WO2014185069A1 - Éjecteur - Google Patents

Éjecteur Download PDF

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Publication number
WO2014185069A1
WO2014185069A1 PCT/JP2014/002545 JP2014002545W WO2014185069A1 WO 2014185069 A1 WO2014185069 A1 WO 2014185069A1 JP 2014002545 W JP2014002545 W JP 2014002545W WO 2014185069 A1 WO2014185069 A1 WO 2014185069A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
space
swirling
passage
upstream
Prior art date
Application number
PCT/JP2014/002545
Other languages
English (en)
Japanese (ja)
Inventor
山田　悦久
高野　義昭
西嶋　春幸
Original Assignee
株式会社デンソー
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 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112014002444.9T priority Critical patent/DE112014002444T5/de
Priority to US14/890,170 priority patent/US20160090995A1/en
Publication of WO2014185069A1 publication Critical patent/WO2014185069A1/fr

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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
    • F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits
    • 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
    • F25B2327/00—Refrigeration system using an engine for driving a compressor
    • F25B2327/001—Refrigeration system using an engine for driving a compressor of the internal combustion 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers

Definitions

  • This disclosure relates to an ejector that decompresses a fluid and sucks the fluid by a suction action of a high-speed jet fluid.
  • Patent Document 1 discloses a decompression device that is applied to a vapor compression refrigeration cycle device to decompress a refrigerant.
  • the decompression device of Patent Document 1 has a main body that forms a swirling space for swirling the refrigerant.
  • the refrigerant pressure on the swiveling center side is reduced and the refrigerant is boiled under reduced pressure.
  • the pressure is reduced to the pressure (which causes cavitation).
  • the refrigerant in the gas-liquid mixed state in which the gas-phase refrigerant and the liquid-phase refrigerant on the turning center side are mixed, is caused to flow into the minimum passage area and decompressed.
  • Patent Document 1 also describes an ejector configured using this decompression device as a nozzle.
  • the gas-phase refrigerant that has flowed out of the evaporator is sucked by the suction action of the jet refrigerant injected from the nozzle, and the jet refrigerant and the suction refrigerant are mixed and boosted by the booster section (diffuser section).
  • the booster section diffuseuser section
  • a refrigeration cycle apparatus including an ejector as a refrigerant decompression apparatus (hereinafter referred to as an ejector-type refrigeration cycle)
  • the power consumption of the compressor can be reduced by utilizing the refrigerant pressure-increasing action in the pressure-increasing section of the ejector.
  • the coefficient of performance (COP) of the cycle can be improved as compared with a normal refrigeration cycle apparatus including an expansion valve or the like as the refrigerant decompression device.
  • the flow rate variation of the injected refrigerant injected from the nozzle is suppressed, and the refrigerant in the gas-liquid mixed state is decompressed in the minimum passage area portion, thereby
  • the nozzle efficiency is improved by promoting the boiling of the phase refrigerant.
  • the nozzle efficiency is energy conversion efficiency when the pressure energy of the refrigerant is converted into kinetic energy at the nozzle.
  • the present inventors investigated the cause, and in the ejector described in Patent Document 1, when the refrigerant is caused to flow into the swirl space, the refrigerant is caused to flow in the tangential direction of the swirl space having a circular cross section. It has been found that this is the reason why the nozzle efficiency cannot be improved to a desired value. The reason is that if the refrigerant is caused to flow in the tangential direction of the swirling space having a circular cross section, the reduced-pressure boiling of the refrigerant in the swirling space is suppressed as described later.
  • the ejector includes a swirling space forming member having a swirling space for swirling the fluid, a nozzle that discharges the fluid flowing out of the swirling space by depressurizing, and a high-speed spray ejected from the nozzle.
  • a fluid suction port that sucks the fluid by a fluid suction action, and a body having a boosting unit that boosts the pressure by mixing the ejection fluid and the suction fluid sucked from the fluid suction port.
  • the swirl space has an upstream swirl space that swirls the fluid that flows in from the outside and a downstream swirl space that guides the fluid that has flowed out of the upstream swirl space to the nozzle while swirling.
  • the upstream swirling space and the downstream swirling space have a rotating body shape in which the central axes are coaxially arranged.
  • the upstream swirling space has an outlet portion through which fluid flows out to the downstream swirling space, and the outlet portion has an annular shape along the outer peripheral shape of the upstream swirling space in a cross section perpendicular to the central axis.
  • the downstream swirl space has a circular shape in a cross section perpendicular to the central axis.
  • the fluid pressure on the turning center side in the downstream side turning space is reduced to a pressure at which the fluid boils under reduced pressure (causes cavitation).
  • the fluid of the gas-liquid mixed state which the gas-phase fluid and liquid phase fluid of the turning center side of downstream swirl space mixed can be made to flow in and it can reduce pressure.
  • the gas-liquid mixed state refrigerant does not mean only a gas-liquid two-phase state refrigerant, but also includes a refrigerant in which bubbles are mixed in the refrigerant in the supercooled liquid phase state.
  • the cross-sectional shape of the outlet portion is formed in an annular shape along the outer periphery shape of the upstream swirl space, the fluid that has flowed out from the upstream swirl space is caused to flow in the axial direction from the outer periphery side of the downstream swirl space. be able to.
  • the fluid that has flowed out of the upstream swirling space can be prevented from flowing toward the swiveling center side of the downstream swirling space formed in the shape of a hollow rotating body, and the fluid that has flowed out of the upstream swirling space can be prevented.
  • the flow of the liquid phase fluid staying while circulating in the downstream side swirl space it can be merged with the flow from the outer peripheral side toward the nozzle.
  • the fluid flowing into the downstream swirl space from the upstream swirl space does not hinder the flow of the fluid staying while circulating in the downstream swirl space, and the gas-liquid mixed state flowing into the nozzle It can suppress that the ratio of the gaseous-phase fluid in the fluid of this falls.
  • boiling of the liquid phase fluid in the nozzle can be promoted, and a decrease in the nozzle efficiency of the ejector can be suppressed.
  • the ejector is applied to a vapor compression refrigeration cycle apparatus.
  • the ejector communicates with the refrigerant inlet, the swirling space for turning the refrigerant flowing in from the refrigerant inlet, the decompression space for decompressing the refrigerant flowing out of the turning space, and the refrigerant flow downstream side of the decompression space, and sucks the refrigerant from the outside And a body having a pressurizing space for mixing the refrigerant injected from the decompression space and the suction refrigerant sucked from the suction passage.
  • the ejector further includes a passage forming member having at least a portion disposed in the decompression space and the pressurization space, and the passage formation member has a conical shape whose cross-sectional area increases in a direction away from the decompression space.
  • the refrigerant passage formed between the inner peripheral surface of the body that defines the decompression space and the outer peripheral surface of the passage forming member is a nozzle passage that functions as a nozzle that decompresses and injects the refrigerant flowing out of the swirling space.
  • the refrigerant passage formed between the inner peripheral surface of the body that defines the pressurizing space and the outer peripheral surface of the passage forming member is a diffuser passage that functions as a diffuser that increases the pressure by mixing the injected refrigerant and the suction refrigerant.
  • the swirl space has an upstream swirl space that swirls the refrigerant that flows in from the outside and a downstream swirl space that guides the refrigerant that has flowed out of the upstream swirl space to the nozzle passage while swirling.
  • the upstream swirling space and the downstream swirling space have a rotating body shape in which the central axes are coaxially arranged.
  • the upstream swirling space has an outlet portion through which the refrigerant flows out to the downstream swirling space, and the outlet portion has an annular shape along the outer peripheral shape of the upstream swirling space in a cross section perpendicular to the central axis. Yes.
  • the downstream swirl space has a circular shape in a cross section perpendicular to the central axis.
  • the gas-liquid mixed state refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant on the turning center side of the downstream-side turning space are mixed can be caused to flow into the nozzle passage and depressurized.
  • the refrigerant that has flowed out of the upstream-side swirling space can be merged with the flow from the outer peripheral side toward the nozzle passage among the flow of the liquid-phase refrigerant that circulates in the downstream-side swirling space.
  • the refrigerant flowing into the downstream swirl space from the upstream swirl space does not hinder the flow of the refrigerant that circulates in the downstream swirl space, and the gas-liquid mixture flowing into the nozzle passage is not hindered. It can suppress that the ratio of the gaseous-phase refrigerant
  • the boiling of the liquid refrigerant in the nozzle passage can be promoted, and the decrease in energy conversion efficiency (corresponding to the nozzle efficiency) when converting the pressure energy of the refrigerant into velocity energy in the nozzle passage of the ejector is suppressed. can do.
  • the passage forming member is not limited to one having a shape in which the cross-sectional area expands strictly in the direction away from the decompression space, and the cross-sectional area increases in a direction away from the decompression space at least partially.
  • the shape of the diffuser passage can be expanded outward in the direction away from the decompression space.
  • a conical shape is not limited to the meaning that the passage forming member is formed in a complete conical shape, but a shape close to a conical shape, a shape including a conical shape in part, or It includes the meaning that the shape is a combination of a conical shape, a cylindrical shape, a truncated cone shape, and the like.
  • the shape in which the axial cross-sectional shape is not limited to an isosceles triangle, the shape in which the two sides sandwiching the apex are convex on the inner peripheral side, the shape in which the two sides sandwiching the apex are convex on the outer peripheral side, Furthermore, it is meant to include those having a semicircular cross section.
  • the “rotating body shape” means a solid shape formed when a plane figure is rotated around one straight line (center axis) on the same plane.
  • the “annular shape” along the outer peripheral shape of the upstream swirl space does not mean only a complete annular shape, but a shape in which the outlet portion is divided by a connecting portion of a member that forms the outlet portion. Even if it is, it is meant to include a shape that is substantially annular. Therefore, it may be an annular shape by combining two semicircular shapes.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG. 3.
  • It is a Mollier diagram which shows the state of the refrigerant
  • FIG. 7 is a sectional view taken along line VIII-VIII in FIG. 6. It is a mimetic diagram showing an ejector type refrigerating cycle of a 3rd embodiment of this indication. It is sectional drawing in the axial direction of the ejector of 3rd Embodiment. It is typical sectional drawing which shows the flow of the refrigerant
  • FIGS. 1 to 5 A first embodiment of the present disclosure will be described with reference to FIGS. 1 to 5.
  • the ejector 13 of the present embodiment is applied to a refrigeration cycle apparatus including an ejector as a refrigerant decompression apparatus, that is, an ejector refrigeration cycle 10.
  • this ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling the blown air blown into the vehicle interior, which is the air-conditioning target space.
  • the ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as a refrigerant, and constitutes a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. is doing.
  • HFC refrigerant specifically, R134a
  • coolants for example, R1234yf
  • refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.
  • the compressor 11 sucks the refrigerant and discharges it until it becomes a high-pressure refrigerant.
  • the compressor 11 of the present embodiment is an electric compressor configured by housing a fixed capacity type compression mechanism 11a and an electric motor 11b for driving the compression mechanism 11a in one housing.
  • the compression mechanism 11a various compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism can be adopted. Further, the electric motor 11b is controlled in its operation (number of rotations) by a control signal output from a control device to be described later, and may adopt either an AC motor or a DC motor.
  • the compressor 11 may be an engine-driven compressor that is driven by a rotational driving force transmitted from a vehicle traveling engine via a pulley, a belt, or the like.
  • This type of engine-driven compressor includes a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, and a fixed type that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch.
  • a capacity type compressor or the like can be employed.
  • the refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port side of the compressor 11.
  • the radiator 12 is a heat exchanger for heat radiation that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (outside air) blown by the cooling fan 12d. .
  • the radiator 12 is a condensing unit that exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d to radiate and condense the high-pressure gas-phase refrigerant.
  • 12a a receiver 12b that separates the gas-liquid refrigerant flowing out of the condensing unit 12a and stores excess liquid-phase refrigerant, and a liquid-phase refrigerant that flows out of the receiver unit 12b and the outside air blown from the cooling fan 12d exchange heat.
  • This is a so-called subcool condenser that includes a supercooling section 12c that supercools the liquid-phase refrigerant.
  • the cooling fan 12d is an electric blower whose rotation speed (amount of blown air) is controlled by a control voltage output from the control device.
  • a refrigerant inlet 31 a of the ejector 13 is connected to the refrigerant outlet side of the supercooling portion 12 c of the radiator 12.
  • the ejector 13 functions as a refrigerant pressure reducing device that depressurizes the supercooled high-pressure liquid-phase refrigerant (fluid) that has flowed out of the radiator 12 and flows it downstream, and the refrigerant (fluid) injected at a high speed. It functions as a refrigerant circulation device (refrigerant transport device) that sucks (transports) and circulates refrigerant (fluid) flowing out from the evaporator 14 described later by the suction action. Furthermore, the ejector 13 of the present embodiment also functions as a gas-liquid separator that separates the gas-liquid of the refrigerant whose pressure has been reduced.
  • FIGS. 2 The specific configuration of the ejector 13 will be described with reference to FIGS.
  • the up and down arrows in FIG. 2 indicate the up and down directions in a state where the ejector refrigeration cycle 10 is mounted on the vehicle air conditioner.
  • 3 and 4 are schematic cross-sectional views for explaining the function and shape of each refrigerant passage of the ejector 13, and the same parts as those in FIG. 2 are denoted by the same reference numerals.
  • the ejector 13 of the present embodiment includes a body 30 configured by combining a plurality of constituent members.
  • the body 30 includes a housing body 31 that is formed of a prismatic or cylindrical metal or resin and forms an outer shell of the ejector 13.
  • a nozzle body 32 is provided inside the housing body 31.
  • the middle body 33, the lower body 34, etc. are fixed.
  • the housing body 31 includes a refrigerant inlet 31 a that allows the refrigerant flowing out of the radiator 12 to flow into the body 30, a refrigerant suction port 31 b that sucks the refrigerant flowing out of the evaporator 14, and a gas formed inside the body 30.
  • the liquid-phase refrigerant outlet 31c for flowing the liquid-phase refrigerant separated in the liquid separation space 30f to the refrigerant inlet side of the evaporator 14 and the gas-phase refrigerant separated in the gas-liquid separation space 30f are sucked into the compressor 11.
  • a gas-phase refrigerant outlet 31d and the like that flow out to the side are formed.
  • the refrigerant inflow port 31 a is opened at the center of the upper surface of the housing body 31. Further, the refrigerant inflow passage 31e that guides the refrigerant from the refrigerant inlet 31a to the inside of the body 30 is formed in a columnar shape whose central axis extends in the vertical direction (vertical direction in FIG. 2). Further, the refrigerant inflow passage 31 e guides the refrigerant flowing in from the refrigerant inflow port 31 a to a space formed in the nozzle body 32. 2 and 3, the central axis of the refrigerant inflow passage 31e is indicated by a one-dot chain line.
  • the nozzle body 32 is formed of a substantially conical metal member or the like that tapers in the refrigerant flow direction, and decompresses the refrigerant flowing out of the swirl space 30a and a part of the swirl space 30a in which the refrigerant is swirled.
  • a decompression space 30b is formed.
  • a part of the swirling space 30a and the decompression space 30b are formed in a rotating body shape by combining a cylindrical shape, a truncated cone shape, and the like.
  • the nozzle body 32 is fixed to the inside of the housing body 31 by press-fitting or the like so that the central axis of the space formed therein is arranged coaxially with the central axis of the refrigerant inflow passage 31e.
  • a turning promotion member 38 for turning the refrigerant flowing from the refrigerant inflow port 31a around the central axis of the refrigerant inflow passage 31e is fixed.
  • the swivel promoting member 38 is formed in a disc shape, and the plate surfaces thereof are arranged in parallel to each other.
  • the upper plate 38a forms a fixing portion when the rotation promoting member 38 is fixed in the refrigerant inflow passage 31e.
  • the outer peripheral side surface of the upper plate 38a is press-fitted into the inner peripheral wall surface of the refrigerant inflow passage 31e. It is fixed.
  • a through hole penetrating the front and back of the upper plate 38a is formed in the central portion of the upper plate 38a, and this through hole is an inlet portion 38d through which the refrigerant flowing in from the refrigerant inlet 31a flows out to the nozzle body 32 side. Is configured.
  • the outer diameter of the lower plate 38b is formed smaller than the inner diameter of the refrigerant inflow passage 31e as shown in FIG. Accordingly, an annular gap is formed between the outer peripheral side of the lower plate 38b and the inner peripheral wall surface of the refrigerant inflow passage 31e when viewed from the axial direction of the refrigerant inflow passage 31e.
  • This annular gap constitutes an outlet 38e through which the refrigerant that has flowed into the space between the upper plate 38a and the lower plate 38b flows out to the nozzle body 32 side. Further, no through hole is formed in the lower plate 38b.
  • the plurality of rectifying plates 38c are arranged in an annular shape around the central axis of the refrigerant inflow passage 31e. Further, the plate surfaces of the respective rectifying plates 38c are inclined or curved so as to turn the refrigerant flow around the central axis when viewed from the central axis direction.
  • the refrigerant that has flowed into the refrigerant inflow passage 31e from the refrigerant inflow port 31a flows into the space between the upper plate 38a and the lower plate 38b through the inlet portion 38d of the upper plate 38a.
  • the refrigerant that has flowed into the space between the upper plate 38a and the lower plate 38b flows from the central axis side toward the outer peripheral side in this space.
  • the refrigerant flows along the plate surfaces of the plurality of rectifying plates 38c, so that the refrigerant turns around the central axis.
  • attained the outer peripheral side of the space between the upper side plate 38a and the lower side plate 38b is the lower side (downstream side) of the lower side plate 38b from the exit part 38e formed in the outer peripheral side of the lower side plate 38b.
  • the refrigerant flowing into the space on the lower side (downstream side) of the lower plate 38b is guided to the later-described nozzle passage 13a side while turning around the central axis.
  • the turning promotion member 38 of the present embodiment (specifically, the upper plate 38a) defines a turning space 30a on the lower side (downstream side) thereof. Forming. Furthermore, the space formed between the upper plate 38a and the lower plate 38b inside the turning promotion member 38 is an example of the upstream turning space 301 for turning the refrigerant flowing from the outside.
  • the outlet portion 38e through which the refrigerant flows out from the space (upstream swirl space 301) formed between the upper plate 38a and the lower plate 38b has a cross-sectional shape in a cross section perpendicular to the axial direction of the upstream swirl space 301. Is formed in an annular shape along the inner peripheral shape of the refrigerant inflow passage 31e, that is, the outer peripheral shape of the upstream swirl space 301.
  • the swirling space 30a on the lower side (downstream side) of the lower plate 38b is an example of the downstream swirling space 302 that guides the refrigerant flowing out from the upstream swirling space 301 to the decompression space 30b side while swirling.
  • the swirling space 30a (downstream swirling space 302) on the lower side of the lower plate 38b has a hollow rotating body shape, that is, a cross-sectional shape perpendicular to the axial direction of the refrigerant inflow passage 31e is circular. It is formed into a shape. Therefore, in the downstream swirl space 302, the refrigerant pressure on the central axis side is lower than the refrigerant pressure on the outer peripheral side by the action of the centrifugal force generated by the swirling of the refrigerant.
  • the refrigerant pressure on the central axis side in the downstream-side swirl space 302 is reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation).
  • Such adjustment of the refrigerant pressure on the central axis side in the downstream swirl space 302 is performed by adjusting the number or inclination angle of the plurality of rectifying plates 38c or adjusting the arrangement of the plurality of rectifying plates 38c (for example, This can be done by, for example, arranging a speed increasing blade row.
  • the decompression space 30b formed below the swirl space 30a (specifically, the downstream swirl space 302) among the spaces formed in the nozzle body 32 includes a columnar space and a lower portion of the columnar space.
  • a rotating body is formed by combining a frustoconical space that gradually spreads in the refrigerant flow direction from the side.
  • the passage forming member 35 is formed in a substantially conical shape that gradually widens toward the downstream side of the refrigerant flow, and the central axis thereof is arranged coaxially with the central axis of the refrigerant inflow passage 31e.
  • the passage forming member 35 is formed in a conical shape whose cross-sectional area expands in a direction away from the decompression space 30b.
  • the tip 131 is formed on the upstream side of the refrigerant flow from the portion 30m and gradually decreases in the refrigerant passage area until reaching the minimum passage area 30m, and the refrigerant passage is formed on the downstream side of the refrigerant flow from the minimum passage area 30m.
  • a divergent portion 132 whose area gradually increases is formed.
  • the decompression space 30b and the passage forming member 35 are overlapped (overlapped) when viewed from the radial direction, so the shape of the axial cross section of the refrigerant passage is annular (circular)
  • the shape is a donut shape excluding a small-diameter circular shape arranged coaxially.
  • the spread angle of the passage forming member 35 of the present embodiment is smaller than the spread angle of the frustoconical space of the decompression space 30b, the refrigerant passage area in the divergent portion 132 is directed toward the downstream side of the refrigerant flow. Gradually expanding.
  • a nozzle passage 13a that functions as a nozzle is a refrigerant passage formed between the inner peripheral surface of the pressure reducing space 30b and the outer peripheral surface on the top side of the passage forming member 35 by this passage shape. Further, in the nozzle passage 13a, the refrigerant is depressurized and accelerated so that the flow velocity of the refrigerant in the gas-liquid mixed state becomes higher than the two-phase sound velocity.
  • the refrigerant flowing into the nozzle passage 13a is a refrigerant swirling in the swirling space 30a (specifically, the downstream swirling space 302), the refrigerant flowing through the nozzle passage 13a and the injection injected from the nozzle passage 13a.
  • the refrigerant also has a velocity component in a direction that swirls in the same direction as the refrigerant swirling in the swirling space 30a (the upstream swirling space 301 and the downstream swirling space 302).
  • the middle body 33 is provided with a rotating body-shaped through hole penetrating the front and back at the center, and driving the passage forming member 35 to be displaced to the outer peripheral side of the through hole. It is formed of a metal disk-like member that accommodates the device 37.
  • the central axis of the through hole is disposed coaxially with the central axis of the refrigerant inflow passage 31e and the passage forming member 35.
  • the middle body 33 is fixed inside the housing body 31 and below the nozzle body 32 by press-fitting or the like.
  • An inflow space 30c is formed between the upper surface of the middle body 33 and the inner wall surface of the housing body 31 facing the middle body 33 for retaining the refrigerant flowing in from the refrigerant suction port 31b.
  • the inflow space 30c is viewed from the central axis direction of the refrigerant inflow passage 31e and the passage forming member 35.
  • it is formed in an annular cross section.
  • the suction refrigerant inflow passage connecting the refrigerant suction port 31b and the inflow space 30c extends in the tangential direction of the inner peripheral wall surface of the inflow space 30c when viewed from the central axis direction of the inflow space 30c. Accordingly, in the present embodiment, the refrigerant that has flowed into the inflow space 30c from the refrigerant suction port 31b via the suction refrigerant inflow passage is used as the refrigerant in the swirl space 30a (the upstream swirl space 301 and the downstream swirl space 302). It is made to turn in the same direction.
  • the tapered tip of the nozzle body 32 is formed.
  • the refrigerant passage area gradually decreases in the refrigerant flow direction so as to conform to the outer peripheral shape.
  • a suction passage 30d is formed between the inner peripheral surface of the through hole and the outer peripheral surface on the lower side of the nozzle body 32 to connect the inflow space 30c and the refrigerant flow downstream side of the decompression space 30b. That is, in this embodiment, the suction passage 13b that sucks the refrigerant from the outside is formed by the inflow space 30c and the suction passage 30d. Furthermore, the central axis vertical cross section of the suction passage 13b is also formed in an annular shape, and the suction refrigerant flows while swirling from the outer peripheral side to the inner peripheral side of the central shaft in the suction passage 13b.
  • a pressure increasing space 30e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction is formed on the downstream side of the refrigerant flow in the suction passage 30d.
  • the pressurizing space 30e is a space for mixing the refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the suction passage 30d.
  • the lower side of the passage forming member 35 described above is disposed. Further, the expansion angle of the conical side surface of the passage forming member 35 in the pressure increasing space 30e is smaller than the expansion angle of the frustoconical space of the pressure increasing space 30e. The flow gradually expands toward the downstream side.
  • a diffuser passage 13c functioning as a diffuser, and the velocity energy of the mixed refrigerant of the injection refrigerant and the suction refrigerant is converted into pressure energy. That is, in the diffuser passage 13c, the injection refrigerant and the suction refrigerant are mixed and pressurized.
  • the cross-sectional shape perpendicular to the central axis of the diffuser passage 13c is also formed in an annular shape.
  • the refrigerant injected from the nozzle passage 13a to the diffuser passage 13c and the refrigerant sucked from the suction passage 13b are the same as the refrigerant swirling in the swirling space 30a (the upstream swirling space 301 and the downstream swirling space 302). It has a velocity component in the direction of turning in the direction. Accordingly, the refrigerant flowing in the diffuser passage 13c and the refrigerant flowing out of the diffuser passage 13c also have the speed in the direction of turning in the same direction as the refrigerant swirling in the swirling space 30a (the upstream swirling space 301 and the downstream swirling space 302). Has ingredients.
  • the drive device 37 disposed inside the middle body 33 and displacing the passage forming member 35 will be described.
  • the drive device 37 is configured to include a circular thin plate diaphragm 37a which is a pressure responsive member. More specifically, as shown in FIG. 2, the diaphragm 37 a is fixed by welding or the like so as to partition a cylindrical space formed on the outer peripheral side of the middle body 33 into two upper and lower spaces.
  • the space on the upper side constitutes an enclosed space 37b in which a temperature-sensitive medium whose pressure changes according to the temperature of the refrigerant flowing out of the evaporator 14 is enclosed.
  • a temperature-sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed in the enclosed space 37b so as to have a predetermined density. Therefore, the temperature sensitive medium in this embodiment is R134a.
  • the lower space of the two spaces partitioned by the diaphragm 37a constitutes an introduction space 37c for introducing the refrigerant flowing out of the evaporator 14 through a communication path (not shown). Therefore, the temperature of the refrigerant flowing out of the evaporator 14 is transmitted to the temperature-sensitive medium enclosed in the enclosed space 37b through the lid member 37d and the diaphragm 37a that partition the inflow space 30c and the enclosed space 37b.
  • the suction passage 13 b is disposed above the middle body 33 of the present embodiment, and the diffuser passage 13 c is disposed below the middle body 33. Therefore, at least a part of the drive device 37 is disposed at a position sandwiched between the suction passage 13b and the diffuser passage 13c when viewed in the radial direction of the axis.
  • the enclosed space 37b of the drive device 37 is a position that overlaps with the suction passage 13b and the diffuser passage 13c when viewed from the central axis direction of the refrigerant inflow passage 31e, the passage forming member 35, and the like. It is disposed at a position surrounded by the suction passage 13b and the diffuser passage 13c. As a result, the temperature of the refrigerant flowing out of the evaporator 14 is transmitted to the enclosed space 37b, and the internal pressure of the enclosed space 37b becomes a pressure corresponding to the temperature of the refrigerant flowing out of the evaporator 14.
  • the diaphragm 37a is deformed according to the differential pressure between the internal pressure of the enclosed space 37b and the pressure of the refrigerant flowing out of the evaporator 14 flowing into the introduction space 37c.
  • the diaphragm 37a is preferably formed of a tough material having high elasticity and good heat conduction, and is preferably formed of a thin metal plate such as stainless steel (SUS304).
  • the upper end side of a columnar actuating rod 37e is joined to the center portion of the diaphragm 37a by welding or the like, and the lowermost side (bottom side) of the passage forming member 35 is fixed to the lower end side of the actuating rod 37e. ing.
  • the diaphragm 37a and the passage forming member 35 are connected, and the passage forming member 35 is displaced in accordance with the displacement of the diaphragm 37a, and the refrigerant passage area of the nozzle passage 13a (passage sectional area in the minimum passage area portion 30m) is adjusted.
  • the diaphragm 37a displaces the channel
  • the diaphragm 37a displaces the passage forming member 35 in a direction (vertical direction upper side) in which the passage sectional area in the minimum passage area portion 30m is reduced.
  • the diaphragm 37a displaces the passage forming member 35 in the vertical direction according to the superheat degree of the refrigerant flowing out of the evaporator 14, so that the superheat degree of the refrigerant flowing out of the evaporator 14 approaches a predetermined value.
  • the passage sectional area in the minimum passage area portion 30m can be adjusted.
  • the gap between the operating rod 37e and the middle body 33 is sealed by a sealing member such as an O-ring (not shown), and the refrigerant does not leak from the gap even if the operating rod 37e is displaced.
  • the bottom surface of the passage forming member 35 receives a load of a coil spring 40 fixed to the lower body 34.
  • the coil spring 40 applies a load that urges the passage forming member 35 toward the side that reduces the cross-sectional area of the passage in the minimum passage area portion 30m (the upper side in FIG. 2). It is also possible to change the valve opening pressure of the passage forming member 35 to change the target degree of superheat.
  • a plurality (specifically, two as shown in FIGS. 2 and 3) of columnar spaces are provided on the outer peripheral side of the middle body 33, and each of the circular thin plate-like shapes is provided inside the space.
  • two diaphragms 37a are fixed to form two driving devices 37, the number of driving devices 37 is not limited to this.
  • a diaphragm formed by an annular thin plate is fixed in a space formed in an annular shape when viewed from the central axis direction, and the diaphragm and the passage forming member 35 are connected by a plurality of operating rods. Also good.
  • the lower body 34 is formed of a cylindrical metal member, and is fixed in the housing body 31 by screws or the like so as to close the bottom surface of the housing body 31.
  • a gas-liquid separation space 30f is formed between the upper side of the lower body 34 and the middle body 33 to separate the gas and liquid refrigerant flowing out of the diffuser passage 13c. Yes.
  • the gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space, and the central axis of the gas-liquid separation space 30f is also coaxial with the central axes of the refrigerant inflow passage 31e, the passage forming member 35, and the like. Is arranged.
  • the refrigerant flowing out of the diffuser passage 13c and flowing into the gas-liquid separation space 30f swirls in the same direction as the refrigerant swirling in the swirling space 30a (the upstream swirling space 301 and the downstream swirling space 302). It has a velocity component in the direction. Therefore, the gas-liquid refrigerant is separated in the gas-liquid separation space 30f by the action of centrifugal force.
  • a cylindrical pipe 34a is provided coaxially with the gas-liquid separation space 30f and extending upward. And the liquid phase refrigerant
  • a gas-phase refrigerant outflow passage 34b is formed in the pipe 34a to guide the gas-phase refrigerant separated in the gas-liquid separation space 30f to the gas-phase refrigerant outlet 31d of the housing body 31.
  • the above-described coil spring 40 is fixed to the upper end portion of the pipe 34a.
  • the coil spring 40 also functions as a vibration buffer member that attenuates the vibration of the passage forming member 35 caused by pressure pulsation when the refrigerant is depressurized.
  • an oil return hole 34c for returning the refrigeration oil in the liquid-phase refrigerant into the compressor 11 through the gas-phase refrigerant outflow passage 34b is formed in the root part (lowermost part) of the pipe 34a.
  • the inlet side of the evaporator 14 is connected to the liquid-phase refrigerant outlet 31 c of the ejector 13.
  • the evaporator 14 performs heat exchange between the low-pressure refrigerant decompressed by the ejector 13 and the blown air blown into the vehicle interior from the blower fan 14a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is a vessel.
  • the blower fan 14a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.
  • a refrigerant suction port 31 b of the ejector 13 is connected to the outlet side of the evaporator 14. Further, the suction side of the compressor 11 is connected to the gas-phase refrigerant outlet 31 d of the ejector 13.
  • a control device includes a known microcomputer including a CPU, a ROM, a RAM, and the like and its peripheral circuits. This control device performs various calculations and processes based on the control program stored in the ROM, and controls the operations of the various electric actuators 11b, 12d, 14a and the like described above.
  • control device includes an internal air temperature sensor that detects the temperature inside the vehicle, an external air temperature sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and an air temperature (evaporator temperature) of the evaporator 14.
  • a sensor group for air conditioning control such as an evaporator temperature sensor to detect, an outlet side temperature sensor to detect the temperature of the radiator 12 outlet side refrigerant, and an outlet side pressure sensor to detect the pressure of the radiator 12 outlet side refrigerant are connected, Detection values of these sensor groups are input.
  • an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input to the control device.
  • various operation switches provided on the operation panel there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.
  • control device of the present embodiment is configured integrally with a control unit that controls the operation of various control target devices connected to the output side of the control device.
  • a configuration (hardware and software) for controlling the operation constitutes a control unit of each control target device.
  • operation of the electric motor 11b of the compressor 11 comprises the discharge capability control part.
  • the vertical axis of the Mollier diagram shows pressures corresponding to P0, P1, and P2 in FIG.
  • the control device operates the electric motor 11b, the cooling fan 12d, the blower fan 14a, and the like of the compressor 11.
  • the compressor 11 sucks the refrigerant, compresses it, and discharges it.
  • the high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 11 flows into the condenser 12a of the radiator 12 and exchanges heat with the blown air (outside air) blown from the cooling fan 12d. , Dissipates heat and condenses.
  • the refrigerant that has dissipated heat in the condensing unit 12a is gas-liquid separated in the receiver unit 12b.
  • the liquid-phase refrigerant separated from the gas and liquid in the receiver unit 12b exchanges heat with the blown air blown from the cooling fan 12d in the supercooling unit 12c, and further dissipates heat to become a supercooled liquid-phase refrigerant (FIG. 5). a5 point ⁇ b5 point).
  • the supercooled liquid-phase refrigerant that has flowed out of the supercooling portion 12c of the radiator 12 passes through the nozzle passage 13a formed between the inner peripheral surface of the decompression space 30b of the ejector 13 and the outer peripheral surface of the passage forming member 35.
  • the pressure is reduced entropically and injected (b5 point ⁇ c5 point in FIG. 5).
  • the refrigerant passage area in the minimum passage area portion 30m of the decompression space 30b is adjusted so that the superheat degree of the refrigerant on the outlet side of the evaporator 14 approaches a predetermined value.
  • the refrigerant flowing out of the evaporator 14 by the suction action of the refrigerant injected from the nozzle passage 13a passes through the refrigerant suction port 31b and the suction passage 13b (more specifically, the inflow space 30c and the suction passage 30d). Sucked. Further, the refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b and the like flow into the diffuser passage 13c (point c5 ⁇ d5, point h5 ⁇ d5 in FIG. 5).
  • the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area.
  • the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d5 ⁇ point e5 in FIG. 5).
  • the refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (point e5 ⁇ f5, point e5 ⁇ g5 in FIG. 5).
  • the liquid refrigerant separated in the gas-liquid separation space 30f flows out from the liquid refrigerant outlet 31c and flows into the evaporator 14.
  • the refrigerant flowing into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates, and the blown air is cooled (g5 point ⁇ h5 point in FIG. 5).
  • the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out of the gas-phase refrigerant outlet 31d, is sucked into the compressor 11, and is compressed again (point f5 ⁇ a5 in FIG. 5).
  • the ejector refrigeration cycle 10 of the present embodiment operates as described above, and can cool the blown air blown into the vehicle interior. Further, in the ejector refrigeration cycle 10, since the refrigerant whose pressure has been increased in the diffuser passage 13c is sucked into the compressor 11, the driving power of the compressor 11 can be reduced and cycle efficiency (COP) can be improved. .
  • COP cycle efficiency
  • the fluid is swirled in the upstream swirl space 301 and the downstream swirl space 302, thereby reducing the fluid pressure on the swirl center side of the downstream swirl space 302 and the refrigerant boiling under reduced pressure. It can be reduced to a pressure that causes cavitation. Then, the gas-liquid mixed refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant on the turning center side of the downstream-side turning space 302 are mixed can be introduced into the nozzle passage 13a and depressurized.
  • the state of the refrigerant flowing into the swirl space 30a (specifically, the upstream swirl space 301) changes due to changes in the outside air temperature
  • the density of the refrigerant flowing into the nozzle passage 13a greatly changes. This can be suppressed and fluctuations in the flow rate of the injection refrigerant injected from the nozzle passage 13a can be suppressed.
  • the state of the refrigerant in the vicinity of the minimum passage area 30m is brought close to a gas-liquid mixed state in which the gas-phase refrigerant and the liquid-phase refrigerant are homogeneously mixed,
  • the flow rate of the refrigerant can be accelerated until it becomes equal to or higher than the speed of sound.
  • the refrigerant in a gas-liquid mixed state that has become a supersonic state is caused to flow into the divergent section 132, so that it can be further accelerated and injected. Therefore, the nozzle passage 13a can be expected to effectively improve the energy conversion efficiency when converting the pressure energy of the refrigerant into velocity energy.
  • the cross-sectional shape of the outlet portion 38e that allows the refrigerant to flow out of the upstream swirl space 301 is formed in an annular shape along the outer peripheral shape of the upstream swirl space 301.
  • the refrigerant flowing out of the upstream swirl space 301 can be caused to flow in the axial direction from the outer peripheral side of the downstream swirl space 302 as indicated by a thick solid arrow in FIG.
  • downstream swirl space 302 out of the flow of the liquid-phase refrigerant that stays while circulating the refrigerant flowing out of the upstream swirl space 301 in the downstream swirl space 302 (flow indicated by the broken line arrow in FIG. 3). It can be made to merge with the flow which goes to the nozzle channel
  • the refrigerant flowing into the downstream swirl space 302 from the upstream swirl space 301 does not hinder the flow of the fluid staying while circulating in the downstream swirl space 302, and flows into the nozzle passage 13a. It can suppress that the ratio of the gaseous-phase refrigerant
  • the upstream swirl space 301 is formed in the space between the upper plate 38a and the lower plate 38b, and the refrigerant on the center side of the upstream swirl space 301 is supplied to the rectifying plate 38c.
  • a swirl promoting member 38 that swirls the refrigerant in the upstream swirl space 301 around the central axis by flowing toward the outer periphery along the plate surface is provided.
  • the shape of the outlet portion 38 e that allows the refrigerant to flow out of the upstream side swirl space 301 can be easily formed into an annular shape along the outer peripheral shape of the upstream side swirl space 301. Furthermore, since it is not necessary to provide a space for generating a swirl flow in the refrigerant outside the upstream swirl space 301, the size of the ejector 13 as a whole can be prevented from increasing in size.
  • the passage forming member 35 is formed in a conical shape whose cross-sectional area increases in the direction away from the decompression space 30b, and the cross-sectional shape of the diffuser passage 13c is annular. Since it forms, the shape of the diffuser channel
  • the body 30 of the ejector 13 of the present embodiment is formed with a gas-liquid separation space 30f for separating the gas-liquid of the refrigerant flowing out from the diffuser passage 13c, a gas-liquid separation device is provided separately from the ejector 13. In contrast, the volume of the gas-liquid separation space 30f can be effectively reduced.
  • the refrigerant flowing out of the diffuser passage 13c formed in an annular cross section already has a velocity component in the direction of swirling, so that the refrigerant flows in the gas-liquid separation space 30f. It is not necessary to provide a space for generating a swirling flow. Therefore, the volume of the gas-liquid separation space 30f can be effectively reduced as compared with the case where a gas-liquid separation device is provided separately from the ejector 13.
  • the turning promotion member 39 of the present embodiment includes a plate 39a formed in a disc shape, a plurality of rectifying plates 39b protruding downward from the outer peripheral portion of the plate 39a, and rectifying from the central portion of the plate 39a. It has a cylindrical protrusion 39c that protrudes in the same direction (downward) as the plate 39b.
  • the protruding amount of the protruding portion 39c from the plate 39a is equal to or more than the protruding amount of the rectifying plate 39b.
  • the outer diameter of the refrigerant inflow passage 31e of this embodiment is formed larger than the outer diameter of the space formed inside the nozzle body 32, and the outer diameter of the plate 39a is smaller than the outer diameter of the refrigerant inflow passage 31e. Is formed. Therefore, an annular gap is formed between the outer peripheral side of the plate 39a and the inner peripheral wall surface of the refrigerant inflow passage 31e when viewed from the axial direction of the refrigerant inflow passage 31e. This annular gap constitutes an inlet portion 39d through which the refrigerant flowing in from the refrigerant inlet 31a flows out to the nozzle body 32 side.
  • the plurality of rectifying plates 39b are arranged in an annular shape around the central axis of the refrigerant inflow passage 31e. Further, the plate surfaces of the respective rectifying plates 39b are inclined or curved so as to turn the refrigerant flow around the central axis when viewed from the central axis direction. These rectifying plates 39b are provided in a range from the outer periphery of the plate 39a to the outer periphery of the space formed in the nozzle body 32 when viewed from the central axis direction.
  • the central axis of the protrusion 39c is arranged coaxially with the central axis of the refrigerant inflow passage 31e, and the outer diameter of the protrusion 39c is smaller than the outer diameter of the space formed inside the nozzle body 32. Yes. Therefore, a cylindrical gap space in which a cross section perpendicular to the central axis direction is formed in an annular shape is formed between the inner peripheral side of the plurality of rectifying plates 39b arranged in an annular shape and the outer peripheral side of the protruding portion 39c. Has been.
  • the refrigerant flowing into the refrigerant inflow passage 31e from the refrigerant inflow port 31a flows into the outer peripheral side of the plurality of rectifying plates 39b arranged in an annular shape through the inlet portion 39d on the outer peripheral side of the plate 39a. Further, the refrigerant flowing into the outer peripheral side of the plurality of rectifying plates 39b flows toward the inner peripheral side of the plurality of rectifying plates 39b. At this time, the refrigerant flows along the plate surfaces of the plurality of rectifying plates 39b, so that the refrigerant turns around the central axis.
  • the refrigerant that has flowed out to the inner peripheral side of the plurality of rectifying plates 39b flows into a cylindrical gap space formed between the inner peripheral side of the plurality of rectifying plates 39b and the outer peripheral side of the protruding portion 39c.
  • the refrigerant that has flowed into the cylindrical gap space flows from the lowermost side of the cylindrical gap space to the space on the lower side (downstream side) of the turning promotion member 39 while turning around the central axis. Furthermore, the refrigerant that has flowed into the space below the turning promotion member 39 is guided to the nozzle passage 13a described later while turning around the central axis.
  • a cylindrical gap space formed between the inner peripheral side of the plurality of rectifying plates 39b and the outer peripheral side of the protruding portion 39c is formed. It is an example of the upstream side turning space 301 which turns the refrigerant
  • the upstream swirl space 301 has an annular shape similar to the cross-sectional shape in the cross section perpendicular to the axial direction, that is, an annular shape along the outer peripheral shape of the upstream swirl space 301.
  • the space on the lower side (downstream side) of the turning promotion member 39 is an example of the downstream turning space 302 that guides the refrigerant flowing out from the upstream turning space 301 to the pressure reducing space 30b side while turning.
  • Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.
  • the refrigerant flowing out of the upstream swirl space 301 (the flow shown by the thick solid arrow in FIG. 7) is circulated in the downstream swirl space 302.
  • the flow of the liquid-phase refrigerant that is staying (the flow indicated by the broken line arrow in FIG. 7)
  • it can be merged with the flow from the outer peripheral side of the downstream-side swirl space 302 toward the nozzle passage 13a.
  • a decrease in energy conversion efficiency in the nozzle passage 13a can be suppressed.
  • the upstream swirl space 301 is formed in a rotating body shape in which the cross-sectional shape in a cross section perpendicular to the central axis direction is an annular shape.
  • the shape of the outlet portion 38e to be discharged can be easily formed into an annular shape along the outer peripheral shape of the upstream side swirl space 301.
  • the ejector 53 of the present embodiment does not have a function as a gas-liquid separator, it functions as a refrigerant decompression device and also functions as a refrigerant circulation device (refrigerant transport device), like the ejector 13 of the first embodiment. ).
  • refrigerant transport device refrigerant transport device
  • the ejector 53 has a nozzle 531 and a body 532 as shown in FIG.
  • the nozzle 531 is formed of a substantially cylindrical metal (for example, stainless steel alloy) whose tip end gradually tapers in the refrigerant flow direction, and isentropically depressurizes the refrigerant that has flowed inside, The refrigerant flow is injected from the refrigerant injection port 531a provided on the most downstream side.
  • a swirling space 531c for swirling the refrigerant flowing in from the refrigerant inflow port 531b, and a refrigerant passage for depressurizing the refrigerant flowing out of the swirling space 531c.
  • the swirl space 531c is formed inside a cylindrical portion 531g provided on the upstream side of the refrigerant flow of the nozzle 531. Therefore, this cylindrical part 531g may be used as an example of a swirl space forming member having a swirl space 531c. In this embodiment, the swirl space forming member and the nozzle are integrated.
  • a columnar member 531h formed in a columnar shape having a smaller diameter than the inner diameter of the cylindrical portion 531g is disposed inside the cylindrical portion 531g on the refrigerant flow upstream side.
  • the columnar member 531h is formed so that its axial length is shorter than the axial length of the cylindrical portion 531g, and is coaxial with the central axis of the cylindrical portion 531g.
  • the refrigerant inflow passage connecting the refrigerant inlet 531b and the swirling space 531c is open in the cylindrical space, and is tangent to the inner wall surface of the swirling space 531c when viewed from the central axis direction of the swirling space 531c. Extending in the direction.
  • the refrigerant flowing into the cylindrical space from the refrigerant inlet 531b flows along the inner peripheral wall surface of the cylindrical portion 531g and swirls around the central axis of the cylindrical portion 531g. Furthermore, the refrigerant that has flowed out of the cylindrical space flows into the columnar space while turning around the central axis.
  • the cylindrical space in the cylindrical portion 531g is an example of the upstream-side swirl space 311 that swirls the refrigerant flowing from the outside, and the cylindrical shape in the cylindrical portion 531g.
  • the space is an example of the downstream swirl space 312 that guides the refrigerant flowing out of the upstream swirl space 301 to the minimum passage area 531d of the nozzle 531 while swirling.
  • an outlet portion 311 a that is provided on the most downstream side of the cylindrical space (upstream swirl space 311) and allows the refrigerant to flow out of the upstream swirl space 301 is a cross section in a cross section perpendicular to the axial direction of the upstream swirl space 311. It has an annular shape similar to the shape, that is, an annular shape along the outer peripheral shape of the upstream swirl space 311.
  • the downstream swirl space 312 is formed as a hollow rotating body, the refrigerant pressure on the central axis side is reduced in the downstream swirl space 312 due to the centrifugal force generated by the swirling of the refrigerant. Lower than the refrigerant pressure on the outer peripheral side. Therefore, in the present embodiment, during normal operation of the ejector refrigeration cycle 10, the refrigerant pressure on the central axis side in the downstream-side swirling space 312 is reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation). .
  • Such adjustment of the refrigerant pressure on the central axis side in the downstream swirl space 312 can be realized by adjusting the swirling flow velocity of the refrigerant swirling in the downstream swirl space 312. Further, the swirl flow velocity can be adjusted by adjusting the area ratio between the cross-sectional area of the refrigerant inflow passage and the axial vertical cross-sectional area of the downstream swirl space 312, for example. Note that the swirling flow velocity in the present embodiment means the flow velocity in the swirling direction of the refrigerant in the vicinity of the outermost peripheral portion of the swirling space 531c.
  • the refrigerant passage formed inside the nozzle 531 includes a minimum passage area portion 531d having the smallest refrigerant passage area, and a tip portion that gradually reduces the refrigerant passage area from the swirling space 531c toward the minimum passage area portion 531d. 531e and a divergent portion 531f that gradually expands the refrigerant passage area from the minimum passage area portion 531d toward the refrigerant injection port 531a are formed.
  • the body 532 is formed of a substantially cylindrical metal (for example, aluminum) or resin, and functions as a fixing member for supporting and fixing the nozzle 531 inside, and forms an outer shell of the ejector 53. It is. More specifically, the nozzle 531 is fixed by press-fitting or the like so as to be accommodated inside the longitudinal end of the body 532.
  • a refrigerant suction port 532 a is formed in a portion corresponding to the outer peripheral side of the nozzle 531 among the outer peripheral side surfaces of the body 532.
  • the refrigerant suction port 532 a is a through hole that penetrates a portion of the outer peripheral side surface of the body 532 corresponding to the outer peripheral side of the nozzle 531, and is provided so as to communicate with the refrigerant injection port 531 a of the nozzle 531.
  • the refrigerant suction port 532 a sucks the refrigerant that has flowed out of the evaporator 14 due to the suction action of the refrigerant injected from the refrigerant injection port 531 a of the nozzle 531 into the ejector 53.
  • the refrigerant suction port 532a may be used as an example of a fluid suction port that sucks fluid by a suction action of a high-speed jet fluid ejected from the nozzle 531.
  • the body 532 has a diffuser portion 532b for increasing the pressure by mixing the refrigerant injected from the refrigerant injection port 531a and the suction refrigerant sucked from the refrigerant suction port 532a, and the suction refrigerant sucked from the refrigerant suction port 532a.
  • the diffuser unit 532b may be used as an example of a boosting unit that increases the pressure by mixing the jetted fluid ejected from the nozzle 531 and the suctioned fluid sucked from the fluid suction port.
  • the suction passage 532c is formed by a space between the outer peripheral side around the tapered tip of the nozzle 531 and the inner peripheral side of the body 532, and the refrigerant passage area of the suction passage 532c is directed toward the refrigerant flow direction. It is gradually shrinking. Thereby, the flow rate of the suction refrigerant flowing through the suction passage 532c is gradually increased, and energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser portion 532b is reduced.
  • the diffuser portion 532b is disposed so as to be continuous with the outlet side of the suction passage 532c, and is formed so that the refrigerant passage area gradually increases.
  • the function of converting the velocity energy of the mixed refrigerant of the injected refrigerant and the suction refrigerant into pressure energy that is, the function of a pressure increasing unit that depressurizes the mixed refrigerant to increase the pressure of the mixed refrigerant.
  • the wall surface shape of the inner peripheral wall surface of the body 532 forming the diffuser portion 532b of the present embodiment is formed by combining a plurality of curves as shown in the axial cross section of FIG. And since the degree of spread of the refrigerant passage cross-sectional area of the diffuser portion 532b gradually increases in the refrigerant flow direction and then decreases again, the refrigerant can be increased in an isentropic manner.
  • the refrigerant inlet of the gas-liquid separator 60 is connected to the refrigerant outlet side of the diffuser portion 532b of the ejector 53.
  • the gas-liquid separator 60 is a gas-liquid separator that separates the gas-liquid of the refrigerant that has flowed into the interior.
  • the refrigerant inlet side of the evaporator 14 is connected to the liquid phase refrigerant outlet of the gas-liquid separator 60.
  • the gas-phase refrigerant outlet of the gas-liquid separator 60 is connected to the suction port side of the compressor 11.
  • Other configurations and operations are the same as those in the first embodiment.
  • the refrigerant (flow indicated by the broken line arrow in FIG. 10) flowing out from the upstream swirl space 311 is circulated in the downstream swirl space 312 as in the first embodiment.
  • the flow of the liquid refrigerant that has stayed the flow indicated by the broken arrow in FIG. 10
  • the flow can be merged with the flow from the outer peripheral side of the downstream swirl space 312 toward the minimum passage area 531 d of the nozzle 531.
  • the refrigerant inflow passage 31e is formed so as to extend in the tangential direction of the inner wall surface of the swirling space 30a, and further, the same as in the third embodiment inside the swirling space 30a.
  • a cylindrical member is arranged.
  • a cylindrical space formed in a range where the swirl space 30a and the columnar member overlap is defined as an upstream swirl space 301, and a columnar space formed in a range where the swirl space 30a and the columnar member do not overlap is swept downstream.
  • the space 302 may be used.
  • an upstream swirl space 311 and a downstream swirl space 312 may be formed.
  • the drive device 37 for displacing the passage forming member 35 includes an enclosed space 37b in which a temperature-sensitive medium whose pressure changes with temperature change is enclosed, and the enclosed space 37b.
  • a drive device is not limited to this.
  • thermowax that changes in volume depending on temperature
  • a drive device that includes a shape memory alloy elastic member may be employed.
  • a drive device that displaces the passage forming member 35 by an electric motor may be employed.
  • the arrangement of the ejector 53 is such that the axial direction of the nozzle 531 is vertical as in the first and second embodiments. You may arrange
  • the ejector refrigeration cycle 10 including the ejector 13 of the present disclosure is applied to a vehicle air conditioner.
  • the application of the ejector refrigeration cycle 10 including the ejector 13 of the present disclosure is described. Is not limited to this.
  • the present invention may be applied to a stationary air conditioner, a cold storage container, a cooling / heating device for a vending machine, and the like.
  • FIG. 11 is a cross-sectional view in the axial direction of the swirling space 70d showing the result of this simulation analysis.
  • the region where the liquid-phase refrigerant is present is indicated by point hatching, and the flow lines of the refrigerant in this region are indicated by arrows. .
  • the swirl space 70d is formed in the main body 70a of the decompression device 70, and has a hollow rotating body shape (more specifically, a shape in which a cylindrical space and a conical space are coaxially coupled). Is formed.
  • FIG. 11 confirms that the gas-phase refrigerant is unevenly distributed in a columnar shape on the swiveling center side of the swirling space 70d.
  • the liquid-phase refrigerant around the gas-phase refrigerant (hereinafter referred to as the air column) that is unevenly distributed in the columnar shape is axially extended along the air column as indicated by the streamline indicated by the broken-line arrow. It flows from the side of the smallest passage area 70b (the lower side in FIG. 11) toward the other end side in the axial direction (the upper side in FIG. 11).
  • the refrigerant that flows along the air column and reaches the other end in the axial direction flows to the outer peripheral side of the swirling space 70d and flows from the outer peripheral side toward the minimum passage area portion 70b.
  • path area part 70b side is flowing again from the minimum channel
  • the liquid phase refrigerant around the air column stays while circulating, and the liquid phase refrigerant flows from the minimum passage area portion 70b side to the other end side in the axial direction along the air column.
  • the angular momentum of the swirling flow of the refrigerant in the vicinity of the portion 70b is transmitted to the refrigerant in the entire axial direction on the swiveling center side.
  • the reduced-pressure boiling of the refrigerant in the entire axial direction on the turning center side is promoted by the transmission of the angular momentum, and the air column is formed over the entire axial direction in the turning space 70d.
  • the refrigerant flowing into the swirl space 70d from the refrigerant inlet 70c connected to the side surface of the main body 70a circulates around the air column as shown by the streamline indicated by the thick solid arrow in FIG.
  • the outer peripheral side of the staying refrigerant flows toward the minimum passage area portion 70b.
  • the refrigerant flowing into the swirl space 70d is a high-pressure refrigerant that has flowed out of the radiator, even if it flows in the tangential direction of the swirl space 70d having a circular cross section,
  • the refrigerant that has flowed into the swirling space 70d tends to flow toward the low-pressure side (that is, the turning center side).
  • the ratio of the gas-phase refrigerant in the refrigerant in the gas-liquid mixed state flowing into the minimum passage area portion may be reduced, and the nozzle efficiency may be reduced.
  • the gas-liquid mixed state refrigerant does not mean only a gas-liquid two-phase state refrigerant but also includes a refrigerant in which bubbles are mixed in the supercooled liquid phase state.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

L'invention concerne un espace de tourbillonnement (30a) qui crée un état de mélange air-liquide en faisant tourbillonner un fluide frigorigène comprenant un espace de tourbillonnement en amont (301) qui fait tourbillonner un fluide frigorigène s'écoulant vers l'intérieur en provenance de l'extérieur et un espace de tourbillonnement en aval (302) qui fait tourbillonner le fluide frigorigène en provenance de l'espace de tourbillonnement en amont (301) et qui guide celui-ci vers un canal de buse (13a). Par ailleurs, la forme en coupe d'une sortie (38e) de l'espace de tourbillonnement en amont (301) est formée pour être annulaire le long de la circonférence extérieure de l'espace de tourbillonnement en amont (301). Ainsi, l'obstruction de l'écoulement du fluide frigorigène retenu et circulant dans l'espace de tourbillonnement en aval (302) par le fluide frigorigène s'écoulant depuis l'espace de tourbillonnement en amont (301) jusqu'à l'espace de tourbillonnement en aval (302) peut être supprimée, et la réduction au niveau de la proportion du fluide frigorigène en phase gazeuse dans le fluide frigorigène, dans un état de mélange air-liquide, s'écoulant jusqu'au canal de buse (13a) peut être supprimée. En conséquence, l'ébullition du fluide frigorigène dans le canal de buse (13a) peut être facilitée, et une diminution de l'efficacité de la buse de l'éjecteur, qui donne lieu à une diminution de la pression d'un fluide dans un état de mélange air-liquide en raison du tourbillonnement, peut être supprimée.
PCT/JP2014/002545 2013-05-15 2014-05-14 Éjecteur WO2014185069A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112014002444.9T DE112014002444T5 (de) 2013-05-15 2014-05-14 Ejektor
US14/890,170 US20160090995A1 (en) 2013-05-15 2014-05-14 Ejector

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JP2013103141A JP2014224626A (ja) 2013-05-15 2013-05-15 エジェクタ
JP2013-103141 2013-05-15

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WO (1) WO2014185069A1 (fr)

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Publication number Priority date Publication date Assignee Title
GB2524820A (en) * 2014-04-04 2015-10-07 Caltec Ltd Jet pump
EP3994362A4 (fr) * 2019-08-19 2023-07-05 Q.E.D. Environmental Systems, Inc. Pompe à fluide pneumatique à double action de nettoyage tourbillonnant en rotation
EP3907443A1 (fr) * 2020-05-06 2021-11-10 Carrier Corporation Circuit de réfrigération d'éjecteur et procédé de fonctionnement de celui-ci
US11397030B2 (en) * 2020-07-10 2022-07-26 Energy Recovery, Inc. Low energy consumption refrigeration system with a rotary pressure exchanger replacing the bulk flow compressor and the high pressure expansion valve
US11421918B2 (en) 2020-07-10 2022-08-23 Energy Recovery, Inc. Refrigeration system with high speed rotary pressure exchanger

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4378681A (en) * 1981-09-08 1983-04-05 Modisette, Inc. Refrigeration system
JPS6176800A (ja) * 1984-09-25 1986-04-19 Sakou Giken:Kk 蒸気エゼクタ−
JPH032670B2 (fr) * 1981-12-16 1991-01-16 Matsushita Electric Ind Co Ltd
US6138456A (en) * 1999-06-07 2000-10-31 The George Washington University Pressure exchanging ejector and methods of use
JP2010210111A (ja) * 2009-03-06 2010-09-24 Denso Corp エジェクタ方式の減圧装置およびこれを備えた冷凍サイクル
WO2013002872A2 (fr) * 2011-06-10 2013-01-03 Carrier Corporation Éjecteur à tourbillon de débit moteur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4378681A (en) * 1981-09-08 1983-04-05 Modisette, Inc. Refrigeration system
JPH032670B2 (fr) * 1981-12-16 1991-01-16 Matsushita Electric Ind Co Ltd
JPS6176800A (ja) * 1984-09-25 1986-04-19 Sakou Giken:Kk 蒸気エゼクタ−
US6138456A (en) * 1999-06-07 2000-10-31 The George Washington University Pressure exchanging ejector and methods of use
JP2010210111A (ja) * 2009-03-06 2010-09-24 Denso Corp エジェクタ方式の減圧装置およびこれを備えた冷凍サイクル
WO2013002872A2 (fr) * 2011-06-10 2013-01-03 Carrier Corporation Éjecteur à tourbillon de débit moteur

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US20160090995A1 (en) 2016-03-31
DE112014002444T5 (de) 2016-02-18
JP2014224626A (ja) 2014-12-04

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