WO2015015783A1 - エジェクタ - Google Patents
エジェクタ Download PDFInfo
- Publication number
- WO2015015783A1 WO2015015783A1 PCT/JP2014/003931 JP2014003931W WO2015015783A1 WO 2015015783 A1 WO2015015783 A1 WO 2015015783A1 JP 2014003931 W JP2014003931 W JP 2014003931W WO 2015015783 A1 WO2015015783 A1 WO 2015015783A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- passage
- forming member
- space
- nozzle
- Prior art date
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- 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
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- 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
- F04F5/10—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 liquids, e.g. containing solids, or liquids and elastic fluids
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- 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
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- 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
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- 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
- F04F5/48—Control
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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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
- 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
Definitions
- This disclosure relates to an ejector that decompresses a fluid and sucks the fluid by a suction action of a jet fluid ejected at a high speed.
- an ejector is known as a decompression device applied to a vapor compression refrigeration cycle apparatus.
- This type of ejector has a nozzle part that decompresses the refrigerant, sucks the gas-phase refrigerant that has flowed out of the evaporator by the suction action of the jetted refrigerant jetted from the nozzle part, and injects it at the booster (diffuser part)
- the pressure can be increased by mixing the refrigerant and the suction refrigerant.
- a refrigeration cycle apparatus including an ejector as a 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 provided with an expansion valve or the like as the apparatus.
- Patent Document 1 discloses an ejector that is applied to an ejector-type refrigeration cycle and that has a nozzle portion that depressurizes the refrigerant in two stages. More specifically, in the ejector disclosed in Patent Document 1, the refrigerant in the high-pressure liquid phase is decompressed by the first nozzle until the gas-liquid two-phase state is obtained, and the refrigerant in the gas-liquid two-phase state is supplied to the second nozzle. Inflow.
- a diffuser part (a boosting part) is coaxially arranged on an extension line in the axial direction of the nozzle part.
- Patent Document 2 describes that the ejector efficiency can be improved by relatively reducing the spread angle of the diffuser portion arranged in this way.
- the nozzle efficiency is the energy conversion efficiency when the pressure energy of the refrigerant is converted into kinetic energy in the nozzle portion
- the ejector efficiency is the energy conversion efficiency of the entire ejector.
- the effect of improving the nozzle efficiency by flowing the gas-liquid two-phase refrigerant into the second nozzle may not be obtained, and the refrigerant may not be sufficiently boosted in the diffuser section.
- the diffuser portion having a relatively small spread angle disclosed in Patent Literature 2 to the ejector of Patent Literature 1 and improving the ejector efficiency, the diffuser portion is also at a low load of the ejector refrigeration cycle. It is conceivable to sufficiently increase the pressure of the refrigerant at
- an object of the present disclosure is to suppress a decrease in ejector efficiency without causing an increase in the size of an ejector in which a refrigerant passage is formed on the outer peripheral side of a passage forming member.
- the ejector is used in a vapor compression refrigeration cycle apparatus.
- the ejector communicates with a refrigerant inlet into which the refrigerant is introduced, a swirling space in which the refrigerant flowing from the refrigerant inlet swirls, a decompression space in which the refrigerant flowing out of the swirling space is decompressed, and a refrigerant flow downstream of the decompression space.
- the ejector further includes a passage forming member that is disposed at least in the decompression space and in the pressurization space and has a conical shape whose cross-sectional area increases as the distance from the decompression space increases.
- the decompression space has a nozzle passage that functions as a nozzle that decompresses and injects the refrigerant that has flowed out of the swirl space between the inner peripheral surface of the body and the outer peripheral surface of the passage forming member.
- the space for pressurization has a diffuser passage functioning as a diffuser that converts the kinetic energy of the mixed refrigerant of the injected refrigerant and the suction refrigerant into pressure energy between the inner peripheral surface of the body and the outer peripheral surface of the passage forming member.
- the rate of increase in the distance from the central axis of the passage forming member gradually decreases on the outer peripheral surface defining the nozzle passage of the passage forming member toward the refrigerant flow downstream side.
- the passage forming member has a contact portion that contacts the body in the nozzle passage when the passage forming member is displaced in the axial direction in a cross section parallel to the axial direction of the passage forming member.
- an acute angle between the tangent at the contact portion and the central axis is defined as ⁇ 2.
- the passage forming member has a nozzle outlet portion that defines an outlet of the nozzle passage in a cross section parallel to the axial direction.
- a nozzle outlet portion that defines an outlet of the nozzle passage in a cross section parallel to the axial direction.
- an acute angle between the tangent at the nozzle outlet portion and the central axis is defined as ⁇ 3.
- the angle ⁇ 2 and the angle ⁇ 3 satisfy the condition of ⁇ 2 ⁇ ⁇ 3.
- the expansion angle of the portion forming the outlet side of the nozzle passage in the passage forming member is set to the passage It can be made smaller than the spread angle of the part which forms the entrance side of a nozzle channel among formation members.
- the expansion angle of the portion forming the outlet side of the nozzle passage can be set to a relatively small value regardless of the expansion angle of the portion forming the inlet side of the nozzle passage in the passage forming member.
- the main flow direction of the injected refrigerant to be injected can be made closer to the axial direction of the passage forming member.
- the crossing angle between the main flow direction of the injection refrigerant and the main flow direction of the suction refrigerant is reduced by bringing the main flow direction of the suction refrigerant flowing out of the suction passage and joining the injection refrigerant closer to the axial direction. can do. Therefore, energy loss (mixing loss) when the injection refrigerant and the suction refrigerant merge can be suppressed, and a decrease in ejector efficiency can be suppressed.
- the guide member needs to be formed in a shape that expands in the radial direction. There is no. Therefore, it is possible to suppress an increase in the size of the passage forming member in the radial direction as the entire ejector.
- the portion forming the inlet side of the nozzle passage can be set to an appropriate value.
- the passage forming member when the passage forming member is displaced to change the refrigerant passage sectional area of the nozzle passage, the change degree of the refrigerant passage sectional area on the inlet side of the nozzle passage with respect to the displacement amount (stroke amount) of the passage forming member is changed. It can suppress becoming small.
- the flow direction of the main flow of the injection refrigerant and the flow direction of the main flow of the suction refrigerant can be made closer without causing an increase in the size of the physique. Energy loss at the time when the refrigerant and the suction refrigerant merge can be suppressed, and a decrease in ejector efficiency can be suppressed.
- the passage forming member is not limited to one having a shape in which the cross-sectional area expands strictly as it moves away from the decompression space, but at least partially as it moves away from the decompression space.
- the shape of the diffuser passage can be expanded to the outside as the distance from the decompression space is increased.
- “conically formed” is not limited to the meaning that the passage forming member is formed in a complete conical shape. That is, the cross-sectional shape parallel to the axial direction is not limited to an isosceles triangle shape, the two sides sandwiching the apex are convex on the inner peripheral side, the two sides sandwiching the apex are convex on the outer peripheral side, Furthermore, it means that the cross-sectional shape includes a semicircular shape and a combination of these.
- the present inventors have previously proposed an ejector to be applied to an ejector-type refrigeration cycle in Japanese Patent Application No. 2012-184950 (hereinafter referred to as the prior application example).
- the ejector is a swirling space in which the refrigerant flowing out of the radiator swirls, a decompression space in which the refrigerant flowing out of the swirling space is depressurized, and a refrigerant flowing out of the evaporator through the refrigerant flow downstream of the decompression space is sucked
- a body having a pressure increasing space in which the pressure of the injection refrigerant injected from the decompression space and the suction refrigerant sucked from the suction passage is increased.
- the ejector further includes a passage forming member that is disposed at least in the decompression space and in the pressurization space and has a conical shape whose cross-sectional area increases as the distance from the decompression space increases.
- the decompression space has a nozzle passage that functions as a nozzle that decompresses and injects the refrigerant that has flowed out of the swirl space between the inner peripheral surface of the body and the outer peripheral surface of the passage forming member.
- the pressurizing space has a diffuser passage functioning as a diffuser for boosting the mixed refrigerant of the injected refrigerant and the suction refrigerant between the inner peripheral surface of the body and the outer peripheral surface of the passage forming member.
- the ejector includes a driving device that changes the refrigerant passage cross-sectional area of the nozzle passage by displacing the passage forming member.
- the refrigerant pressure on the turning center side in the swirling space is reduced to the pressure that becomes the saturated liquid phase refrigerant or the pressure at which the refrigerant boils at a reduced pressure (causes cavitation). Can be reduced.
- the gas phase refrigerant is present in the swirl space in the vicinity of the swirl center line so that the gas phase refrigerant is present more on the inner circumference side than the outer circumference side of the swirl center axis, and the liquid single phase is around the gas phase. It can be.
- the refrigerant in the two-phase separation state flows into the nozzle passage, and the boiling is promoted by wall surface boiling and interface boiling, so that the gas phase and the liquid phase are homogeneously mixed in the vicinity of the minimum flow path area of the nozzle passage. It becomes a gas-liquid mixed state. Further, the refrigerant in the gas-liquid mixed state in the vicinity of the minimum flow path area of the nozzle passage is blocked (choking), and the refrigerant is accelerated until the flow rate of the refrigerant in the gas-liquid mixed state becomes a two-phase sound speed.
- the refrigerant accelerated to the two-phase sonic velocity becomes an ideal two-phase spray flow that is homogeneously mixed downstream from the minimum flow path area of the nozzle passage, and can further increase the flow velocity. it can.
- the energy conversion efficiency equivalent to nozzle efficiency
- when converting the pressure energy of the refrigerant into kinetic energy in the nozzle passage can be improved.
- a conical shape is adopted as the passage forming member, and the shape of the diffuser passage is formed so as to expand along the outer periphery of the passage forming member as the distance from the decompression space increases.
- the ejector of the prior application example is provided with a drive device, the refrigerant passage cross-sectional area of the nozzle passage can be appropriately adjusted according to the load fluctuation of the ejector refrigeration cycle. Therefore, according to the ejector of the prior application example, it is possible to suppress a decrease in energy conversion efficiency (corresponding to nozzle efficiency) in the nozzle passage even if the load fluctuation of the ejector type refrigeration cycle occurs without increasing the size of the physique. Can do.
- the present inventors have studied the ejector of the prior application example in order to further improve the energy conversion efficiency of the ejector.
- the decrease in the energy conversion efficiency in the nozzle passage is suppressed.
- the energy conversion efficiency (ejector efficiency) of the ejector as a whole may be lower than a desired value.
- the present inventors investigated the cause, and in the ejector of the prior application example, since the refrigerant passage is formed on the outer peripheral side of the conical passage forming member, it is parallel to the axial direction of the passage forming member.
- the flow direction of the main flow of the injection refrigerant injected from the nozzle passage and the flow direction of the main flow of the suction refrigerant joining the injection refrigerant intersect at a relatively large angle (specifically, 60 ° or more). was found to be the cause.
- the injected refrigerant flows along the outer peripheral side surface of the passage forming member, so that the suction refrigerant that merges with the injected refrigerant also runs along the outer peripheral side surface of the passage forming member.
- a guide member (guide member) or the like that guides to flow can be added.
- such a guide member is formed in a shape that extends to the outer peripheral side along the outer peripheral side surface of the passage forming member, and is disposed between the outlet side of the nozzle passage and the outlet side of the suction passage, As a whole, the ejector may increase the size of the passage forming member in the radial direction. Furthermore, when a body is configured by combining a plurality of constituent members as in the ejector of the prior application, the assembly of the body may be deteriorated by adding a guide member.
- the angle of expansion of the passage forming member in the cross section parallel to the axial direction of the passage forming member is reduced and injection is performed.
- Both the main flow direction of the refrigerant and the main flow direction of the suction refrigerant may be close to the axial direction of the passage forming member.
- the energy conversion efficiency in the nozzle passage is improved by allowing the refrigerant in the two-phase separation state on the swirling center side of the swirling space to flow into the nozzle passage.
- a nozzle passage must be formed on the outer peripheral side of the tip.
- the ejector 13 of the present embodiment is applied to a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression apparatus, that is, an ejector refrigeration cycle 10. Furthermore, this ejector-type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior that is a space to be air-conditioned.
- the ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure.
- an HFO refrigerant specifically, 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.
- a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or adjusting the refrigerant discharge capacity by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch.
- a fixed capacity compressor can be employed.
- the refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port 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 in which the rotation speed (the 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 decompression device that decompresses the supercooled high-pressure liquid-phase refrigerant that has flowed out of the radiator 12 and causes the refrigerant to flow downstream, and is also described later by the suction action of the refrigerant flow injected at a high speed. It functions as a refrigerant circulation device (refrigerant transport device) that sucks (transports) and circulates the refrigerant that has flowed out of the evaporator 14. 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. 1 and 2 are schematic cross-sectional views for explaining the functions of the refrigerant passages of the ejector 13, and the same reference numerals are given to the portions that perform the same functions as those in FIG. .
- 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 interior, a refrigerant suction port 31 b that sucks the refrigerant flowing out of the evaporator 14, and a gas-liquid separation space formed inside the body 30.
- the liquid-phase refrigerant outlet 31c that causes the liquid-phase refrigerant separated in 30f to flow out to the refrigerant inlet side of the evaporator 14 and the gas-phase refrigerant separated in the gas-liquid separation space 30f flow out to the suction side of the compressor 11.
- the gas-phase refrigerant outlet 31d to be made is formed.
- the nozzle body 32 is formed of a substantially conical metal member or the like tapering in the refrigerant flow direction, and is press-fitted into the housing body 31 so that the axial direction is parallel to the vertical direction (vertical direction in FIG. 2). It is fixed by the method. Between the upper side of the nozzle body 32 and the housing body 31, a swirling space 30a for swirling the refrigerant flowing from the refrigerant inlet 31a is formed.
- the swirling space 30a is formed in a rotating body shape, and a central axis K indicated by a one-dot chain line in FIG. 2 extends in the vertical direction.
- the rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (central axis) on the same plane. More specifically, the swirl space 30a of the present embodiment is formed in a substantially cylindrical shape. Of course, you may form in the shape etc. which combined the cone or the truncated cone, and the cylinder.
- the refrigerant inflow passage 31e that connects the refrigerant inlet 31a and the swirl space 30a is formed on the inner peripheral wall surface of the body 30 that forms the swirl space 30a when viewed from the central axis K direction of the swirl space 30a. It extends in the tangential direction. Thereby, the refrigerant that has flowed into the swirl space 30a from the refrigerant inflow passage 31e flows along the inner peripheral wall surface of the part of the body 30 that forms the swirl space 30a, and swirls within the swirl space 30a.
- the refrigerant inflow passage 31e does not have to be formed so as to completely coincide with the tangential direction of the swirl space 30a when viewed from the direction of the central axis K of the swirl space 30a, and at least the tangential direction of the swirl space 30a.
- a component in another direction for example, a component in the axial direction of the swirling space 30a may be included.
- the refrigerant pressure on the central axis K side is lower than the refrigerant pressure on the outer peripheral side in the swirling space 30a. Therefore, in the present embodiment, during normal operation of the ejector refrigeration cycle 10, the refrigerant pressure on the central axis K side in the swirling space 30a is set to the pressure that becomes a saturated liquid phase refrigerant, or the refrigerant boils under reduced pressure (cavitating cavitation). ) Reduce to pressure.
- Such adjustment of the refrigerant pressure on the central axis K side in the swirling space 30a can be realized by adjusting the swirling flow velocity of the refrigerant swirling in the swirling space 30a.
- the swirl flow rate can be adjusted by adjusting the area ratio between the passage sectional area of the refrigerant inflow passage 31e and the vertical sectional area in the axial direction of the swirling space 30a, for example.
- 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 30a.
- a decompression space 30b is formed in which the refrigerant that has flowed out of the swirling space 30a is decompressed and flows downstream.
- the decompression space 30b is formed in a rotating body shape in which a cylindrical space and a frustoconical space that continuously spreads from the lower side of the cylindrical space and gradually expands in the refrigerant flow direction.
- the working space 30b is arranged coaxially with respect to the swirling space 30a and the central axis K.
- a minimum passage area portion 30m having the smallest refrigerant passage sectional area is formed in the decompression space 30b, and a passage forming member that changes the passage sectional area of the minimum passage area portion 30m. 35 is arranged.
- the passage forming member 35 is formed in a substantially conical shape that gradually spreads toward the downstream side of the refrigerant flow, and is disposed coaxially with the decompression space 30b and the central axis K. In other words, the passage forming member 35 is formed in a conical shape whose cross-sectional area increases as the distance from the decompression space 30b increases.
- a taper 131 is formed on the downstream side of the refrigerant flow from the minimum passage area portion 30m, and a tapered portion 131 in which the refrigerant passage cross-sectional area from the portion 30m to the minimum passage area portion 30m is gradually reduced.
- a divergent portion 132 is formed in which the passage cross-sectional area gradually increases.
- 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 circular. It becomes an annular shape (a donut shape excluding a small-diameter circular shape arranged coaxially from a large-diameter circular shape).
- the decompression space 30b has a nozzle passage 13a that functions as a nozzle between the inner peripheral surface of the nozzle body 32 and the outer peripheral surface on the top side of the passage forming member 35. Further, in the nozzle passage 13a, the refrigerant is decompressed, and the flow rate of the refrigerant in the gas-liquid two-phase state is increased so as to be higher than the two-phase sound velocity, and is injected.
- the refrigerant passage formed between the inner peripheral surface of the decompression space 30b and the outer peripheral surface on the top side of the passage forming member 35 in this embodiment is the outer periphery of the passage forming member 35 as shown in FIG.
- This is a refrigerant passage formed so as to include a range where a line segment extending in the normal direction from the surface intersects a portion of the nozzle body 32 forming the decompression space 30b.
- the refrigerant flowing into the nozzle passage 13a swirls in the swirling space 30a
- the refrigerant flowing through the nozzle passage 13a and the jet refrigerant injected from the nozzle passage 13a are the same as the refrigerant swirling in the swirling space 30a. It has a velocity component in the direction of turning in the direction.
- the middle body 33 is provided with a rotating body-shaped through hole penetrating the front and back at the center thereof, and the passage forming member 35 is axially disposed on the outer peripheral side of the through hole. It is formed of a metal disk-shaped member that houses a drive device 37 to be displaced.
- the through hole of the middle body 33 is arranged coaxially with respect to the turning space 30a and the decompression space 30b and the central axis K.
- the middle body 33 is fixed inside the housing body 31 and below the nozzle body 32 by a method such as press fitting.
- 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 opposite to the middle body 33 for retaining the refrigerant flowing in from the refrigerant suction port 31b.
- the inflow space 30c is viewed from the direction of the central axis K of the swirl space 30a and the decompression space 30b.
- the cross section is formed in an annular shape.
- 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 K direction of the inflow space 30c.
- the refrigerant that has flowed into the inflow space 30c from the refrigerant suction port 31b via the suction refrigerant inflow passage is swirled in the same direction as the refrigerant in the swirling space 30a.
- the tapered tip 32a of the nozzle body 32 is formed.
- the refrigerant passage cross-sectional area gradually decreases in the refrigerant flow direction so as to conform to the outer peripheral shape of the refrigerant.
- a suction passage 30d is provided between the inner peripheral surface of the through hole and the outer peripheral surface of the tapered tip portion 32a on the lower side of the nozzle body 32 so as to communicate the inflow space 30c and the refrigerant flow downstream side of the decompression space 30b. It is formed. That is, in this embodiment, the suction passage 13b for sucking the refrigerant from the outside is formed by the suction refrigerant inflow passage connecting the refrigerant suction port 31b and the inflow space 30c, the inflow space 30c, and the suction passage 30d.
- the cross section perpendicular to the central axis K of the suction passage 30d is also formed in an annular shape, and the refrigerant flowing through the suction passage 30d also has a speed component in the direction swirling in the same direction as the refrigerant swirling in the swirling space 30a.
- the refrigerant outlet of the suction passage 13b (specifically, the refrigerant outlet of the suction passage 30d) opens in an annular shape on the outer peripheral side of the refrigerant outlet (refrigerant injection port) of the nozzle passage 13a.
- a mixing space 30h formed in a substantially cylindrical shape or a substantially truncated cone shape is formed on the downstream side of the refrigerant flow in the suction passage 30d.
- the mixing space 30h includes an injection refrigerant injected from the above-described decompression space 30b (specifically, the nozzle passage 13a) and a suction refrigerant sucked from the suction passage 13b (specifically, the suction passage 30d). It is a space that joins.
- the intermediate portion in the vertical direction of the passage forming member 35 described above is disposed, and as shown in FIGS. 3 and 4, the mixing space 30h is formed in the through hole of the middle body 33.
- the refrigerant passage formed between the inner peripheral surface of the part and the outer peripheral surface of the passage forming member 35 constitutes a mixing passage 13d that promotes mixing of the injected refrigerant and the suction refrigerant.
- the refrigerant passage formed between the inner peripheral surface of the mixing space 30h and the outer peripheral surface of the passage forming member 35 in this embodiment is a method from the outer peripheral surface of the passage forming member 35 as shown in FIG.
- a line segment extending in the linear direction is a refrigerant passage formed to include a range where the middle body 33 intersects with a portion forming the mixing space 30h.
- the shapes of the nozzle passage 13a, the suction passage 13b, and the mixing passage 13d will be described with reference to FIG.
- the outer peripheral surface defining the nozzle passage 13a in the passage forming member 35 is a distance from the central axis K toward the downstream side of the refrigerant flow.
- the curved surface has a gradually increasing rate of L.
- the passage forming member 35 in the cross section parallel to the axial direction of the passage forming member 35, is a nozzle when the passage forming member 35 is displaced toward the upper side in the axial direction, that is, toward the swirling space 30 a.
- the passage 13a has a contact portion C2 that contacts the nozzle body 32.
- ⁇ 2 an angle formed by the tangent line Ld2 and the central axis K at the contact portion C2 on the side sandwiching the passage forming member 35 at an acute angle. That is, an acute angle between the tangent line Ld2 and the central axis K at the contact portion C2 is defined as ⁇ 2.
- the passage forming member 35 has a nozzle outlet portion C3 that partitions the outlet of the nozzle passage 13a.
- the nozzle outlet portion C3 is provided in a region corresponding to the displaceable range of the passage forming member 35 on the outer peripheral surface of the passage forming member 35.
- An angle formed by the tangent line Ld3 and the central axis K at the nozzle outlet portion C3 on the side sandwiching the passage forming member 35 at an acute angle is defined as ⁇ 3. That is, an acute angle between the tangent line Ld3 and the central axis K at the nozzle outlet portion C3 is defined as ⁇ 3.
- the angles ⁇ 2 and ⁇ 3 are set to satisfy the following formula F1.
- the angle obtained by doubling ⁇ 2 corresponds to the spread angle on the inlet side of the nozzle passage 13a in the passage forming member 35
- the angle obtained by doubling ⁇ 3 is This corresponds to the spread angle on the outlet side of the nozzle passage 13a in the passage forming member 35.
- the spread angle of the portion forming the outlet side of the nozzle passage 13a of the passage forming member 35 becomes smaller than the spread angle of the portion forming the inlet side of the nozzle passage 13a. Therefore, in this embodiment, the value of ⁇ 3 is set to a relatively small value (15 ° or less in this embodiment), and the flow direction of the main flow of the injected refrigerant flowing from the nozzle passage 13a to the mixing passage 13d is the vertical direction. Nozzle passage 13a is formed so as to approach.
- the suction passage 13 b has an outlet outside the outlet of the nozzle passage 13 a in the radial direction of the passage forming member 35.
- the middle body 33 has a suction outlet portion C1 that defines a radially outer side of the outlet of the suction passage 13b (specifically, the suction passage 30d) in a cross section parallel to the axial direction of the passage forming member 35.
- the tangent line Ls at the suction outlet part C1 is sandwiched between the tangent line Ld3 and the tangent line Ls that sandwich the tapered tip end part (part that defines the radially inner side of the outlet of the suction passage 13b) 32a.
- ⁇ 1 is set so as to satisfy the following formula F2.
- ⁇ 1 ⁇ ⁇ 2 / 2 (F2) As is apparent from FIG. 4, as ⁇ 1 decreases, the tangent line Ld3 and the tangent line Ls on the outer peripheral side of the outlet of the suction passage 13b come closer to parallel. Therefore, in this embodiment, the value of ⁇ 1 is set to a relatively small value (30 ° or less in this embodiment), and the flow direction of the main flow of the suction refrigerant flowing from the suction passage 13b to the mixing passage 13d is vertical. A suction passage 13b is formed so as to approach the direction.
- the mixing passage 13d is formed in a shape in which the passage cross-sectional area gradually decreases toward the downstream side of the refrigerant flow.
- the passage cross-sectional area of the mixing passage 13d is a line segment extending in the normal direction from the outer peripheral surface of the passage forming member 35 to the inner peripheral surface of the mixing space 30h of the middle body 33 is rotated around the axis. It can be defined as the area of the outer peripheral side surface of the truncated cone shape formed at the time.
- “toward the refrigerant flow downstream” means “from the upper side toward the downstream side along the outer peripheral surface of the passage forming member 35 in the cross section parallel to the axial direction of the passage forming member 35”. Can be defined.
- the axial vertical cross-sectional shape of the mixing passage 13d is also formed in an annular shape, and the refrigerant flowing through the mixing passage 13d is also from the speed component in the swirling direction of the injection refrigerant injected from the nozzle passage 13a and the suction passage 13b.
- the speed component in the swirling direction of the sucked suction refrigerant has a speed component in the direction swirling in the same direction as the refrigerant swirling in the swirling space 30a.
- the pressure increasing space 30 e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction on the downstream side of the refrigerant flow in the mixing passage space. Is formed.
- the pressurizing space 30e is a space into which the refrigerant that has flowed out of the mixing space 30h (specifically, the mixing passage 13d) flows.
- the lower part of the above-described passage forming member 35 is disposed inside the pressurizing space 30e. 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 refrigerant gradually expands toward the downstream side of the refrigerant flow.
- a diffuser passage 13c functioning as a diffuser is provided.
- the kinetic energy of the mixed refrigerant mixed in the mixing passage 13d is converted into pressure energy.
- the axial vertical cross-sectional shape of the diffuser passage 13c is also formed in an annular shape, and the refrigerant flowing through the diffuser passage 13c is also from the speed component in the swirling direction of the injection refrigerant injected from the nozzle passage 13a and the suction passage 13b.
- the speed component in the swirling direction of the sucked suction refrigerant has a speed component in the direction swirling in the same direction as the refrigerant swirling in the swirling space 30a.
- 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 37a is fixed by a method such as welding 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 enclosure space 37b via the lid member 37d and the diaphragm 37a that partition the inflow space 30c and the enclosure 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 driving device 37 is a position where it overlaps with the suction passage 13b and the diffuser passage 13c when viewed from the central axis K direction of the swivel space 30a, 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.
- 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).
- a columnar actuating rod 37e is joined to the center portion of the diaphragm 37a by a method such as welding, and the outer peripheral side of the lowermost side (bottom) of the passage forming member 35 is fixed to the lower end side of the actuating rod 37e.
- 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 sectional area of the nozzle passage 13a (passage sectional area in the minimum passage area portion 30m) is adjusted. Is done.
- 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 of (specifically, two) cylindrical spaces are provided on the outer peripheral side of the middle body 33, and a circular thin plate-like diaphragm 37a is fixed inside each of these spaces to drive two drives.
- the apparatus 37 is comprised, the number of the drive apparatuses 37 is not limited to this.
- a diaphragm formed by an annular thin plate may be fixed in a space formed in an annular shape when viewed from the axial direction, and the diaphragm and the passage forming member 35 may be connected by a plurality of operating rods. Good.
- the lower body 34 is formed of a cylindrical metal member or the like, and is fixed in the housing body 31 by a method such as screwing so as to close the bottom surface of the housing body 31.
- a gas-liquid separation space 30f is formed between the upper surface side of the lower body 34 and the bottom surface side of the middle body 33 to separate the gas and liquid of the refrigerant flowing out from the diffuser passage 13c.
- the gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space, and the gas-liquid separation space 30f is also coaxial with the swirl space 30a, the decompression space 30b, the passage forming member 35, and the like with respect to the central axis K. Is placed on top.
- the refrigerant flowing out of the diffuser passage 13c and flowing into the gas-liquid separation space 30f has a velocity component in the direction of turning in the same direction as the refrigerant swirling in the swirling space 30a. 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.
- separated in the gas-liquid separation space 30f is stored by the outer peripheral side of the pipe 34a.
- a gas phase refrigerant outflow passage 34b that guides the gas phase refrigerant separated in the gas-liquid separation space 30f to the gas phase refrigerant outlet 31d is formed inside the pipe 34a.
- 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 cross-sectional area in the minimum passage area 30m of the decompression space 30b is adjusted such that the degree of superheat of the evaporator 14 outlet side refrigerant 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. Furthermore, the refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b and the like flow into the mixing passage 13d and are mixed (points c5 ⁇ d5, h5 in FIG. 5 ⁇ d5 points).
- the mixed refrigerant mixed in the mixing passage 13d flows into the diffuser passage 13c.
- the kinetic energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage cross-sectional 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 is increased in the diffuser passage 13c is sucked into the compressor 11, the driving power of the compressor 11 can be reduced and the cycle efficiency (COP) can be improved. .
- the refrigerant pressure on the swivel center side in the swirl space 30a is reduced to the pressure that becomes a saturated liquid phase refrigerant, or the refrigerant is depressurized.
- the pressure can be reduced to boiling (causing cavitation).
- a larger amount of gas-phase refrigerant is present on the inner peripheral side than the outer peripheral side of the swivel center axis K, so that the vicinity of the swirl center line in the swirl space 30a is a gas single phase and the surroundings are two phases of a liquid single phase. It can be in a separated state.
- the tip 131 of the nozzle passage 13a has a wall surface boiling that occurs when the refrigerant is separated from the outer peripheral side wall surface of the annular refrigerant passage. Boiling of the refrigerant is promoted by interfacial boiling by the boiling nuclei generated by the cavitation of the refrigerant on the central axis K side of the annular refrigerant passage. As a result, the refrigerant flowing into the minimum passage area 30m of the nozzle passage 13a approaches a gas-liquid mixed state in which the gas phase and the liquid phase are uniformly mixed.
- the flow of refrigerant in the gas-liquid mixed state is choked in the vicinity of the minimum passage area portion 30m, and the gas-liquid mixed state refrigerant that has reached the speed of sound by this choking is accelerated by the divergent portion 132 and injected.
- the energy conversion efficiency (equivalent to nozzle efficiency) in the nozzle passage 13a is improved by efficiently accelerating the refrigerant in the gas-liquid mixed state to the sound speed by promoting boiling by both wall surface boiling and interface boiling. Can do.
- the passage forming member 35 is formed in a conical shape in which the cross-sectional area increases with distance from the decompression space 30b, and the cross-sectional shape of the diffuser passage 13c is annular. Therefore, the shape of the diffuser passage 13c can be made to expand along the outer periphery of the passage forming member 35 as the distance from the decompression space 30b increases.
- the passage forming member 35 is displaced according to the load fluctuation of the ejector refrigeration cycle 10, and the refrigerant passage of the nozzle passage 13a and the diffuser passage 13c.
- the cross-sectional area can be adjusted. Therefore, the ejector 13 can be appropriately operated in accordance with the load fluctuation of the ejector refrigeration cycle 10.
- the injection refrigerant injected from the nozzle passage 13 a is on the outer peripheral side of the passage forming member 35. Flowing along.
- the refrigerant passage sectional area of the nozzle passage 13a is adjusted appropriately.
- the spread angle in the cross section parallel to the axial direction of the passage forming member 35 needs to be set relatively large (for example, 60 ° or more).
- the passage forming member 35 is formed in a conical shape in which the cross-sectional shape parallel to the axial direction is a simple isosceles triangle, the main flow of the injected refrigerant flowing out from the nozzle passage 13a and flowing into the mixing passage 13d
- the intersection angle between the flow direction and the main flow direction of the suction refrigerant flowing out of the suction passage 13b and flowing into the mixing passage 13d tends to increase.
- the energy loss (mixing loss) when the injection refrigerant and the suction refrigerant merge is increased. Since the kinetic energy of the mixed refrigerant that is converted into pressure energy in the diffuser passage is reduced, the ejector efficiency is lowered.
- ⁇ 2 and ⁇ 3 are set so as to satisfy the above-described numerical formula F1, and therefore, in the cross section parallel to the axial direction of the passage forming member 35, the passage forming member 35, the expansion angle of the part forming the outlet side of the nozzle passage 13a (corresponding to ⁇ 3 ⁇ 2 in FIG. 4), and the expansion angle of the part of the passage forming member 35 forming the inlet side of the nozzle passage 13a (FIG. 4). (Corresponding to ⁇ 2 ⁇ 2).
- the expansion angle of the portion of the passage forming member 35 that forms the outlet side of the nozzle passage 13a can be set small regardless of the expansion angle of the portion that forms the inlet side of the nozzle passage 13a.
- the flow direction of the main flow of the injection refrigerant injected from the nozzle passage 13a can be made closer to the axial direction of the passage forming member 35.
- the intersection angle between the main flow direction of the injection refrigerant and the main flow direction of the suction refrigerant is changed. Can be small. Therefore, energy loss (mixing loss) when the injection refrigerant and the suction refrigerant merge can be suppressed, and a decrease in ejector efficiency can be suppressed.
- the tapered tip end portion 32a of the nozzle body 32 functioning as a guide portion for bringing the main flow direction of the suction refrigerant closer to the axial direction can be shaped to extend in the axial direction. It is not necessary to form a shape that expands in the radial direction. Accordingly, it is possible to suppress an increase in the size of the passage forming member 35 in the radial direction as the entire ejector 13.
- the passage forming member 35 In the cross section parallel to the axial direction of the passage forming member 35, even if the expansion angle of the portion forming the outlet side of the nozzle passage 13a in the passage forming member 35 is set to a relatively small value, the passage forming member 35 Of these, the spread angle of the portion forming the inlet side of the nozzle passage 13a can be set to an appropriate value. Therefore, it is possible to suppress the change degree of the refrigerant passage cross-sectional area on the inlet side of the nozzle passage 13a from being reduced with respect to the displacement amount (stroke amount) of the passage forming member 35.
- the main flow direction and suction of the injected refrigerant are not caused without increasing the size of the physique.
- the flow direction of the main flow of the refrigerant can be brought close to each other, energy loss when the injected refrigerant and the suction refrigerant merge can be suppressed, and a decrease in ejector efficiency can be suppressed.
- ⁇ 1 is set so as to satisfy the above-described mathematical formula F2, and therefore, it is possible to effectively suppress a decrease in ejector efficiency.
- ⁇ 1 becomes larger than ⁇ 2 / 2
- ⁇ 1 is 0 ° (that is, the flow direction of the main flow of the injection refrigerant and the flow of the main flow of the suction refrigerant). It has been confirmed that the ejector efficiency is reduced by 24% or more with respect to the case where the directions are substantially parallel.
- the mixing passage 13d is formed in a shape in which the passage cross-sectional area gradually decreases toward the downstream side of the refrigerant flow, the injected refrigerant flowing into the mixing passage 13d and The mixed refrigerant with the suction refrigerant can be accelerated. Thereby, in the mixing passage 13d, the pressure of the mixed refrigerant can be gradually decreased toward the outlet side.
- the flow of the injected refrigerant forms the mixing space 30h in the outer peripheral surface side of the passage forming member 35 and the middle body 33. It can suppress drifting to the internal peripheral surface side of a site
- the droplets in the injection refrigerant, the gas phase refrigerant in the injection refrigerant, and the suction refrigerant (gas phase refrigerant) can be sufficiently mixed. And the velocity energy which the droplet in an injection refrigerant
- the pressure on the outlet side of the mixing passage 13d is reduced even if the mixing passage 13d is formed in a shape having a constant passage sectional area toward the downstream side of the refrigerant flow. It has been found that droplets in the injection refrigerant, gas phase refrigerant in the injection refrigerant, and suction refrigerant (gas phase refrigerant) can be sufficiently mixed in the mixing passage 13d.
- 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 speed component in the swirling direction, so that the refrigerant swirls in the gas-liquid separation space 30f. It is not necessary to provide a space for generating a 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.
- thermowax that changes in volume depending on temperature
- a drive device that includes a shape memory alloy elastic member may be used as the drive device.
- a device that displaces the passage forming member 35 by an electric mechanism such as an electric motor or a solenoid may be employed.
- a decompression device for example, a side formed of an orifice or a capillary tube that decompresses the refrigerant at the liquid-phase refrigerant outlet 31c.
- a fixed aperture may be arranged.
- 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 / hot storage, a cooling / heating device for a vending machine, and the like.
- the radiator 12 is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air
- the evaporator 14 is used as a use-side heat exchanger that cools the blown air.
- the ejector of the present disclosure is configured as a heat pump cycle in which the evaporator 14 is configured as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 is configured as an indoor heat exchanger that heats a heated fluid such as air or water. 13 may be applied.
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Abstract
Description
なお、通路形成部材35の軸方向に平行な断面において、θ2を2倍した角度は、通路形成部材35のうちノズル通路13aの入口側の拡がり角度に相当し、θ3を2倍した角度は、通路形成部材35のうちノズル通路13aの出口側の拡がり角度に相当する。
なお、図4から明らかなように、θ1が小さくなるに伴って、接線Ld3と吸引用通路13bの出口の外周側における接線Lsが平行に近づくことになる。そこで、本実施形態では、θ1の値を比較的小さな値(本実施形態では、30°以下)に設定して、吸引用通路13bから混合通路13dへ流入する吸引冷媒の主流の流れ方向が鉛直方向に近づくように、吸引用通路13bを形成している。
Claims (5)
- 蒸気圧縮式の冷凍サイクル装置(10)に用いられるエジェクタであって、
冷媒が導入される冷媒流入口(31a)、前記冷媒流入口から流入した冷媒が旋回する旋回空間(30a)、前記旋回空間(30a)から流出した冷媒が減圧される減圧用空間(30b)、前記減圧用空間(30b)の冷媒流れ下流側に連通して外部から冷媒が吸引される吸引用通路(13b)、前記減圧用空間(30b)から噴射された噴射冷媒と前記吸引用通路(13b)から吸引された吸引冷媒とが流入する昇圧用空間(30e)を有するボデー(30)と、
前記減圧用空間(30b)の内部および前記昇圧用空間(30e)の内部に少なくとも配置されており、前記減圧用空間(30b)から離れるに伴って断面積が拡大する円錐形状を有する通路形成部材(35)と、を備え、
前記減圧用空間(30b)は、前記ボデー(30)の内周面と前記通路形成部材(35)の外周面との間に、前記旋回空間(30a)から流出した冷媒を減圧させて噴射するノズルとして機能するノズル通路(13a)を有し、
前記昇圧用空間(30e)は、前記ボデー(30)の内周面と前記通路形成部材(35)の外周面との間に、前記噴射冷媒と前記吸引冷媒との混合冷媒の運動エネルギを圧力エネルギへ変換するディフューザとして機能するディフューザ通路(13c)を有し、
前記通路形成部材(35)の軸方向に平行な断面において、前記通路形成部材(35)のうち前記ノズル通路(13a)を区画する前記外周面は、冷媒流れ下流側に向かって、前記通路形成部材(35)の中心軸(K)からの距離(L)の増加率が徐々に小さくなる曲面を有し、
前記通路形成部材(35)は、前記通路形成部材(35)の前記軸方向に平行な前記断面において、前記通路形成部材(35)が前記軸方向に変位した際に前記ノズル通路(13a)内でボデー(30)に当接する当接部位(C2)を有し、
前記軸方向に平行な前記断面において、前記当接部位(C2)における接線(Ld2)と前記中心軸(K)との間の鋭角である角度をθ2と定義し、
前記通路形成部材(35)は、前記軸方向に平行な前記断面において、前記ノズル通路(13a)の出口を区画するノズル出口部位(C3)を有し、
前記軸方向に平行な前記断面において、前記ノズル出口部位(C3)における接線(Ld3)と前記中心軸(K)との間の鋭角である角度をθ3と定義し、
前記角度θ2と前記角度θ3は、
θ2≧θ3
の条件を満たしているエジェクタ。 - 前記吸引用通路(13b)は、前記通路形成部材(35)の径方向において、前記ノズル通路(13a)の前記出口の外側に出口を有しており、
前記ボデー(30)は、前記軸方向に平行な前記断面において、前記吸引用通路(13b)の前記出口の前記径方向外側を区画する吸引出口部位(C1)を有し、
前記軸方向に平行な前記断面において、前記ノズル出口部位(C3)における接線(Ld3)と前記吸引出口部位(C1)における接線(Ls)との間の鋭角である角度をθ1と定義し、
前記角度θ1と前記角度θ2は、
θ1≦θ2/2
の条件を満たしている請求項1に記載のエジェクタ。 - 前記通路形成部材(35)を前記軸方向に変位させて、前記ノズル通路(13a)の断面積を変化させる駆動装置(37)を備える請求項1または2に記載のエジェクタ。
- さらに、前記ボデー(30)は、前記噴射冷媒および前記吸引冷媒を合流させる混合用空間(30h)を有しており、
前記混合用空間(30h)は、前記ボデー(30)の内周面と前記通路形成部材(35)の外周面との間に、前記噴射冷媒および前記吸引冷媒が混合し前記ディフューザ通路(13c)へ流入する混合通路(13d)を有する請求項1ないし3のいずれか1つに記載のエジェクタ。 - 前記ノズル出口部位(C3)は、前記通路形成部材(35)の外周面における前記通路形成部材(35)の変位可能範囲に相当する領域に設けられている請求項1ないし4のいずれか1つに記載のエジェクタ。
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CN201480043211.1A CN105431640B (zh) | 2013-08-01 | 2014-07-25 | 喷射器 |
DE112014003507.6T DE112014003507B4 (de) | 2013-08-01 | 2014-07-25 | Ejektor |
US14/908,598 US10330123B2 (en) | 2013-08-01 | 2014-07-25 | Ejector for refrigeration cycle device |
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JP2013-160100 | 2013-08-01 | ||
JP2013160100A JP6048339B2 (ja) | 2013-08-01 | 2013-08-01 | エジェクタ |
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WO2015015783A1 true WO2015015783A1 (ja) | 2015-02-05 |
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US (1) | US10330123B2 (ja) |
JP (1) | JP6048339B2 (ja) |
CN (1) | CN105431640B (ja) |
DE (1) | DE112014003507B4 (ja) |
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Cited By (1)
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US10465957B2 (en) | 2013-08-29 | 2019-11-05 | Denso Corporation | Ejector-type refrigeration cycle, and ejector |
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JP6350108B2 (ja) | 2014-08-21 | 2018-07-04 | 株式会社デンソー | エジェクタ、およびエジェクタ式冷凍サイクル |
WO2016185664A1 (ja) * | 2015-05-19 | 2016-11-24 | 株式会社デンソー | エジェクタ、およびエジェクタ式冷凍サイクル |
JP6399009B2 (ja) * | 2015-05-19 | 2018-10-03 | 株式会社デンソー | エジェクタ、およびエジェクタ式冷凍サイクル |
JP6512071B2 (ja) * | 2015-11-09 | 2019-05-15 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP2017089963A (ja) * | 2015-11-09 | 2017-05-25 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP6481678B2 (ja) | 2016-02-02 | 2019-03-13 | 株式会社デンソー | エジェクタ |
JP6540609B2 (ja) * | 2016-06-06 | 2019-07-10 | 株式会社デンソー | エジェクタ |
CN111912023B (zh) * | 2020-07-16 | 2022-01-21 | 青岛海尔空调器有限总公司 | 立式空调室内机 |
CN111912015B (zh) * | 2020-07-16 | 2021-11-23 | 青岛海尔空调器有限总公司 | 立式空调室内机 |
CN111912018B (zh) * | 2020-07-16 | 2021-11-23 | 青岛海尔空调器有限总公司 | 立式空调室内机 |
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Also Published As
Publication number | Publication date |
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CN105431640B (zh) | 2017-05-31 |
US20160186782A1 (en) | 2016-06-30 |
US10330123B2 (en) | 2019-06-25 |
CN105431640A (zh) | 2016-03-23 |
DE112014003507B4 (de) | 2023-03-30 |
JP2015031184A (ja) | 2015-02-16 |
JP6048339B2 (ja) | 2016-12-21 |
DE112014003507T5 (de) | 2016-04-21 |
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