WO2006060953A1 - Climatiseur a pompe a chaleur - Google Patents

Climatiseur a pompe a chaleur Download PDF

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Publication number
WO2006060953A1
WO2006060953A1 PCT/CN2005/002092 CN2005002092W WO2006060953A1 WO 2006060953 A1 WO2006060953 A1 WO 2006060953A1 CN 2005002092 W CN2005002092 W CN 2005002092W WO 2006060953 A1 WO2006060953 A1 WO 2006060953A1
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WO
WIPO (PCT)
Prior art keywords
pipe
heat
water
tube
heat pipe
Prior art date
Application number
PCT/CN2005/002092
Other languages
English (en)
Chinese (zh)
Inventor
Xiamin Tong
Aming Ji
Original Assignee
J Systems Research Corp.
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 J Systems Research Corp. filed Critical J Systems Research Corp.
Publication of WO2006060953A1 publication Critical patent/WO2006060953A1/fr

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Classifications

    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to an air conditioning system, and more particularly to a low pressure differential circulating heat pump air conditioning unit comprising a novel evaporator, condenser and compressor.
  • the corrugated inner fins and flat tubes in the outdoor side heat exchanger J 2 described in the Chinese patent No. ZL96116305. 4 and U.S. Patent No. 5,775,114 are susceptible to pressure peeling and form a large radial thermal resistance.
  • the upper and lower sides of the ventilation fin film wave need sufficient support strength to be pressed, which limits the heat exchange efficiency of the surface of the ventilation fin and increases the ventilation resistance; the moisture content of the outer surface of the flat tube evaporating surface is insufficient in wettability. It is difficult to completely eliminate the surface gas-containing layer. If the water circulation amount is increased, the membrane evaporation surface of the surface of the ventilation fin film wave is submerged to increase the airflow resistance and the surface heat exchange efficiency.
  • the rotor and stator cores and coils of the motor cannot be effectively eliminated due to the strong heat release caused by the magnetic flux of the alternating magnetic field, which reduces the efficiency of the motor. It is obvious that the thermal resistance formed by the difference between the operating temperature of the compressor and the condensing temperature hinders the heat emission, which hinders the extraction of the cooling capacity and increases the compression work.
  • the current air conditioning unit consisting of the above three components has a thermal cycle system.
  • the efficiency of the system is not perfect enough and needs further improvement. Summary of the invention
  • the invention overcomes the above-mentioned technical defects, and provides a low-drop differential circulating heat pump air-conditioning unit, which optimizes the thermal circulation system by improving the three components of the J 2 , the evaporator and the fully enclosed compressor, thereby establishing a more perfect Efficient thermal cycling, especially to improve heat pump efficiency.
  • the low-drop differential circulation heat pump air conditioning unit of the present invention comprises an outdoor side heat exchanger water-permeable condenser J 2 , an indoor-side heat exchanger internal scroll evaporator and an internal heat pipe compressor M (hereinafter referred to as a cold heat pipe air conditioner).
  • the heat exchange system of the water-permeable condenser J 2 of the chamber-side heat exchanger is fastened to the upper and lower by a multi-layer J 2 piece and a multilayer film type wave fin (referred to as a film wave)
  • the upper splint has a drip pipe with a small hole and a drip pipe with a small hole
  • the sprinkler pipe is connected to the outlet of the small circulation pump, and the small circulation pump is placed.
  • the suction port is connected to the outer tank sink, and the drip pipe is connected to the water supply pipe connected to the water source.
  • J 2 can be made into a curved shape, a circular shape and an L shape.
  • Each J 2 piece has two parallel flat tubes inserted into the inner fins, the inner fins have a bi-directional strip-shaped window on the vertical wall surface, the outer wall of the flat tube is rolled with a lateral water guiding groove, and the flat tube is covered with a film-type evaporating surface.
  • the flat tubes are embedded with longitudinally spaced long strips of sponge and card, and the lower and left and right semicircles are made of thin aluminum sheets, uniformly perforated with fine pores, and a water-permeable support sheet with a membrane evaporation surface on the outside.
  • the J 2 piece can also be made of another inner tube flat tube or a single tube J 2 piece.
  • the skeleton of the film-forming material is rolled into a fine corrugated skeleton by a thin-coated aluminum sheet to form a capillary groove, and the two sides are processed into a fluffy structure by using a water-absorbent fiber material to form a composite belt having a film evaporation surface on both sides. material.
  • the film wave is a wave shape, and the vertical wall surface is bi-directional strip-shaped window.
  • the improvement of the water-permeable condenser J 2 can increase the heat transfer coefficient outside the flat tube to 5 ⁇ 10Kw/M 2 ⁇ V, thereby reducing the consumption of the raw material of the condenser, and reducing the volume, weight, and ventilation resistance of the external machine. Open up technical channels.
  • the internal side heat exchanger vortex evaporator J i the internal thread of the interposed aluminum core is a spaced length rack, the long rack spacing opening forms a serration, and the long teeth force the refrigerant to vortex at a helix angle ⁇ , serration Exchange the boundary layer to form a turbulent flow, the centrifugal force of the rotation and the surface tension will be in the liquid part
  • the refrigerant crucible enhances radial heat conduction to the wall.
  • the internal heat pipe compressor M the cooling heat pipe of the fully enclosed rotor type compressor is mainly for the cylinder wall with a higher working temperature, the lubricating oil outside the cylinder, the stator core, and is uniformly distributed on the outer circumference of the stator core wire groove.
  • the branch pipe, the branch pipe passing vertically through the stator core bypasses the coil downward, and a part passes through the upper and lower caps and cylinders of the cylinder, and is evenly distributed around the circumference of the cylinder wall (staggered suction pipe and exhaust valve plate); the other part wears Through the oil sump hole, this part of the branch pipe is covered with fins at the oil immersion part.
  • the upper and lower annular tubes are respectively connected in parallel with the respective branches at the top and the bottom, and the upper annular tube is connected to the top heat pipe exhaust pipe and the lower circular ring pipe is connected to the bottom heat pipe inlet pipe.
  • the branch pipe is a thin round pipe in which the inner wall surface axially distributes the capillary groove.
  • the rotor core distributes cooling holes.
  • a spiral heat return pipe is arranged in the liquid vapor separator.
  • the upper annular tube and the heat pipe exhaust pipe of the heat pipe can be removed to become the open internal heat pipe compressor ⁇ ⁇ .
  • M's compression heat release and motor heat release should be excluded. This part of the heat, if cooled by J 2 , increases the heat load of J 2 , and can fully utilize the low temperature circulating water in the bottom tank, M bottom Immersion can also enhance the cooling of M.
  • Heat pipe circuit After the primary pipe of the heat pipe is cooled by the auxiliary heat pipe, the spiral cooling pipe immersed in the water tank is in a liquid state, and then the heat pipe is introduced into the lower ring pipe to be distributed to each branch pipe to absorb the heat and boil and vaporize (referred to as secondary compression). ), and form a lift from the heat pipe exhaust pipe to form a gravity heat pipe.
  • the inner wall of the branch pipe is axially grooved, on the one hand, the inner cooling can be strengthened, and on the other hand, the lift of the capillary groove can raise the liquid level height of the liquid medium.
  • the cylinder wall Under the isothermal cooling of the heat pipe, the cylinder wall can realize the exothermic compression close to the isothermal compression, and the heat release channel of the system can be unblocked to enhance the extraction capacity of the cooling capacity.
  • Bayer IJ focuses on enhancing the condensation of J 2 and the heat exchange efficiency.
  • M compression heat release and motor heat release shell IJ should be transported to the condensation, from the outflow of liquid refrigerant into two: heat pipe loop, the split refrigerant enters the heat absorption of each branch in M under the action of gravity Boiling evaporation (secondary compression) is the vapor heat pipe exhaust; the other way is reduced by capillary throttling to P. After being absorbed by heat in J 2 , it is compressed by M to be compressed and compressed into compressed exhaust gas, and the compressed exhaust gas and the heat pipe exhaust are combined, that is, equal pressure is sent to the condensation heat release.
  • An open internal heat pipe compressor ⁇ ⁇ can be used.
  • the absorption of the strong absorbent in the cooling state is a "condensation function".
  • the concentration of the absorbent is the storage of the absorbed energy.
  • the absorbed air energy in the evaporator is concentrated to the vapor state, and the vapor state X is M inhalation, i, pressurized by a small liquid pump to the heat pipe absorption heat release and motor heat release (secondary compression) further concentrated to i 2 and vapor state Xl discharged from the heat pipe exhaust pipe combined with M compressed exhaust gas
  • the ⁇ ⁇ condition is cooled to a dilute solution.
  • the heat absorption and heat release (secondary compression) energy absorbed by the heat pipe can enhance the heat pump energy and heat pump efficiency.
  • the heat of the shower drain is considered to enhance the heat pump energy in the water circulation loop.
  • the internal heat pipe compressor eliminates and utilizes the compression heat release and the motor heat release, and realizes the exothermic compression close to the isothermal compression, which significantly improves the heat pump efficiency and the cooling efficiency.
  • Figure 1 is a cross-sectional view of a J 2 sheet
  • Figure 2 is a cross-sectional view of a cross section of the inner crucible tube
  • Figure 2a is a view taken along line A of Figure 2;
  • Figure 3 is a cross-sectional view of a single tube J 2 sheet
  • Figure 4 is a front view of the ventilation fin film wave
  • Figure 5 is a cross-sectional view of a film wave strip
  • Figure 6 is a development view of the vortex tube in the evaporator
  • Figure 6a is a cross-sectional view taken along line A-A of Figure 6;
  • Figure 6b is a cross-sectional view taken along line B-B of Figure 6;
  • Figure 7 is a front cross-sectional view of the internal heat pipe compressor M
  • Figure 8 is a front cross-sectional view of the open internal heat pipe compressor M K ;
  • Figure 9 is a plan view of the stator core lamination
  • Figure 10 is a cycle diagram of a cold-heat pipe air conditioning refrigeration unit
  • Figure 11 is a cycle diagram of a cold-heat pipe air-conditioning unit using an open-type internal heat pipe compressor ⁇ ⁇ ;
  • Figure 12 is a cycle diagram of a cold-heat pipe air-conditioning 8-word circulating heat pump unit;
  • Figure 13 is a cycle diagram of a heat pump type water heater system. detailed description
  • J 2 sheet 1 has two parallel tubes 2 arranged in parallel, the inner tube 3 is inserted into the flat tube 2, and the vertical wall surface of the inner fin 3 is bi-directional strip-shaped opening window 4.
  • the outer wall surface of the flat tube 2 is rolled with a lateral water guiding groove, and the flat tube 2 is covered with a film evaporation surface 5.
  • the flat tubes 2 are embedded with longitudinally spaced long strips of sponge 6 and card 7, and the lower and left and right semicircles have water-permeable sheets 8 , and the water-permeable sheets 8 are made of thin aluminum sheets to form uniform water-permeable pores 9 .
  • the J2 sheet 1 may also employ an inner spur flat tube 11, the inner wall of which has a ribbed spike 12 and a partition wall 13, and the outer wall surface also rolls the lateral water guiding groove 14.
  • the film wave 16 is a corrugated fin having a bifurcated strip opening window 17 in a vertical wall.
  • the skeleton of the composite strip 18 from which the film wave 16 is formed is rolled into a fine corrugated skeleton 19 by a coated aluminum sheet, and a double-sided capillary groove 20 is formed, and a film evaporation surface 21 is formed on both sides.
  • J 2 is an arc shape, a circular shape, and an L shape.
  • the inner fin flat tube 2 or the inner fin flat tube 11 is a refrigerant tube, and each flat tube is connected to constitute a J 2 refrigerant flow path.
  • the film evaporation faces 5, 10, 21 are nonwoven fabrics made of a corrosion-resistant water-absorbent fiber material.
  • J 2 water seepage process The supplementary water slowly drops into the membrane wave 16 through the small hole in the drip pipe, a part flows along the capillary groove 20 to the J 2 piece 1 , and a part is fully expanded on the surface of the film evaporation surface 21 of the fluffy structure to form a huge
  • the evaporation surface area, the water seepage flow cooled by the membrane wave 16 is uniformly distributed in the lateral water guiding groove 14 in the membrane evaporation surface 5 and the elongated sponge 6 of the J 2 sheet 1, and the water leakage pores passing through the water permeable sheet 8 9 infiltrates the next layer of film wave 16...
  • J 2 piece 1 of the inner fin flat tube 2 or the inner barbed flat tube 11 is in an infiltrated state.
  • the seepage flow merges the cooling heat pipe in the bottom tank, and the small circulation pump supplies water to the shower pipe periodically, quantitatively and intermittently to maintain a uniform water circulation flow.
  • a filter screen is arranged in the bottom tank, and the water level is controlled by a float valve.
  • Membrane wave 16 water permeable sheet 8
  • J 2 sheet 1 membrane evaporation surface forms a saturated wet air layer in the air flow channel
  • membrane wave 16 window 17 makes the airflow boundary layer frequently replaced to form disturbing turbulence and reduce membrane evaporation
  • the surface water vapor partial pressure of the surface so the J 2 water seepage flow (in standard refrigeration conditions) always tends to 24 ° C, that is, the flat tube surface always tends to 24 ° C Isothermal inertia.
  • J 2 is the evaporator.
  • the ambient temperature is below o°c, a small amount of ethylene glycol is added to the bottom tank (42) to achieve continuous frost-free operation.
  • the internal thread of the interposed aluminum core 22 is spaced apart from the long rack 23 and the short rack 24 .
  • the long rack 23 forms serrations along the flow spacing opening 25 , and the outer wall surface of the aluminum core 22 and the copper tube 26 are interposed.
  • the inner wall is close to the surface.
  • the threaded rod can be used to expand the tube.
  • the branch pipes 27 are evenly distributed on the outer circumference of the wire grooves 29 of the stator core laminations 28.
  • the branch pipe 27 vertically passing through the stator core 28 bypasses the coil 30, partially perpendicularly passing through the cylinder 31 and the upper cover 32, and the lower cover 33 is evenly distributed on the circumference of the inner wall of the cylinder 31 (staggering the suction pipe and the exhaust valve piece)
  • the other portion passes through the oil sump hole 34, and the portion of the branch pipe 27 is covered with the fins 35 at the oil immersion portion.
  • the upper ring tube 36 is connected in parallel with the branch pipes 27 at the top and the heat pipe exhaust pipe 38, and the lower ring pipe 37 is connected in parallel with the branch pipes 27 and the heat pipe inlet pipes 39 at the bottom.
  • the rotor core laminations distribute cooling holes 40.
  • the air conditioning unit consisting of a seepage type cold suspect J 2 , an internal vortex evaporator and an internal heat pipe compressor M is simply referred to as a cold heat pipe air conditioner.
  • the heat pipe medium may also be a refrigerant, heat pipe medium circuit: the gaseous medium is discharged from the heat pipe exhaust pipe 38 through the auxiliary heat pipe 41 and then enters the spiral cooling pipe 43 in the immersion chassis water tank 42. The medium is transferred from the inlet pipe 39 into the lower annular tube 37 and distributed to each branch pipe 27. The liquid medium absorbs the compression heat release in each branch pipe 27 and the motor heats up intensely to be converted into a vapor medium to merge in the upper ring pipe 36.
  • the heat pipe exhaust pipe 38 is exhausted to constitute a gravity heat pipe cycle.
  • the axial capillary groove of the branch pipe 27 enhances the liquid column height of the liquid medium to enhance the anti-gravity effect.
  • the bottom of the M is immersed in water to enhance cooling.
  • Refrigerant circulation circuit The compressed exhaust gas of M is cooled to a liquid state in the ⁇ ⁇ condition, and is supercooled by the spiral heat recovery pipe 45 placed in the liquid vapor separator 44, and then throttled and reduced to ⁇ by the capillary 46. Intake of the endothermic vaporization into a vapor state is taken up by the liquid vapor separator 44 to form a cycle.
  • the liquid refrigerant is reheated and subcooled, which reduces the supply temperature and increases the cooling capacity and reduces the loss of throttling.
  • the water temperature in the bottom tank 42 is 24 to 26 ° C. Under the isothermal cooling of the heat pipe, the end temperature of the M compression is much higher than ⁇ ⁇ , so that the exothermic compression close to isothermal compression can be achieved.
  • the ideal isothermal compression conditions are: The compression process is infinitely slow, and the compressed working fluid is close to the isothermal cylinder wall.
  • the rotor core opening 40 is for reinforced rotor cooling, and the cooling of the lubricating oil outside the cylinder requires that the operating temperature of M be as close as possible to the operating temperature of the heat pipe.
  • Refrigeration circuit ⁇ ⁇ exhaust is divided into two ways: one way through the reversing valve 53 into J 2 in the ⁇ ⁇ working condition condenses into a liquid state, after passing through the check valve 50 through the spiral regenerative pipe 45, the subcooling is cooled by the capillary 46 to ⁇ is absorbed by ⁇ ⁇ after the heat is evaporated in the ⁇ ; the other is the heat pipe circuit: ⁇ ⁇ exhaust gas is cooled by the electromagnetic valve 48 through the auxiliary heat pipe 41 and the spiral cooling pipe 43 immersed in the bottom tank to be liquid.
  • the valve 49 enters each branch pipe 27 to absorb heat and boil and evaporate into heat pipe exhaust.
  • Heating circuit ⁇ ⁇ exhaust gas enters the second stage through the reversing valve 53 after the ⁇ ⁇ working condition is radiated and condensed into a liquid state: one way passes through the check valve 52 and is subcooled by the capillary 46, and then passes through the heating capillary 47 to reduce the flow. Pressed for ⁇ . After entering J 2 , the heat is evaporated to a vapor state and is sucked by ⁇ ⁇ ; the other is a heat pipe circuit: after passing through the check valve 51 , the branch pipe 27 is introduced and the heat is boiled and evaporated to heat pipe exhaust. Heat pipe exhaust and ⁇ ⁇ compressed exhaust are combined into ⁇ ⁇ exhaust.
  • Heat pump type 8-word cycle unit cycle working fluid: refrigerant-absorbent composition.
  • cycle working fluid refrigerant-absorbent composition.
  • the spiral heat recovery pipe 45 is placed in the absorbent separation tank 54.
  • Refrigeration circuit a dilute solution i consisting of an absorbent and a refrigerant.
  • the capillary 46 is throttled to a pressure of P. Thereafter, the inner absorption air energy is concentrated to a solution and the vapor refrigerant X flows into the absorbent separation tank 54 via the reversing valve 53.
  • the vaporous refrigerant X is sucked by the liquid vapor separator 44, and the liquid L is pressurized by the small liquid pump 55 at the bottom and sent to the heat pipe to absorb the compression heat release and the heat of the motor, and further concentrated into i 2 and the vapor refrigerant X1 and pressure.
  • the shrinkage exhaust X is merged through the reversing valve 53 to condense into a dilute solution i in the ⁇ ⁇ condition. After the unidirectional width 50, the spiral heat recovery tube 45 heat exchange and enter the capillary 46.
  • Heating circuit Dilute solution i flowing from J. After the heat exchange in the spiral heat recovery pipe 45 through the check valve 52, the heating capillary 47 is throttled to a pressure P. The J 2 absorbs heat to a solution and vapor phase X flows through the reversing valve 53 into the absorbent separating tank 54, and the vapor state X is sucked by the liquid vapor separator 44, and the solution is pressurized by the small liquid pump 55 at the bottom and sent to the heat pipe for absorption. exothermic heat and compression machine further concentrated vapor and i 2 Xl and X combined compression and discharge through the valve 53 enters the ⁇ ⁇ ⁇ exothermic conditions Condensation into a dilute solution i. ....
  • the concentrated absorbent solution i 2 has a low surface partial pressure under cooling conditions and has strong absorption, which is characterized by super condensation, which can sufficiently reduce the compressor load.
  • the tap water return heat pipe 57 is heated to S 2 into the condensing pipe 63 and is heated to S 3 .
  • the shower head 58 is sprayed and used to flow into the bottom of the bathtub or the chassis 59 to cool down to S 4 through the hemisphere filter 60
  • the filter 61 is filtered by the small water pump 62 and enters the heat recovery tube 57 to release the heat to a temperature of S 5 .
  • the evaporation of the refrigerant to the refrigerant through the evaporation tube 56 is S 6 rows of the down channel to form an open water cycle.
  • Refrigerant line circulation The liquid refrigerant flowing out from the condensing pipe 63 is divided into two paths: one way is throttled down by the capillary 47 to reduce P Q into the evaporation tube 56, and the heat is evaporated to be vaporized by the M; the other heat pipe circuit: The liquid refrigerant enters the heat pipe by the gravity to absorb the compression heat release and the motor exothermic boiling evaporation to the vapor heat pipe exhaust. The heat pipe exhaust and the compressed exhaust gas are combined into the condensing pipe 63 to be cooled by the ⁇ ⁇ condition to be cooled to a liquid refrigerant flowing out of the condensing pipe 63 .

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

Abstract

La présente invention décrit un climatiseur à pompe à chaleur avec un cycle de différence de basse pression qui comprend un condenseur à infiltration d’eau (J2), un évaporateur (J1) avec des tubes en volute intérieurs et un compresseur (M) avec des caloducs intérieurs. Un fluide actif extérieur, c'est-à-dire de l’eau, s’infiltre et revient par cycle entre les ailettes de ventilation du condenseur (J2) et la surface des caloducs pour former un échange thermique forcé. Le cycle de réfrigération du climatiseur est un cycle en forme de 8, dans lequel l’absorbant et le caloporteur servent de fluide actif. En améliorant la structure du condenseur (J2), de l’évaporateur (J1) et du compresseur (M), il est possible d’augmenter davantage la capacité de réfrigération et de réduire le travail comprimé dans le climatiseur selon la présente invention. En même temps, le rendement de la pompe à chaleur peut être amélioré.
PCT/CN2005/002092 2004-12-07 2005-12-05 Climatiseur a pompe a chaleur WO2006060953A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CNB2004101008401A CN100483044C (zh) 2004-12-07 2004-12-07 低压差循环热泵空调机组
CN200410100840.1 2004-12-07

Publications (1)

Publication Number Publication Date
WO2006060953A1 true WO2006060953A1 (fr) 2006-06-15

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CN (1) CN100483044C (fr)
WO (1) WO2006060953A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
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CN103550941A (zh) * 2013-11-15 2014-02-05 厦门绿邦膜技术有限公司 一种低温蒸发浓缩装置及高浓度废水浓缩方法
CN108518338A (zh) * 2018-06-04 2018-09-11 黄石东贝电器股份有限公司 制冷压缩机及制冷设备
CN111481957A (zh) * 2020-05-21 2020-08-04 江西依思特香料有限公司 一种香精香料提取用快速冷凝装置
EP4145062A1 (fr) * 2021-09-07 2023-03-08 BSH Hausgeräte GmbH Système de pompe à chaleur à refroidissement amélioré du compresseur et procédé de fonctionnement du système de pompe à chaleur

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JP5413480B2 (ja) * 2012-04-09 2014-02-12 ダイキン工業株式会社 空気調和装置
TWI635244B (zh) 2015-12-02 2018-09-11 國立臺灣師範大學 Energy-saving compressor
CN108150391A (zh) * 2018-01-12 2018-06-12 珠海凌达压缩机有限公司 压缩机及制冷循环装置
CN110822879B (zh) * 2019-11-27 2021-01-26 江苏天舒电器有限公司 一种基于非共沸混合工质热泵系统的烘干除湿方法
CN112564356A (zh) * 2020-10-28 2021-03-26 西安交通大学 一种电机具有冷却通道的电动涡旋压缩机

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CN103550941A (zh) * 2013-11-15 2014-02-05 厦门绿邦膜技术有限公司 一种低温蒸发浓缩装置及高浓度废水浓缩方法
CN108518338A (zh) * 2018-06-04 2018-09-11 黄石东贝电器股份有限公司 制冷压缩机及制冷设备
CN108518338B (zh) * 2018-06-04 2024-05-17 黄石东贝压缩机有限公司 制冷压缩机及制冷设备
CN111481957A (zh) * 2020-05-21 2020-08-04 江西依思特香料有限公司 一种香精香料提取用快速冷凝装置
CN111481957B (zh) * 2020-05-21 2023-07-25 江西依思特香料有限公司 一种香精香料提取用快速冷凝装置
EP4145062A1 (fr) * 2021-09-07 2023-03-08 BSH Hausgeräte GmbH Système de pompe à chaleur à refroidissement amélioré du compresseur et procédé de fonctionnement du système de pompe à chaleur

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