WO2015019564A1 - エジェクタ - Google Patents
エジェクタ Download PDFInfo
- Publication number
- WO2015019564A1 WO2015019564A1 PCT/JP2014/003890 JP2014003890W WO2015019564A1 WO 2015019564 A1 WO2015019564 A1 WO 2015019564A1 JP 2014003890 W JP2014003890 W JP 2014003890W WO 2015019564 A1 WO2015019564 A1 WO 2015019564A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- space
- passage
- swirling
- ejector
- Prior art date
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Classifications
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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
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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
- F04F5/54—Installations characterised by use of jet pumps, e.g. combinations of two or more jet pumps of different type
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
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- 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
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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
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
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 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
- the present disclosure is an ejector applied to a vapor compression refrigeration cycle apparatus, A swirling space for swirling the refrigerant flowing in from the refrigerant inlet, a depressurizing space for depressurizing the refrigerant flowing out of the swirling space, a suction passage communicating with the refrigerant flow downstream side of the depressurizing space, and sucking the refrigerant from the outside, and depressurizing A body in which a pressurizing space is formed to allow the injected refrigerant injected from the working space and the sucked refrigerant sucked from the suction passage to flow in, and at least a part of the body is disposed in the decompressing space and in the boosting space.
- the refrigerant passage formed between the inner peripheral surface of the part of the body that forms the decompression space and the outer peripheral surface of the passage forming member is a nozzle passage that decompresses and injects the refrigerant flowing out of the swirling space.
- the refrigerant passage formed between the inner peripheral surface of the portion forming the pressurizing space and the outer peripheral surface of the passage forming member is a diffuser that converts the kinetic energy of the mixed refrigerant of the injected refrigerant and the suction refrigerant into pressure energy.
- the swirling space is formed in a rotating body shape that is symmetric about the central axis, and the central axis of the swirling space and the central axis of the passage forming member are coaxially arranged.
- a plurality of drive passages for guiding the refrigerant from the inlet to the swirling space are formed, Further, when viewed from the axial direction of the passage forming member, the refrigerant that has flowed into the swirl space from the plurality of drive passages has a speed component in a direction flowing along the outer periphery of the swirl space, and has a speed component in a direction different from each other.
- the refrigerant flowing into the swirl space from the plurality of drive passages has a velocity component in the direction of flowing along the outer periphery of the swirl space when viewed from the axial direction of the passage forming member.
- the refrigerant that has flowed into the space can be swirled in the swirling space.
- each of the refrigerant that has flowed into the swirl space has velocity components in different directions when viewed from the axial direction of the passage forming member, each of the refrigerant that has flowed into the swirl space has Among the speed components, the speed components in the direction that causes the swirling center of the refrigerant swirling in the swirling space to deviate from the central axis of the swirling space can be configured to cancel each other.
- boiling of the refrigerant in the two-phase separation state can be promoted in the nozzle passage, and energy conversion efficiency (corresponding to nozzle efficiency) when converting the pressure energy of the refrigerant into kinetic energy in the nozzle passage is improved.
- energy conversion efficiency corresponding to nozzle efficiency
- the nozzle efficiency can be sufficiently improved in the ejector that decompresses the refrigerant swirling in the swirling space.
- the refrigerant outlets of the plurality of drive passages are arranged at equiangular intervals around the central axis of the passage forming member. According to this, it can suppress effectively that the turning center of the refrigerant
- the passage forming member is not limited to a member that is formed only from a shape whose cross-sectional area expands as it is strictly separated from the decompression space.
- the passage forming member includes a shape in which the cross-sectional area increases as it moves away from the decompression space, at least partially, so that the shape of the diffuser passage expands outward as it moves away from the decompression space. Including those that can.
- “formed in a conical shape” is not limited to the meaning that the passage forming member is formed in a complete conical shape, and is formed close to a conical shape or partially including a conical shape. It also includes the meaning of being. Specifically, 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 “equal angular interval” does not mean that the angular intervals are strictly equal, and the swirling center of the refrigerant swirling in the swirling space and the central axis of the swirling space are greatly displaced. It is meant to include those that are slightly deviated with respect to an equal angle within a range that can be suppressed.
- FIG. 3 is a cross-sectional view taken along the line III-III in FIG. It is typical sectional drawing for demonstrating the function of each refrigerant path of the ejector of 1st Embodiment.
- FIG. 7 is a sectional view taken along line VII-VII in FIG. 6.
- An ejector applied to an ejector refrigeration cycle A swirling space for swirling the refrigerant flowing out of the radiator, a decompression space for depressurizing the refrigerant flowing out of the swirling space, and a suction passage for sucking the refrigerant flowing out of the evaporator in communication with the refrigerant flow downstream side of the depressurizing space , And a body formed with a pressure increasing space for increasing the pressure by mixing the refrigerant injected from the pressure reducing space and the suction refrigerant sucked from the suction passage; A passage forming member that is at least partially disposed in the decompression space and in the pressurization space, and has a conical shape whose cross-sectional area expands with distance from the decompression space; Nozzle passage functioning as a nozzle in which a refrigerant passage formed between an inner peripheral surface of a
- a diffuser passage in which a refrigerant passage formed between an inner peripheral surface of a portion of the body forming a pressurizing space and an outer peripheral surface of the passage forming member functions as a diffuser for increasing the pressure of the mixed refrigerant of the injected refrigerant and the suction refrigerant.
- 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.
- it is possible to suppress a decrease in energy conversion efficiency (corresponding to nozzle efficiency) when the pressure energy of the refrigerant is converted into kinetic energy in the nozzle passage.
- 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 present inventors have studied the ejector of the prior application example in order to further improve the energy conversion efficiency of the ejector.
- the ejector of the prior application example regarding the decrease in the energy conversion efficiency in the nozzle passage, Although it can be suppressed, this energy conversion efficiency may be lower than a desired value.
- the present inventors investigated the cause, and in the ejector of the prior application example, the central axis of the swirling space formed in the shape of the rotating body and the central axis of the passage forming member are arranged coaxially. Regardless, because it is configured to flow the refrigerant from one direction into the swirling space, the cause is that the swirling center of the refrigerant swirling in the swirling space deviates from the central axis of the swirling space. .
- the following embodiment aims to sufficiently improve the nozzle efficiency in an ejector that depressurizes a refrigerant swirling in a swirling space.
- 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 vapor compression 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 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 so-called subcool type condenser having a condensing unit 12a, a receiver unit 12b, and a supercooling unit 12c.
- the condenser 12a exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d, and radiates and condenses the high-pressure gas-phase refrigerant.
- the receiver unit 12b separates the gas-liquid refrigerant flowing out of the condensing unit 12a and stores excess liquid-phase refrigerant.
- the supercooling unit 12c exchanges heat between the liquid refrigerant flowing out of the receiver unit 12b and the outside air blown from the cooling fan 12d to supercool the liquid 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 flows it downstream.
- the ejector 13 functions as a refrigerant circulation device (refrigerant transport device) that sucks (transports) and circulates refrigerant that has flowed out from the evaporator 14 described later by the suction action of the refrigerant flow injected at a high speed.
- 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.
- FIG. 4 is a schematic cross-sectional view for explaining the function of each refrigerant passage of the ejector 13, and parts having the same functions 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. More specifically, the body 30 includes a housing body 31 that is formed of a prismatic or cylindrical metal or resin as a constituent member and forms the outer shell of the ejector 13. A nozzle body 32, a middle body 33, a lower body 34, an upper cover 36, and the like are fixed to the housing body 31.
- the housing body 31 is formed with a refrigerant inlet 31a, a refrigerant suction port 31b, a liquid phase refrigerant outlet 31c, a gas phase refrigerant outlet 31d, and the like.
- the refrigerant inlet 31a allows the refrigerant that has flowed out of the radiator 12 to flow into the interior.
- the refrigerant suction port 31b sucks the refrigerant that has flowed out of the evaporator 14.
- the liquid-phase refrigerant outlet 31 e allows the liquid-phase refrigerant separated in the gas-liquid separation space 30 f formed inside the body 30 to flow out to the refrigerant inlet side of the evaporator 14.
- the gas-phase refrigerant outlet 31d allows the gas-phase refrigerant separated in the gas-liquid separation space 30f to flow out to the suction side of the compressor 11.
- an upper surface side fixing hole 31e to which the upper cover 36 is inserted and fixed is formed on the upper surface of the housing body 31.
- a bottom surface side fixing hole 31f into which the lower body 34 is inserted and fixed is formed on the bottom surface of the housing body 31.
- the upper cover 36 is a bottomed cylindrical member made of metal or resin.
- the outer peripheral surface of the upper cover 36 is fixed to the upper surface side fixing hole 31e formed in the housing body 31 by press fitting or screwing.
- a nozzle body 32 (described later) formed of a substantially conical metal member tapered in the refrigerant flow direction is fixed to the lower side of the upper cover 36 by press fitting or the like.
- a swirling space 30a for swirling the refrigerant flowing from the refrigerant inlet 31a is formed inside the upper cover 36 and above the nozzle body 32.
- the swirling space 30a is formed in a rotating body shape, and a central axis indicated by a one-dot chain line in FIGS. 2 and 4 extends in the vertical direction (vertical direction).
- the rotating body shape is a three-dimensional shape that is formed when a plane figure is rotated around one straight line (center axis) on the same plane and has a symmetrical shape with the center axis as the center. More specifically, the swirl space 30a of the present embodiment is formed in a substantially cylindrical shape.
- the swirling space 30a may be formed in a shape or the like in which a cone or a truncated cone and a cylinder are combined.
- a groove portion having a rectangular cross section recessed on the inner peripheral side is provided on the cylindrical side surface of the upper cover 36. More specifically, the groove portion is provided in an annular shape over the entire outer periphery of the upper cover 36 when viewed from the axial direction of the upper cover 36. Therefore, when the upper cover 36 is fixed to the housing body 31, an annular space is formed by the groove and the inner peripheral surface of the housing body 31 as shown in the cross-sectional view of FIG. 3.
- the annular space is defined as the distribution space 30g, and the refrigerant inflow passage 31g that connects the refrigerant inlet 31a and the distribution space 30g to the housing body 31 is formed.
- the upper cover 36 is formed with a plurality of (two in this embodiment) drive passages 36a that allow the distribution space 30g and the swirl space 30a to communicate with each other.
- the refrigerant inflow passage 31g extends in the tangential direction of the inner peripheral wall surface of the portion of the housing body 31 that forms the distribution space 30g when viewed from the central axis direction of the swirling space 30a.
- the refrigerant flowing into the distribution space 30g from the refrigerant inflow passage 31g flows along the inner peripheral wall surface of the portion of the body 30 that forms the distribution space 30g, as shown by the thick solid line in FIG. Turn inside.
- the refrigerant flowing into the distribution space 30g is swirled around the central axis of the swirl space 30a, thereby homogenizing the state of the refrigerant in the distribution space 30g.
- the state of the refrigerant being homogenized means that the pressure of the refrigerant in the distribution space 30g is the same in any part, and the state of the refrigerant in the distribution space 30g is the same in any part. ing.
- the refrigerant flowing out of the radiator 12 configured as a subcool condenser is caused to flow into the refrigerant inlet 31a, so that the state of the refrigerant in the distribution space 30g is basically supercooled. It becomes a liquid phase state.
- the two-phase ratio of the refrigerant in the distribution space 30g is made equal by rotating the refrigerant in the distribution space 30g. Can do.
- the distribution space 30g of the present embodiment functions to bring the state of each refrigerant distributed from the distribution space 30g to the plurality of drive passages 36a closer to the same state.
- the state of the refrigerant in the distribution space 30g can be homogenized, it is not necessary to rotate the refrigerant in the distribution space 30g around the axis.
- the plurality of (two in the present embodiment) drive passages 36a have inner peripheries of portions of the upper cover 36 and the nozzle body 32 that form the swirl space 30a when viewed from the central axis direction of the swirl space 30a. It extends in the tangential direction of the wall surface.
- the refrigerant flowing into the swirl space 30a from the refrigerant inflow passage 31g flows along the inner peripheral wall surface of the part of the body 30 that forms the swirl space 30a, as shown by the thick solid line in FIG. Turn inside.
- the refrigerant that has flowed into the swirl space 30a from the respective drive passages 36a has a velocity component in the direction of flowing along the outer periphery of the swirl space 30a.
- the refrigerant outlets (refrigerant outlets) formed on the swirl space 30a side of the respective drive passages 36a are equiangularly spaced from each other around the central axis when viewed from the central axis direction of the swirl space 30a (this embodiment). Then, the openings are opened at intervals of 180 °. Therefore, the refrigerant that has flowed into the swirl space 30a from the plurality of drive passages 36a not only has a speed component in the direction of flowing along the outer periphery of the swirl space 30a, but also has speed components in different directions. . In other words, the inflow direction of the refrigerant when flowing into the swirl space 30a from each drive passage 36a is a direction along the outer periphery of the swirl space 30a and different from each other (in the opposite direction in the present embodiment).
- the plurality of drive passages 36a do not have to be formed so as to completely coincide with the tangential direction of the swirl space 30a when viewed from the central axis direction of the swirl space 30a. If at least the refrigerant flowing into the swirl space 30a from the drive passage 36a has a speed component in the direction of flowing along the outer periphery of the swirl space 30a, the plurality of drive passages 36a have speed components in other directions (for example, swirl The axial component of the space 30a may be included.
- the refrigerant pressure on the central axis 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 side in the swirling space 30a is set to the pressure that becomes the saturated liquid phase refrigerant, or the refrigerant boils under reduced pressure (causes cavitation). The pressure is lowered to the pressure.
- Such adjustment of the refrigerant pressure on the central axis 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 velocity can be adjusted, for example, by adjusting the area ratio between the sum of the cross-sectional areas of the plurality of drive passages 36a and the vertical cross-sectional area of the swirl space 30a.
- 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 central axis of the working space 30b is arranged coaxially with the central axis of the swirling space 30a.
- a minimum passage area portion 30m having the smallest refrigerant passage area in the decompression space 30b, and a passage forming member 35 that changes the passage area of the minimum passage area portion 30m.
- the passage forming member 35 is formed in a substantially conical shape that gradually expands toward the downstream side of the refrigerant flow, and the central axis thereof is arranged coaxially with the central axis of the decompression space 30b.
- 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.
- the divergent part 132 is formed.
- the tapered portion 131 is formed on the upstream side of the refrigerant flow with respect to the minimum passage area portion 30m and gradually reduces the refrigerant passage area until reaching the minimum passage area portion 30m.
- the divergent portion 132 is formed on the downstream side of the refrigerant flow from the minimum passage area portion 30m, and the refrigerant passage 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 outer peripheral surface is formed.
- 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 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 the present 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, 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-shaped member that accommodates the portion 37.
- the central axis of the through hole of the middle body 33 is disposed coaxially with the central axes of the swirling space 30a and the decompression space 30b.
- 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 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 central axis direction of the swirl space 30a and the decompression space 30b. 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.
- 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 area gradually decreases in the refrigerant flow direction so as to match 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 central axis vertical section of the suction passage 30d is also formed in an annular shape, and the refrigerant flowing through the suction passage 30d also has a velocity component in the direction of turning 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 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 pressure increasing space 30e is a space into which the injected refrigerant injected from the pressure reducing space 30b (specifically, the nozzle passage 13a) and the suction refrigerant sucked from the suction passage 13b flow.
- 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 flow gradually expands toward the downstream side.
- the inner peripheral surface of the middle body 33 that forms the pressurizing space 30 e and the outer peripheral surface on the lower side of the passage forming member 35 are formed.
- a refrigerant passage formed between them serves as a diffuser passage 13c that functions as a diffuser. And in this diffuser channel
- coolant 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 unit 37 disposed inside the middle body 33 and displacing the passage forming member 35 will be described.
- the drive unit 37 includes a circular thin plate-shaped diaphragm 37a that 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 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 unit 37 is disposed at a position sandwiched from above and below by the suction passage 13b and the diffuser passage 13c when viewed from the radial direction of the central axis.
- the enclosed space 37b of the drive unit 37 is a position where it overlaps with the suction passage 13b and the diffuser passage 13c when viewed from the central axis direction of the swivel space 30a, the passage forming member 35, etc. It arrange
- 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 cylindrical actuating rod 37e is joined to the center portion of the diaphragm 37a by welding or the like, and the lowermost side (bottom portion) of the passage forming member 35 is fixed to the lower end side of the actuating rod 37e. Yes.
- 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 biases the passage forming member 35 toward the side (the upper side in FIG. 2) that reduces the cross-sectional area of the passage in the minimum passage area 30 m.
- the valve opening pressure of the passage forming member 35 can be changed 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 part 37 is comprised, the number of the drive parts 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 to the bottom surface side fixing hole 31f formed on the bottom surface of the housing body 31 by press-fitting or screwing.
- 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 central axis of the gas-liquid separation space 30f is also the central axis of the swirl space 30a, the decompression space 30b, the passage forming member 35, and the like. And are arranged on the same axis.
- 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 temporarily 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 device 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 device for each control target device.
- operation of the electric motor 11b of the compressor 11 comprises the discharge capability control apparatus.
- 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 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. 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 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).
- the gas phase refrigerant is present in the swirl space 30a in the vicinity of the swirl center line, and the liquid single phase is surrounded by the two-phase separation so that a larger amount of gas-phase refrigerant exists on the inner periphery side than the outer periphery side of the swirl center shaft.
- 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 boiling nuclei generated by cavitation of the refrigerant on the central axis 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 gas-liquid mixed refrigerant can be efficiently accelerated until it reaches the speed of sound, so that the energy conversion efficiency in the nozzle passage 13a (corresponding to the nozzle efficiency of the prior art) is increased. Can be improved.
- the refrigerant flowing into the swirl space 30a from the plurality of drive passages 36a is swirled when viewed from the axial direction of the swirl space 30a (that is, the axial direction of the passage forming member 35). It not only has a velocity component in the direction flowing along the outer periphery of the space 30a, but also has velocity components in different directions.
- the swirl center of the refrigerant swirling in the swirl space 30a is shifted in a direction that causes the center axis of the swirl space 30a to deviate. It can be set as the structure which cancels a speed component mutually. And it can suppress that the turning center of the refrigerant
- the refrigerant outlets of the plurality of drive passages 36a are opened at equal angular intervals around the axis of the passage forming member 35. It can be reliably suppressed that the swirling center of the refrigerant swirling in the swirling space 30a and the central axis of the swirling space 30a are greatly displaced.
- the two-phase separated refrigerant in which the liquid-phase refrigerant is unevenly distributed on the outer peripheral side and the gas-phase refrigerant is unevenly distributed on the inner peripheral side is caused to flow into the nozzle passage 13a formed on the outer peripheral side of the passage forming member 35.
- the boiling of the refrigerant in the two-phase separation state can be promoted in the nozzle passage 13a, and the energy conversion efficiency when converting the pressure energy of the refrigerant into the kinetic energy in the nozzle passage (corresponding to the nozzle efficiency of the prior art) ) Can be sufficiently improved.
- the refrigerant outlets of the plurality of drive passages 36a do not have to be arranged at exactly equal angular intervals, and the turning center of the refrigerant turning in the turning space 30a and the central axis of the turning space 30a are greatly shifted. It suffices if it is arranged within a range where this can be suppressed.
- the ejector 13 of the present embodiment is formed with the distribution space 30g, the states of the respective refrigerants distributed to the respective drive passages 36a can be brought close to the same state. Therefore, the state of the refrigerant flowing into the swirl space 30a from each drive passage 36a is also equivalent, and it is further effective that the swirl center of the refrigerant swirling in the swirl space 30a and the central axis of the swirl space 30a are shifted. Can be suppressed.
- the distribution space 30g is formed by the groove portion formed on the cylindrical side surface of the upper cover 36, so that the distribution space 30g can be easily formed.
- the distribution space 30g is formed in an annular shape on the outer peripheral side of the swivel space 30a, for example, when the upper cover 36 is fixed to the upper surface side fixing hole 31e of the housing body 31, the mounting position of the upper cover 36 is the center. Even if it deviates in the circumferential direction with respect to the shaft, the refrigerant inflow passage 31g and the distribution space 30g can be reliably communicated.
- 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 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 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 the gas-liquid separation device is provided separately from the ejector 13 (second embodiment).
- FIG. 6 an example in which the configuration of the distribution space 30g of the ejector 13 and the drive passage 36a is changed with respect to the first embodiment will be described.
- a disk-shaped cover plate 36b is fixed to the upper surface of the housing body 31 by press-fitting or the like.
- a plurality of grooves recessed downward are formed in the upper surface of the housing body 31 where the cover plate 36b is fixed, as shown in FIGS. Then, the cover plate 36b is press-fitted and fixed, and these groove portions are partitioned to form the distribution space 30g and the plurality of drive passages 36a similar to those in the first embodiment.
- the nozzle body 32 is fixed to the inside of the housing body 31 by press fitting or the like from below.
- Other configurations are the same as those of the first embodiment. Therefore, even if the distribution space 30g and the drive passage 36a are configured like the ejector 13 of the present embodiment, the same effect as that of the first embodiment can be obtained.
- the drive passage 36a is formed by a groove formed on the upper surface of the housing body 31, so that the axial depth dimension of the refrigerant outlet of the drive passage 36a (FIG. 6).
- the width dimension in the vertical direction) can be easily adjusted. Accordingly, the axial depth dimension of the refrigerant outlet of the drive passage 36a is enlarged, and the refrigerant flows from the drive passage 36a into the swirling space 30a from a wide range in the axial direction, so that the swirling flow of the refrigerant in the swirling space 30a. Can be promoted.
- the distribution space 30 g may be formed by a groove formed in a part of the cylindrical side surface of the upper cover 36.
- the refrigerant inflow passage 31g is not limited to a shape extending in the tangential direction of the outer periphery of the distribution space 30g. 8 to 10 correspond to FIG. 3 of the first embodiment.
- the distribution space 30g and the drive passage 36a having the same shape as that of the first embodiment has been described.
- the distribution space 30g and the drive passage 36a are provided.
- the groove to be formed can be formed by performing milling or the like on the upper surface of the housing body 31. Therefore, according to the structure of 2nd Embodiment, the design freedom of the shape of the distribution space 30g and the drive channel
- the drive passage 36a can be curved. Specifically, as long as the refrigerant flowing into the swirl space 30a from the drive passage 36a flows along the outer periphery of the swirl space 30a, the drive passage 36a is moved from the outer periphery side of the swirl space 30a as shown in FIG. It is good also as the shape curved toward the outer periphery tangent side of the turning space 30a.
- a distribution space 30g having a circular cross section or a rectangular cross section is formed, and this distribution space 30g is made to function as a branching portion that branches the flow of the refrigerant flowing in from the refrigerant inlet 31a.
- the refrigerant may be divided from the distribution space 30g to the respective drive passages 36a. That is, the body 30 may be formed with a branch portion that branches the flow of the refrigerant flowing in from the refrigerant inflow port 31a to each drive passage 36a.
- the distribution space 30g may be eliminated, and the refrigerant flowing from the refrigerant inlet 31a may be directly introduced into the respective drive passages 36a. In this case, it is desirable that the refrigerant flowing into each driving passage 36a can be homogenized even if the distribution space 30g is eliminated.
- 11 to 13 correspond to FIG. 7 of the second embodiment.
- the drive unit 37 that displaces the passage forming member 35, the enclosed space 37b in which the temperature-sensitive medium whose pressure changes with temperature change is enclosed, and the pressure of the temperature-sensitive medium in the enclosed space 37b
- the drive unit is not limited to this.
- thermowax that changes in volume depending on temperature
- a drive unit that includes a shape memory alloy elastic member
- a member that displaces the passage forming member 35 by an electric mechanism such as an electric motor or a solenoid may be adopted.
- a decompression device for example, an orifice or a capillary tube side
- 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 evaporator 14 is configured as an outdoor heat exchanger that absorbs heat from a heat source such as outside air
- the radiator 12 is configured as a heat pump cycle configured as an indoor heat exchanger that heats a heated fluid such as air or water.
- the disclosed ejector 13 may be applied.
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Abstract
Description
冷媒流入口から流入した冷媒を旋回させる旋回空間、旋回空間から流出した冷媒を減圧させる減圧用空間、減圧用空間の冷媒流れ下流側に連通して外部から冷媒を吸引する吸引用通路、および減圧用空間から噴射された噴射冷媒と吸引用通路から吸引された吸引冷媒とを流入させる昇圧用空間が形成されたボデーと、少なくとも一部が減圧用空間の内部および昇圧用空間の内部に配置されており、減圧用空間から離れるに伴って断面積が拡大する円錐状に形成された通路形成部材とを備え、
ボデーのうち減圧用空間を形成する部位の内周面と通路形成部材の外周面との間に形成される冷媒通路は、旋回空間から流出した冷媒を減圧させて噴射するノズル通路であり、ボデーのうち昇圧用空間を形成する部位の内周面と通路形成部材の外周面との間に形成される冷媒通路は、噴射冷媒と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通路であり、
旋回空間は、中心軸を中心とした対称形状である回転体形状に形成されており、旋回空間の前記中心軸と通路形成部材の中心軸は同軸上に配置されており、ボデーには、冷媒流入口から旋回空間へ冷媒を導く複数の駆動通路が形成されており、
さらに、通路形成部材の軸方向から見たときに、複数の駆動通路から旋回空間へ流入した冷媒は、旋回空間の外周に沿って流れる方向の速度成分であって、互いに異なる方向の速度成分を有している。
エジェクタ式冷凍サイクルに適用されるエジェクタであって、
放熱器から流出した冷媒を旋回させる旋回空間、この旋回空間から流出した冷媒を減圧させる減圧用空間、減圧用空間の冷媒流れ下流側に連通して蒸発器から流出した冷媒を吸引する吸引用通路、および減圧用空間から噴射された噴射冷媒と吸引用通路から吸引された吸引冷媒とを混合して昇圧させる昇圧用空間が形成されたボデーと、
少なくとも一部が減圧用空間の内部および昇圧用空間の内部に配置されて、減圧用空間から離れるに伴って断面積が拡大する円錐状に形成された通路形成部材とを備え、
ボデーのうち減圧用空間を形成する部位の内周面と通路形成部材の外周面との間に形成される冷媒通路が、旋回空間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を形成し、
ボデーのうち昇圧用空間を形成する部位の内周面と通路形成部材の外周面との間に形成される冷媒通路が、噴射冷媒と吸引冷媒との混合冷媒を昇圧させるディフューザとして機能するディフューザ通路を形成するエジェクタを提案している。
図1~図5を用いて、本開示の第1実施形態を説明する。本実施形態のエジェクタ13は、図1に示すように、冷媒減圧装置としてエジェクタを備える蒸気圧縮式の冷凍サイクル装置、すなわち、エジェクタ式冷凍サイクル10に適用されている。さらに、このエジェクタ式冷凍サイクル10は、車両用空調装置に適用され、空調対象空間である車室内へ送風される送風空気を冷却する機能を果たす。
(第2実施形態)
本実施形態では、図6に示すように、第1実施形態に対して、エジェクタ13の分配空間30gおよび駆動通路36aの構成を変更した例を説明する。具体的には、本実施形態のエジェクタ13では、ハウジングボデー31の上面に、円板状のカバープレート36bが圧入等によって固定されている。
本開示は上述の実施形態に限定されることなく、本開示の趣旨を逸脱しない範囲内で、以下のように種々変形可能である。 (1)上述の実施形態では、駆動通路36aを2つとして、それぞれの駆動通路36aの旋回空間30a側に形成される冷媒出口を、旋回空間30aの中心軸方向から見たときに、180°間隔で開口させた例を説明したが、駆動通路36aの数および配置はこれに限定されない。
Claims (5)
- 蒸気圧縮式の冷凍サイクル装置(10)に適用されるエジェクタであって、
冷媒流入口(31a)から流入した冷媒を旋回させる旋回空間(30a)、前記旋回空間(30a)から流出した冷媒を減圧させる減圧用空間(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を吸引する吸引用通路(13b)、および前記減圧用空間(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を流入させる昇圧用空間(30e)が形成されたボデー(30)と、
少なくとも一部が前記減圧用空間(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状に形成された通路形成部材(35)とを備え、
前記ボデー(30)のうち前記減圧用空間(30b)を形成する部位の内周面と前記通路形成部材(35)の外周面との間に形成される冷媒通路は、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通路(13a)であり、
前記ボデー(30)のうち前記昇圧用空間(30e)を形成する部位の内周面と前記通路形成部材(35)の外周面との間に形成される冷媒通路は、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通路(13c)であり、
前記旋回空間(30a)は、中心軸を中心とした対称形状である回転体形状に形成されており、
前記旋回空間(30a)の前記中心軸と前記通路形成部材(35)の中心軸は同軸上に配置されており、
前記ボデー(30)には、前記冷媒流入口(31a)から前記旋回空間(30a)へ冷媒を導く複数の駆動通路(36a)が形成されており、
前記通路形成部材(35)の軸方向から見たときに、前記複数の駆動通路(36a)から前記旋回空間(30a)へ流入した冷媒は、前記旋回空間(30a)の外周に沿って流れる方向の速度成分であって、互いに異なる方向の速度成分を有しているエジェクタ。 - 前記通路形成部材(35)の軸方向から見たときに、前記複数の駆動通路(36a)の前記旋回空間(30a)への冷媒流出口は、当該旋回空間(30a)の前記中心軸周りに互いに等角度間隔で配置されている請求項1に記載のエジェクタ。
- 前記ボデー(30)には、前記冷媒流入口(31a)から流入した冷媒を前記複数の駆動通路(36a)へ分配する分配空間(30g)が形成されており、
前記分配空間(30g)は、前記分配空間(30g)から前記複数の駆動通路(36a)へ分配されるそれぞれの冷媒の状態を、互いに同等の状態に近づける空間である請求項1または2に記載のエジェクタ。 - 前記通路形成部材(35)の軸方向から見たときに、前記分配空間(30g)は、環状に形成されており、前記旋回空間(30a)の外周側に配置されている請求項3に記載のエジェクタ。
- 前記ボデー(30)として、内部に旋回空間(30a)の少なくとも一部を形成する円筒状部材(36)が設けられており、
前記分配空間(30g)は、前記円筒状部材(36)の筒状側面に形成された溝部によって形成されている請求項3または4に記載のエジェクタ。
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DE112014003680.3T DE112014003680B4 (de) | 2013-08-09 | 2014-07-24 | Ejektor |
US14/910,281 US9816738B2 (en) | 2013-08-09 | 2014-07-24 | Ejector |
CN201480044813.9A CN105492778B (zh) | 2013-08-09 | 2014-07-24 | 喷射器 |
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DE112014003680T5 (de) | 2016-05-12 |
US20160169566A1 (en) | 2016-06-16 |
DE112014003680B4 (de) | 2023-01-19 |
CN105492778B (zh) | 2017-06-27 |
US9816738B2 (en) | 2017-11-14 |
JP2015034672A (ja) | 2015-02-19 |
CN105492778A (zh) | 2016-04-13 |
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