与壳体100之间的气流间隙形成降膜蒸发器10中排气通道500的一部分。气液分离后溢出的气态冷媒沿挡气板240的内壁向下运动至侧板241的底端，然后沿挡气板240的外壁与壳体100之间的气流间隙排出。进一步，降膜蒸发器10还包括出气管400，出气管400设置于壳体100的顶部，出气管400的一端与壳体100内部连通，出气管400的另一端能够与空调设备的吸气回路连通。气态冷媒能够沿挡气板240与壳体100之间具有气流间隙进入出气管400中并最终进入空调设备的吸气回路。降膜蒸发器10中液体冷媒与管式换热器300换热后蒸发形成的气态冷媒也沿排气通道500排出。挡气板240的存在增加了气态冷媒排出路径的长度，有效降低了气态冷媒中液态冷媒液珠的携带量，进而减小了吸气带液对空调换热循环系统的影响，保证了空调系统的正常运行。
本申请还提供一种空调，包括相互连通的蒸发器和冷凝结构，蒸发器为上述方案中的降膜蒸发器10。
上述布液器200为滴淋式布液器，在气液混合冷媒进入时先进行气液分离，再以液态冷媒进行布液，减小冷媒平均流速，更容易形成液柱流动形式，以层流或波动层流的方式与换热管310外壁面进行接触，再沿换热管310环向延展铺开，布液均匀，减少换热管310上未被液膜覆盖的区域。气态冷媒与液态冷媒分走不同通道，避免了气态冷媒对液态冷媒布液时进行干扰，保证了冷媒液柱完整程度与连续性，同时排气通道500连通壳体100内部和布液器200内部，排气通道500能够平衡布液器200内压与壳体100内压，液体冷媒仅靠自身重力作用进行布液，最终达到布液更加均匀的效果。
在上述布液器200内，气液混合冷媒流动情况包括两种。第一种情况：气液混合冷媒进入进液管260时流速较低，流动至均液管230后液相冷媒进行轴向分布并在重力作用下沉降在均液管230底部，均液管230管壁上的均液通孔231并未完全被液态冷媒覆盖；气态冷媒从未被覆盖的均液通孔231流出并上升，液态冷媒从均液管230底部液态冷媒覆盖的均液通孔231流出，气液混合冷媒实现第一次气液分离。第二种情况：气液混合冷媒进入进液管260时流速较高，流动至均液管230后将所有均液通孔231覆盖，均液管230内压力增加，将液态冷媒从均液通孔231压出；液态冷媒携带气态冷媒流动至挡液槽220，挡液槽220内液态冷媒流入量大于流出量，液态冷媒持续积聚直到流入量与流出量达到平 衡，此时积聚的液态冷媒淹没均液管230下半部；气液混合冷媒流入挡液槽220时，气态冷媒以冒泡的形式溢出，液态冷媒流入均液槽210中，气态冷媒以气泡形式上升，气液混合冷媒实现第二次气液分离。在实际工况中，通过控制挡液槽220侧壁上溢流通孔221的排布，上述两种情况可同时存在。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对发明专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。

Claims (12)

  1. 一种布液器，其特征在于，包括：
    均液槽(210)，所述均液槽(210)的底壁开设有多个布液通孔(211)，所述均液槽(210)的顶部空间与排气通道(500)连通；
    挡液槽(220)，设置于所述均液槽(210)的底壁上方，挡液槽均液槽所述挡液槽(220)包括相对的两侧壁，所述挡液槽(220)上相对的两侧壁分别开设有多个溢流通孔(221)，所述挡液槽(220)的顶部空间与排气通道(500)连通，所述挡液槽(220)内能够注入冷媒。
  2. 根据权利要求1所述的布液器，其特征在于，所述布液器(200)还包括均液管(230)，所述均液管(230)设置于所述挡液槽(220)内，所述均液管(230)的管壁上开设有多个均液通孔(231)，所述均液管(230)能够与冷媒进液口连通。
  3. 根据权利要求2所述的布液器，其特征在于，所述布液器(200)还包括挡气板(240)，挡气板所述挡气板(240)罩设于所述均液槽(210)、所述挡液槽(220)以及所述均液管(230)的顶部；所述均液槽(210)以及所述挡液槽(220)的顶端分别为开口，且所述均液槽(210)的顶端以及所述挡液槽(220)的顶端分别与所述挡气板(240)的内壁间隔设置；所述挡液槽(220)与所述挡气板(240)之间的间隙、所述均液槽(210)与所述挡气板(240)之间的间隙以及所述挡气板(240)的内壁形成排气通道(500)的一部分。
  4. 根据权利要求3所述的布液器，其特征在于，所述布液器(200)还包括两个端挡板(250)，所述均液槽(210)、所述挡液槽(220)、所述均液管(230)以及所述挡气板(240)具有相同的水平延伸方向，所述均液槽(210)、所述挡液槽(220)、所述均液管(230)以及所述挡气板(240)沿水平延伸方向的两端分别为开口，两个所述端挡板分别封闭所述均液槽(210)、所述挡液槽(220)、所述均液管(230)以及所述挡气板(240)沿水平延伸方向的两端。
  5. 根据权利要求3所述的布液器，其特征在于，所述挡气板(240)沿水平延伸方向的两侧还具有侧板(241)，所述侧板(241)的底端低于所述均液槽(210)的底端。
  6. 根据权利要求2-5任一项所述的布液器，其特征在于，挡液槽所述挡液槽(220)两侧壁的顶端高于所述均液管(230)的中心，所述均液通孔(231)开设于所述均液管(230)中心水平面以下部分的管壁。
  7. 根据权利要求2-5任一项所述的布液器，其特征在于，均液通孔(231)的内径大于等于所述溢流通孔(221)的内径，所述溢流通孔(221)的内径大于等于所述布液通孔(211)的内径。
  8. 根据权利要求2-5任一项所述的布液器，其特征在于，所述布液器(200)还包括进液管(260)，所述进液管(260)的两端分别连通所述均液管(230)和冷媒进液口。
  9. 一种降膜蒸发器，其特征在于，包括壳体(100)、布液器(200)以及管式换热器(300)，所述布液器(200)为权利要求3-5任一项所述的布液器(200)；所述布液器(200)设置于所述壳体(100)内的顶端，所述管式换热器(300)设置于所述布液器(200)的下方；所述挡气板(240)与所述壳体(100)之间具有气流间隙。
  10. 根据权利要求9所述的降膜蒸发器，其特征在于，所述挡气板(240)沿水平延伸方向的两侧还具有侧板(241)，所述侧板(241)的底端低于所述均液槽(210)的底端，所述侧板(241)的底端延伸至所述管式换热器(300)中降膜区底部第二排管至底部第五排管之间。
  11. 根据权利要求9所述的降膜蒸发器，其特征在于，所述降膜蒸发器(10)还包括出气管(400)，所述出气管(400)设置于所述壳体(100)的顶部，所述出气管(400)的一端与所述壳体(100)内部连通，所述出气管(400)的另一端能够与空调设备的吸气回路连通。
  12. 一种空调，其特征在于，包括相互连通的蒸发器和冷凝结构，所述蒸发器为权利要求9-11任一项所述的降膜蒸发器(10)。
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