WO2013114856A1 - エジェクタ - Google Patents
エジェクタ Download PDFInfo
- Publication number
- WO2013114856A1 WO2013114856A1 PCT/JP2013/000453 JP2013000453W WO2013114856A1 WO 2013114856 A1 WO2013114856 A1 WO 2013114856A1 JP 2013000453 W JP2013000453 W JP 2013000453W WO 2013114856 A1 WO2013114856 A1 WO 2013114856A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- passage
- space
- diffuser
- pressure
- Prior art date
Links
Images
Classifications
-
- 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
- F04F5/463—Arrangements of nozzles with provisions for mixing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
- F04F5/46—Arrangements of nozzles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F04F5/462—Arrangements of nozzles with provisions for cooling the fluid
-
- 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
- F04F5/50—Control of compressing pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3286—Constructional features
- B60H2001/3298—Ejector-type refrigerant circuits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0014—Ejectors with a high pressure hot primary flow from a compressor discharge
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
Definitions
- the present disclosure relates to an ejector that is a momentum transporting pump that decompresses a fluid and transports the fluid by a suction action of a working fluid ejected at high speed.
- This type of ejector includes a nozzle portion that decompresses the refrigerant condensed and liquefied by the refrigerant condenser after being compressed to a high pressure by a compressor when applied to a refrigeration cycle, and a low-pressure side refrigerant that flows out of the refrigerant evaporator And a diffuser part that mixes the refrigerant sucked from the suction part and the refrigerant sucked from the suction part to increase the pressure.
- the nozzle portion of the ejector of Patent Document 1 ejects the first nozzle that decompresses and expands the liquid refrigerant that has flowed from the refrigerant condenser, and the refrigerant that has become a gas-liquid two-phase by the first nozzle, and decompresses and expands again. And a second nozzle.
- the refrigerant is expanded into a gas-liquid two-phase by the first nozzle and further decompressed and expanded by the second nozzle, so that the outlet speed of the refrigerant flowing out from the second nozzle can be increased, and the nozzle efficiency is improved. It can be made to.
- 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, and 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, the efficiency of the ejector is improved and the diffuser portion can be used even when the refrigeration cycle has a low load.
- the refrigerant may be sufficiently pressurized.
- the length of the nozzle part in the axial direction of the ejector as a whole becomes longer, so that the size of the ejector may become unnecessarily large at the normal load of the refrigeration cycle. is there.
- the first object of the present disclosure is to provide an ejector that can exhibit high nozzle efficiency regardless of load fluctuations in the refrigeration cycle without increasing the size of the physique.
- a second object of the present disclosure is to provide an ejector that can improve the nozzle efficiency and can operate in accordance with the load of the refrigeration cycle.
- an ejector applied to a vapor compression refrigeration cycle which includes a refrigerant inlet into which a refrigerant flows, a swirling space that swirls the refrigerant that flows in from the refrigerant inlet, and an outflow from the swirling space
- the decompression space for decompressing the decompressed refrigerant the suction passage communicating with the refrigerant flow downstream side of the decompression space and sucking the refrigerant from the outside, the injected refrigerant injected from the decompression space, and the suction passage
- a body member having a pressurizing space for mixing and boosting the suction refrigerant is provided.
- the ejector further includes a passage forming member having at least a portion disposed in the decompression space and the boosting space, an inner peripheral surface of a portion of the body member forming the decompression space, and an outer peripheral surface of the passage forming member.
- a nozzle passage that functions as a nozzle portion that decompresses and injects the refrigerant that has flowed out of the swirling space, an inner peripheral surface of a portion of the body member that forms the pressure increasing space, and an outer periphery of the passage forming member
- a diffuser passage that is formed in a space between the surfaces and functions as a diffuser section that mixes and injects the injected refrigerant and the suction refrigerant.
- the passage forming member has a shape whose cross-sectional area expands in a direction away from the decompression space.
- the refrigerant pressure on the swivel center side in the swirl 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).
- the refrigerant whose pressure has been reduced can be caused to flow into the decompression space.
- the refrigerant can be surely boiled in the vicinity of the minimum passage area in the nozzle passage, and the energy conversion efficiency (corresponding to the nozzle efficiency) in the nozzle passage can be improved. it can.
- the cross-sectional area is formed to increase as the passage forming member moves away from the decompression space
- the shape of the diffuser passage expands along the outer periphery of the passage forming member as it moves away from the decompression space. It can be. Therefore, expansion of the dimension of the direction corresponding to the axial direction of a nozzle part can be suppressed, and the enlargement of the physique as the whole ejector can be suppressed.
- the first aspect of the present disclosure it is possible to provide an ejector that can exhibit high nozzle efficiency without causing an increase in the size of the physique and regardless of load fluctuations in the refrigeration cycle.
- the passage forming member is not limited to a member that is strictly formed only from a shape in which the cross-sectional area increases as the distance from the decompression space increases, and the cross-sectional area increases at least partially as the distance from the decompression space increases.
- the shape which expands the shape which can be made into the shape which can be made into the shape which spreads outside as the shape of a diffuser channel
- the passage forming member may have a conical shape whose cross-sectional area increases in a direction away from the decompression space, and the nozzle passage, the suction passage, and the diffuser passage are the shafts of the passage forming member.
- the cross-sectional shape in the cross section perpendicular to the direction may be annular.
- the sectional shape of the nozzle passage, the suction passage and the diffuser passage is formed in an annular shape, the refrigerant flows through these passages from the outer peripheral side of the shaft of the passage forming member to the inner peripheral side, or It can be formed in a shape in which the refrigerant flows from the inner peripheral side to the outer peripheral side. Therefore, passage arrangement that effectively utilizes the internal space of the body member is possible, and the size of the entire ejector can be further prevented from increasing in size.
- the passage forming member may have a conical shape whose cross-sectional area increases in a direction away from the decompression space, and the diffuser passage is annular in a cross section perpendicular to the axial direction of the passage forming member.
- the refrigerant flowing through the diffuser passage may swirl in the same direction as the refrigerant swirling in the swirling space.
- the cross-sectional shape of the diffuser passage is formed in an annular shape, and furthermore, since the refrigerant flowing through the diffuser passage flows while swirling, the flow path for boosting the refrigerant can be formed in a spiral shape. Therefore, the enlargement of the physique as the whole ejector can be further suppressed by suppressing the expansion of the passage forming member in the axial direction.
- a drive unit that displaces the passage forming member may be provided.
- the passage forming member may have a conical shape in which a cross-sectional area increases as the distance from the decompression space increases, and the suction passage and the diffuser passage have an annular cross-sectional shape in a cross section perpendicular to the axial direction of the passage forming member. You may have.
- the suction passage may have a shape in which the refrigerant flows from the outer peripheral side to the inner peripheral side of the shaft of the passage forming member.
- the diffuser passage may have a shape in which the refrigerant flows from the inner peripheral side to the outer peripheral side of the shaft of the passage forming member, and the suction passage and the diffuser passage may be provided along the outer periphery of the drive unit. At least a part of the drive unit may be disposed between the suction passage and the diffuser passage in the axial direction of the passage forming member.
- the passage forming member can be displaced according to the load fluctuation of the refrigeration cycle, and the refrigerant passage areas of the nozzle passage and the diffuser passage can be adjusted. Therefore, it is possible to supply an amount of refrigerant corresponding to the load of the refrigeration cycle, and it is possible to provide an ejector that can operate according to the load of the refrigeration cycle.
- the drive unit since at least a part of the drive unit may be disposed at a position sandwiched between the suction passage and the diffuser passage, the space formed between the suction passage and the diffuser passage can be used effectively. . As a result, the enlargement of the physique as the whole ejector can be further suppressed.
- the term “formed in a conical shape” in the above claims is not limited to the meaning that the passage forming member is formed in a complete conical shape, and a shape close to a cone or a conical shape in part. It also includes the meaning of being formed.
- the axial cross-sectional shape is not limited to an isosceles triangle, but the two sides sandwiching the apex are convex on the inner peripheral side, the two sides are convex on the outer peripheral side, and the cross-sectional shape It is meant to include those having a semicircular shape.
- the drive unit includes a sealed space in which a temperature-sensitive medium whose pressure changes with a temperature change is sealed, and a pressure-responsive member that is displaced according to the pressure of the temperature-sensitive medium in the sealed space.
- the pressure responsive member may be coupled to the passage forming member.
- the temperature-sensitive medium may change in pressure when the temperature of the refrigerant flowing through the suction passage and the temperature of the refrigerant flowing through the diffuser passage are transmitted.
- the enclosed space constituting the drive unit by disposing the enclosed space constituting the drive unit at a position sandwiched between the suction passage and the diffuser passage, the temperature of the refrigerant flowing through the suction passage and the temperature of the refrigerant flowing through the diffuser passage are sensed. It is possible to change the pressure in the enclosed space with good transmission to the warm medium.
- the passage forming member can be displaced according to the temperature of the refrigerant flowing through the suction passage and the temperature of the refrigerant flowing through the diffuser passage, thereby changing the refrigerant passage areas of the nozzle passage and the diffuser passage.
- the decompression space, the suction passage, the pressurization space, and the passage forming member may all have a rotating body shape, and their axes may be arranged coaxially. .
- the pressure reducing space, the suction passage, the pressure increasing space, and the passage forming member formed in the shape of a rotating body are arranged coaxially with each other, the nozzle whose axial vertical cross section is formed in an annular shape
- the passage, the suction passage, and the diffuser passage can be easily formed.
- the body member may have a gas-liquid separation space that separates the gas-liquid of the refrigerant flowing out from the diffuser passage.
- the volume of the gas-liquid separation space is reduced compared to the case where the gas-liquid separation means is arranged outside the body member. can do. That is, since the refrigerant flowing out from the diffuser passage and flowing into the gas-liquid separation space has already swirled, efficient gas-liquid separation can be performed by the action of the centrifugal force of this swirling flow. Therefore, an increase in the size of the ejector having a gas-liquid separation function can be suppressed.
- an ejector is applied to a vapor compression refrigeration cycle, and a low-pressure refrigerant having a pressure lower than that of the high-pressure refrigerant and a nozzle portion that decompresses and expands the high-pressure refrigerant flowing from the high-pressure side of the refrigeration cycle.
- a nozzle having a suction part that sucks by the suction force of the jetted refrigerant ejected from the nozzle part, and an internal channel that is disposed downstream of the nozzle part and whose cross-sectional area gradually expands toward the downstream side
- a diffuser part that decelerates and increases the pressure of the mixed refrigerant in which the refrigerant jetted from the part and the low-pressure refrigerant sucked from the suction part are mixed; and is disposed upstream of the nozzle part to rotate the high-pressure refrigerant.
- the swirling space for allowing the gas-liquid mixed phase refrigerant to flow into the nozzle portion so that a larger amount of gas-phase refrigerant exists on the inner peripheral side than the outer peripheral side of the virtual swirling center line, and the nozzle portion and the diffuser portion The channel area And a surface area varying mechanism to further possible.
- the high-pressure refrigerant is swirled in the swirling space so that more gas phase refrigerant exists on the inner peripheral side than on the outer peripheral side of the swirling center line.
- the vicinity of the swirl center line is in a two-phase separation state of a gas single phase and the surroundings are a liquid single phase. That is, the refrigerant pressure on the turning center side is reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation).
- the flow becomes a two-phase spray state in the vicinity of the minimum flow path area of the nozzle portion, and the two-phase sound speed is reached.
- the refrigerant accelerated to the two-phase sonic velocity can continue an ideal two-phase spray flow from the minimum flow area of the nozzle portion to the outlet of the divergent flow passage, and the flow velocity of the refrigerant injected at the outlet of the divergent flow passage. Can be increased. As a result, the nozzle efficiency of the nozzle portion can be improved and the ejector efficiency can be improved.
- the pressure energy by the diffuser portion can be obtained by utilizing all the pressure energy of the liquid phase refrigerant flowing into the ejector. it can.
- the high-pressure refrigerant may be a liquid-phase refrigerant.
- the high-pressure refrigerant is a liquid phase refrigerant
- the refrigerant is in a swirl flow path as described above, and the vicinity of the swirl center line is in a gas single phase, and the surroundings are in a liquid single phase two-phase separation state.
- the flow from the minimum flow area of the nozzle part to the outlet of the divergent flow part is in a two-phase spray state
- This effect is greater than when the high-pressure refrigerant is a gas-liquid two-phase.
- the area variable mechanism may be capable of simultaneously changing the flow path area between the nozzle part and the diffuser part.
- the flow passage areas of the nozzle portion and the diffuser portion are changed at the same time, so that the flow of the refrigerant flowing through the nozzle portion and the diffuser portion is not disturbed.
- the member that changes the flow path area between the nozzle portion and the diffuser portion can be formed by one member, and the configuration of the area variable mechanism can be simplified.
- the expansion ratio of the flow passage cross-sectional area of the diffuser portion may be set so as to increase sequentially toward the downstream side, and the area variable mechanism is along the inner walls of the nozzle portion and the diffuser portion.
- You may provide the channel
- the internal flow path of the diffuser part provided along the outer peripheral surface of the passage forming member may be provided so as to expand in a direction intersecting the axial direction of the diffuser part.
- the length of the diffuser portion in the axial direction can be reduced, and a compact ejector can be realized.
- the high-pressure refrigerant swirled by the swirling space maintains the swirling state in the nozzle portion and the diffuser portion, and flows out in a direction intersecting the axial direction of the diffuser portion. Therefore, the mixed refrigerant flowing out from the diffuser part is subjected to centrifugal separation by the swirling flow, and the liquid refrigerant having a high density is discharged to the side farther from the axis than the gas refrigerant having a low density. . That is, the ejector itself can have an effective gas-liquid separation function.
- a gas-liquid separator that separates the gas-liquid of the mixed refrigerant flowing out from the diffuser unit may be provided.
- a compact ejector in which the gas-liquid separator is integrally formed can be realized.
- the swirling flow of the refrigerant in the swirling space is also maintained in the nozzle portion and the diffuser portion. Therefore, the mixed refrigerant flowing out from the diffuser part is subjected to centrifugal separation by the swirling flow, and the liquid refrigerant having a high density flows out to the side farther from the axis than the gas refrigerant having a low density.
- the refrigerant separated from the gas-liquid in the diffuser part can immediately flow into the gas-liquid separator, Effective gas-liquid separation can be performed.
- a liquid storage part that stores the refrigerant separated by the gas-liquid separator may be provided, and the liquid storage part may be formed integrally with the gas-liquid separator.
- the refrigeration cycle 10 is mounted on a vehicle for an air conditioner, and includes a compressor 11, a condenser 12, an ejector 100, a gas-liquid separator 13, a liquid storage unit 14, and an evaporator 16, which are refrigerant pipes. Are connected by.
- the operation of the compressor 11 is controlled by a control device (not shown).
- the compressor 11 is a fluid machine that sucks the gas-phase refrigerant in the gas-liquid separator 13, compresses it to high temperature and high pressure, and discharges it to the condenser 12 side.
- the compressor 11 is a vehicle travel engine via an electromagnetic clutch and a belt (not shown). Is driven to rotate.
- the compressor 11 is, for example, a swash plate type variable displacement compressor in which a discharge capacity is changed by inputting a control signal from a control device to an electromagnetic displacement control valve.
- the compressor 11 may be an electric compressor that is rotationally driven by an electric motor. In the case of an electric compressor, the discharge capacity is varied depending on the rotation speed of the electric motor.
- the condenser 12 exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the vehicle exterior air (hereinafter referred to as “outside air”) forcedly blown by a cooling fan (not shown), so that the heat of the high-pressure refrigerant is obtained. Is a heat exchanger that releases (cools) the air to the outside air to condense and liquefy the refrigerant.
- the condenser 12 functions as a heat radiator which cools a high pressure refrigerant
- the refrigerant outflow side of the condenser 12 is connected to an inflow portion 141 (details will be described later) of the ejector 100.
- the ejector 100 is a decompression means for decompressing the liquid-phase refrigerant (high-pressure refrigerant) flowing out from the condenser 12, and is used for fluid transportation that circulates the refrigerant by suction action (entrainment action) of the refrigerant flow ejected at high speed. It is also a refrigerant circulation means. As shown in FIG. 2, the ejector 100 includes a nozzle unit 110, a suction unit 120, a diffuser unit 130, a swirling space 140, and an area variable mechanism 150.
- the nozzle unit 110 takes in the liquid-phase refrigerant flowing out of the condenser 12 through a swirling space 140 described later, and reduces the passage area toward the downstream side of the refrigerant flow to convert the pressure energy of the refrigerant into velocity energy. Thus, it is expanded under reduced pressure in an isentropic manner.
- the nozzle part 110 includes a tapered portion 111 in which the flow path tapers toward the downstream side, and a divergent portion 112 that is disposed on the downstream side of the tapered detail 111 and that the flow path expands toward the downstream side. .
- a portion where the tapered portion 111 and the divergent portion 112 are connected is a nozzle throat portion (minimum passage area portion) 113 in which the flow path area is most reduced.
- coolant flow direction of the nozzle part 110 is defined as the axis line 114.
- the suction part 120 is a flow path formed in a direction intersecting the nozzle part 110, and is arranged so as to communicate with the refrigerant outlet of the nozzle part 110 (the outlet part of the divergent part 112) from the outside of the ejector 100. ing.
- the refrigerant inlet side of the evaporator 16 is connected to the cold inlet side of the suction unit 120.
- the diffuser unit 130 includes a high-speed refrigerant (injected refrigerant) ejected from the nozzle unit 110 on the downstream side of the nozzle unit 110 and the suction unit 120, and a gas-phase refrigerant (from the suction unit 120 (evaporator 16)). Suction refrigerant), the flow of the mixed refrigerant is decelerated, speed energy is converted into pressure energy, and the pressure is increased.
- injected refrigerant injected refrigerant
- suction unit 120 evaporator 16
- the diffuser portion 130 is formed in a shape (so-called diffuser shape) in which the flow passage cross-sectional area of the refrigerant is gradually increased toward the downstream side (so-called diffuser shape), thereby having the above-described boosting function.
- the enlargement ratio of the flow passage cross-sectional area of the diffuser portion 130 is set, for example, in a trumpet shape so as to increase sequentially toward the downstream side.
- a gas-liquid separator 13 is connected to the refrigerant outlet side of the diffuser unit 130.
- the swirl space 140 is disposed on the upstream side of the nozzle unit 110, and swirls the liquid refrigerant flowing out of the condenser 12, and is on the outer peripheral side of a virtual swirl flow center line (hereinafter, swirl center line). This is a flow path through which the gas-liquid mixed phase refrigerant flows into the nozzle part 110 such that a larger amount of the gas-phase refrigerant exists on the inner peripheral side.
- the swirling space 140 is formed by, for example, a flat cylindrical space.
- the swirl space 140 is provided with a pipe-shaped inflow portion 141 that is connected to the cylindrical outer periphery in a tangential direction and communicates with the swirl space 140.
- the cylindrical virtual axis line of the swirl space 140 is defined as the axis line 142, more specifically, the axis line 142, the axis line 114, and the axis line 142 are parallel to the virtual axis line 114 of the nozzle part.
- the swirl space 140 is arranged with respect to the nozzle unit 110 so that the two coincide with each other, and the swirl space 140 is connected to communicate with the nozzle unit 110.
- the refrigerant outlet side of the condenser 12 is connected to the refrigerant inlet side of the inflow portion 141.
- the ratio A of the channel cross-sectional area of the inflow portion 141 to the channel cross-sectional area of the nozzle throat 113 and the ratio B of the channel cross-sectional area of the swirling space 140 to the channel cross-sectional area of the nozzle throat 113 are determined in advance.
- the predetermined value is set.
- the area variable mechanism 150 is a mechanism unit that changes the flow path area between the nozzle unit 110 and the diffuser unit 130, and includes a passage forming member 151 and a driving unit (not shown) that drives the channel forming member 151.
- the passage forming member 151 is formed in a conical shape, and has a curved surface along the inner peripheral surface of the divergent portion 112 and the diffuser portion 130 as an outer peripheral surface thereof, and is arranged so that the tip side faces the nozzle portion 110 side. The divergent section 112 and the diffuser section 130 are inserted.
- the passage forming member 151 is disposed in a space (pressure reduction space) in which the nozzle portion 110 is formed and in a space (pressure increase space) in which the diffuser portion 130 is formed. Further, a gap is formed between the outer peripheral surface of the passage forming member 151 and the inner peripheral surfaces of the divergent portion 112 and the diffuser portion 130, and this gap is formed inside the nozzle portion 110 (the divergent portion 112) and the diffuser portion 130. It is formed as a flow path.
- the refrigerant passage formed between the inner peripheral surface of the space forming the nozzle portion 110 (decompression space) and the outer peripheral surface of the passage forming member 151 functions as a nozzle portion that decompresses and injects the refrigerant.
- a refrigerant passage that forms a flow path (nozzle passage) and is formed between an inner peripheral surface of a space (a pressurizing space) that forms the diffuser portion 130 and an outer peripheral surface of the passage forming member 151 is an injection refrigerant and a suction refrigerant.
- An internal flow path (diffuser passage) that functions as a diffuser part that mixes and boosts the pressure is configured.
- the diffuser portion 130 is formed in a trumpet shape as described above, and the passage forming member 151 is formed with a curved surface along the inner peripheral surface of the diffuser portion 130.
- the internal flow path is formed so as to expand in a direction intersecting the axial direction of the diffuser portion 130. That is, the internal flow path of the diffuser part 130 is a flow path that faces the centrifugal direction from the axial direction from the upstream side toward the downstream side.
- the downstream side of the internal flow path of the diffuser part 130 is not limited to the centrifugal direction that is completely orthogonal to the axis.
- the drive unit slides the passage forming member 151 in the direction of the axis 114, and includes a temperature sensing unit, an operating rod, and an elastic member.
- the temperature-sensing part is the temperature and pressure of the liquid-phase refrigerant supplied from the condenser 12 via the inflow part 141 to the ejector 100, or the vapor-phase refrigerant supplied from the evaporator 16 via the suction part 120 to the ejector 100.
- the volume in the pressure chamber defined by the diaphragm expands and contracts.
- the operating rod is a rod-like member arranged so as to be parallel to the axis 114, one end side being connected to the diaphragm and the other end side being connected to the passage forming member 151.
- the operating rod moves in the direction of the axis 114 in accordance with the expansion and contraction of the temperature sensing part (diaphragm), and slides the passage forming member 151 in the direction of the axis 114.
- the elastic member is arranged so as to urge the passage forming member 151 from the side opposite to the operating rod, and for example, a spring is used.
- the temperature sensing part expands.
- the temperature sensing part moves the operating rod.
- the passage forming member 151 is moved to the side where the gap between the nozzle part 110 and the diffuser part 130 becomes larger, and the flow path areas of the nozzle part 110 and the diffuser part 130 are increased.
- the temperature sensing portion contracts, and the passage forming member 151 has a gap between the nozzle portion 110 and the diffuser portion 130 by the biasing force of the elastic member.
- the flow path area of the nozzle part 110 and the diffuser part 130 is reduced by moving to a smaller side. Since the passage forming member 151 is formed by one member for the nozzle part 110 and the diffuser part 130, the flow passage areas of the nozzle part 110 and the diffuser part 130 are changed at the same time. .
- the gas-liquid separator 13 is a gas-liquid separator that separates the mixed refrigerant flowing out from the diffuser portion 130 of the ejector 100 into two phases.
- the ejector 100 described above and the gas-liquid separator 13 recover the loss of kinetic energy when the refrigerant is decompressed by the nozzle unit 110, and convert the recovered kinetic energy into pressure energy to compress the compressor 11. It can also be expressed that the power recovery device 15 for increasing the pressure of the suction refrigerant is formed.
- the gas-liquid separator 13 is connected to the compressor 11 and the liquid storage unit 14. Among the refrigerant separated into the gas-liquid two phases by the gas-liquid separator 13, the gas-phase refrigerant is sucked into the compressor 11. Of the refrigerant separated into the gas-liquid two phases by the gas-liquid separator 13, the liquid-phase refrigerant flows out to the liquid storage unit 14.
- the liquid storage unit 14 is a container body that stores the liquid-phase refrigerant among the gas-liquid two-phase refrigerant separated by the gas-liquid separator 13.
- the liquid storage unit 14 has a cylindrical flow. A road is formed.
- the refrigerant outflow side of the liquid storage unit 14 is connected to the refrigerant inflow side of the evaporator 16.
- the liquid storage unit 14 is disposed between the gas-liquid separator 13 and the evaporator 16, that is, on the low pressure side of the refrigeration cycle 10.
- the evaporator 16 is a heat exchanger that evaporates refrigerant flowing through the outside air introduced into the air-conditioning case of the air-conditioner by the blower or the heat absorption action from the air in the passenger compartment (hereinafter referred to as “inside air”).
- the refrigerant outflow side of the evaporator 16 is connected to the suction part 120 of the ejector 100 by a refrigerant pipe.
- a control device (not shown) is composed of a well-known microcomputer including a CPU, a ROM, a RAM and the like and its peripheral circuits.
- Various control signals air conditioning operation switch, set temperature switch, etc.
- the apparatus controls the operation of various devices (mainly the compressor 11) by performing various operations and processes based on the control program stored in the ROM using these input signals.
- control current In control signal
- the electromagnetic capacity control valve of the compressor 11 When a control current In (control signal) is output from the control device to the electromagnetic capacity control valve of the compressor 11 based on the control program, the discharge capacity of the compressor 11 is adjusted, and the compressor 11 performs gas-liquid separation. The gas-phase refrigerant is sucked from the vessel 13 and compressed and discharged.
- the high-temperature and high-pressure refrigerant is cooled by the outside air to be condensed and liquefied.
- the liquid-phase refrigerant that has flowed out of the condenser 12 flows into the swirling space 140 from the inflow portion 141 of the ejector 100.
- the liquid-phase refrigerant that has flowed into the swirl space 140 is connected so that the inflow portion 141 faces the tangential direction with respect to the cylindrical outer periphery of the swirl space 140. It turns into a swirling flow.
- the turning center line substantially coincides with the axis 142.
- the pressure in the vicinity of the swirling center line is lowered to a pressure at which the refrigerant boils under reduced pressure (causes cavitation) by the action of centrifugal force.
- the surroundings can be in a liquid single-phase two-phase separation state.
- the gas single-phase and liquid single-phase refrigerants are contained in the nozzle part 110 as refrigerants in a gas-liquid mixed phase state. To flow into.
- the refrigerant is expanded under reduced pressure. Since the pressure energy of the refrigerant is converted into velocity energy during the decompression and expansion, the gas-liquid mixed phase refrigerant is ejected from the nozzle unit 110 at a high velocity. Then, due to the refrigerant suction action of the refrigerant jet flow, the liquid phase refrigerant in the liquid storage unit 14 flows through the evaporator 16 and is sucked into the suction unit 120 as a gas phase refrigerant.
- the vicinity of the swirl center line is in a two-phase separation state of a gas single phase and the surroundings are a liquid single phase.
- the flow from the tapered portion 111 of the nozzle portion 110 to the outlet of the divergent portion 112 becomes a two-phase spray state,
- the flow rate of the refrigerant injected from the outlet of the divergent portion 112 is increased.
- the refrigerant ejected from the nozzle part 110 and the refrigerant sucked by the suction part 120 become mixed refrigerant and flow into the diffuser part 130 on the downstream side of the nozzle part 110.
- the refrigerant velocity energy rises because the velocity energy of the refrigerant is converted into pressure energy by expanding the passage area toward the downstream side.
- the flow rate of the refrigerant passing through the nozzle part 110 and the diffuser part 130 is adjusted by the area variable mechanism 150. That is, when the temperature and pressure of the refrigerant (high-pressure liquid-phase refrigerant or low-pressure gas-phase refrigerant) supplied to the ejector 100 are increased, the flow passage areas of the nozzle part 110 and the diffuser part 130 are changed to the larger side. In addition, when the temperature and pressure of the refrigerant supplied to the ejector 100 are reduced, the flow passage areas of the nozzle part 110 and the diffuser part 130 are changed to a smaller side.
- the refrigerant high-pressure liquid-phase refrigerant or low-pressure gas-phase refrigerant
- the load of the refrigeration cycle 10 is high, and the amount of refrigerant circulating in the refrigeration cycle 10 is increased by the amount that the flow path area is increased.
- the load of the refrigeration cycle 10 is low, and the amount of refrigerant circulating in the refrigeration cycle 10 is reduced by the amount that the flow path area is reduced.
- the refrigerant that has flowed out of the diffuser unit 130 flows into the gas-liquid separator 13.
- the gas-phase refrigerant is sucked into the compressor 11 and compressed again.
- the pressure of the refrigerant sucked into the compressor 11 is increased by the diffuser portion 130 of the ejector 100, the driving power of the compressor 11 can be reduced.
- the liquid-phase refrigerant flows into the liquid storage part 14, and the refrigerant suction action of the ejector 100 causes the liquid storage part 14 to enter the evaporator 16. Inflow.
- the low-pressure liquid-phase refrigerant absorbs heat from the air (outside air or inside air) in the air conditioning case and evaporates. That is, the air in the air conditioning case is cooled. Then, the gas-phase refrigerant after passing through the evaporator 16 is sucked into the ejector 100 and flows out from the diffuser unit 130.
- the ejector 100 is provided with the swirl space 140, the liquid refrigerant is swirled, and in the swirl space 140, the vicinity of the swirl center line is a gas single phase and the surroundings are a liquid single phase.
- Two-phase separation is achieved. That is, the refrigerant pressure on the turning center side is reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation).
- the tapered portion 111 smallest flow passage area portion
- the divergent portion 112 divergent portion 112
- the flow rate of the refrigerant injected from the outlet of the divergent section 112 is increased. Since the efficiency (nozzle efficiency) of the nozzle part 110 of the ejector 100 is proportional to the speed of the refrigerant to be ejected, as a result, the nozzle efficiency of the nozzle part 110 can be improved, and consequently the ejector efficiency can be improved. it can.
- the nozzle unit 110 is not a two-stage nozzle, but performs decompression and expansion of the refrigerant by one nozzle, so that all the pressure energy of the liquid-phase refrigerant flowing into the ejector 100 is utilized to increase the boosted energy by the diffuser unit 130. Obtainable.
- the flow path area can be changed according to the load of the refrigeration cycle 10. Accordingly, it is possible to flow an amount of refrigerant commensurate with the load, and the effective operation of the ejector 100 can be brought out.
- the high-pressure refrigerant that flows into the ejector 100 is a liquid-phase refrigerant in the present embodiment.
- the high-pressure refrigerant is a liquid-phase refrigerant
- the refrigerant is in a two-phase separation state in the swirling space 140 in the swirling space 140, in the vicinity of the swirling center line, with a gas single phase and the surroundings.
- the flow from the tapered portion 111 of the nozzle portion 110 to the outlet of the divergent portion 112 is in a two-phase spray state.
- the flow rate of the refrigerant injected from the outlet of the divergent portion 112 is increased.
- the nozzle efficiency can be greatly improved as compared with the case where the high-pressure refrigerant is a gas-liquid two-phase.
- the area variable mechanism 150 can change the flow path area between the nozzle part 110 and the diffuser part 130 at the same time by the passage forming member 151. Thereby, when changing a flow-path area, the flow of the refrigerant
- a member that changes the flow path area between the nozzle part 110 and the diffuser part 130 can be formed by one member (passage forming member 151), and the configuration of the area variable mechanism 150 can be simplified. .
- the internal flow path of the diffuser portion 130 formed by the passage forming member 151 is provided so as to expand in a direction intersecting the axial direction of the diffuser portion 130. Thereby, the length of the diffuser part 130 in the axial direction can be reduced, and the compact ejector 100 can be obtained.
- the liquid-phase refrigerant swirled by the swirling space 140 is maintained in the swirl state in the nozzle unit 110 and the diffuser unit 130, and intersects the axial direction of the diffuser unit 130 together with the gas-phase refrigerant from the suction unit 120. Will be leaked. Therefore, the mixed refrigerant flowing out of the diffuser unit 130 is subjected to centrifugal separation action by the swirling flow, and the liquid refrigerant having a high density is discharged to the side farther from the axis than the gas refrigerant having the low density.
- the ejector 100 can have an effective gas-liquid separation function.
- the ejector 100 and the gas-liquid separator 13 are integrally formed with respect to the first embodiment. Specifically, as shown in FIG. 4, the ejector 100 and the gas-liquid separator 13 of this embodiment are integrally formed by disposing the ejector 100 on the upper part of the cylindrical gas-liquid separator 13. Has been.
- the axis 114 of the nozzle part 110 is in the same direction as the cylindrical axis of the gas-liquid separator 13, and the swirl space 140, the nozzle part 110, and the diffuser part from the upper side to the lower side. 130 and an area variable mechanism 150 are arranged.
- the downstream side of the diffuser section 130 communicates with the upper side of the gas-liquid separator 13.
- the refrigerant swirled by the swirling space 140 is maintained in the swirling state in the nozzle unit 110 and the diffuser unit 130 and flows out of the diffuser unit 130. Therefore, the mixed refrigerant flowing out of the diffuser unit 130 is subjected to centrifugal separation action by the swirling flow, and the gas phase refrigerant having a low density gathers on the center side of the swirling flow, and the liquid phase having a high density on the outer peripheral side of the swirling flow. Refrigerant gathers and gas-liquid separation occurs.
- a refrigeration cycle 10B of the third embodiment is shown in FIG.
- a receiver (liquid receiving unit) 12b that stores the liquid-phase refrigerant that has flowed out of the condenser 12 is provided in the second embodiment.
- the liquid-phase refrigerant flows out directly to the evaporator 16.
- the receiver 12b is disposed on the refrigerant outflow side of the condenser 12, and stores the liquid phase refrigerant that has flowed out of the condenser 12. And a liquid phase refrigerant
- coolant is supplied to the ejector 100 (inflow part 141) from the receiver 12b. Thereby, the effect similar to the said 2nd Embodiment can be acquired.
- a refrigeration cycle 10C of the fourth embodiment is shown in FIGS.
- a liquid storage part 14 is further provided integrally with the ejector 100 in which the gas-liquid separator 13 is integrally formed as in the second embodiment.
- the compact ejector 100 which is integrally provided with the gas-liquid separator 13 and the liquid storage part 14 is realizable. Further, by integrating the liquid storage unit 14 with the gas-liquid separator 13, the refrigerant separated by the gas-liquid separator 13 can be efficiently stored in the liquid storage unit 14.
- the ejector 100 integrally provided with the gas-liquid separator 13 and the liquid storage unit 14 described in the fourth embodiment is applied to the refrigeration cycle 10D shown in FIG. An example configured as shown in the sectional view will be described. In the refrigeration cycle 10D, a compressor 11, a condenser 12, an ejector 100, and an evaporator 16 are connected by a refrigerant pipe.
- the condenser 12 As the condenser 12, the high-pressure gas-phase refrigerant discharged from the compressor 11 is condensed by exchanging heat with the outside air blown from the cooling fan, and the refrigerant flowing out of the condenser 12a is condensed.
- a receiver 12b that separates gas-liquid and stores excess liquid-phase refrigerant, and a supercooling unit 12c that heat-exchanges the liquid-phase refrigerant flowing out from the receiver 12b with the outside air blown from the cooling fan and supercools it.
- the so-called subcool condenser is used.
- an HFC refrigerant (specifically, R134a) is adopted as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured.
- an HFO-based refrigerant (specifically, R1234yf) or the like may be adopted as long as it is a refrigerant constituting the subcritical refrigeration cycle.
- 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.
- FIG. 10 is a schematic cross-sectional view for explaining the function of each refrigerant passage of the ejector 100, corresponding to FIG. 2 of the first embodiment, and the same parts as those in FIG.
- symbol is attached
- the ejector 100 of the present embodiment includes a body member 200 configured by combining a plurality of constituent members as shown in FIG.
- the body member 200 has a housing body 210 that is formed of a prismatic or columnar metal and forms the outer shell of the ejector 100.
- a nozzle body 220, a middle body, and the like. 230, lower body 240, etc. are fixed.
- the housing body 210 includes a refrigerant inlet 211 that allows the refrigerant flowing out of the condenser 12 to flow into the interior, a refrigerant suction port 212 that sucks the refrigerant flowing out of the evaporator 16, and a gas-liquid separation formed inside the body member 200.
- the liquid-phase refrigerant outlet 213 that causes the liquid-phase refrigerant separated in the space 206 to flow out to the refrigerant inlet side of the evaporator 16 and the gas-phase refrigerant separated in the gas-liquid separation space 206 to the suction side of the compressor 11.
- a gas-phase refrigerant outlet 214 and the like are formed to flow out.
- the nozzle body 220 is formed of a substantially conical metal member that tapers in the refrigerant flow direction.
- the nozzle body 220 is press-fitted into the housing body 210 so that its axial direction is parallel to the vertical direction (vertical direction in FIG. 9). It is fixed by means of Between the upper side of the nozzle body 220 and the housing body 210, a swirl space 140 is formed for swirling the refrigerant flowing from the refrigerant inlet 211.
- the swirling space 140 is formed in a rotating body shape, and its central axis 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 140 of this 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 inflow portion (refrigerant inflow passage) 141 that connects the refrigerant inlet 211 and the swirl space 140 extends in the tangential direction of the inner wall surface of the swirl space 140 when viewed from the central axis direction of the swirl space 140.
- the refrigerant that has flowed into the swirl space 140 from the inflow portion 141 flows along the inner wall surface of the swirl space 140 and swirls in the swirl space 140.
- the inflow portion 141 does not have to be formed so as to completely coincide with the tangential direction of the swirl space 140 when viewed from the central axis direction of the swirl space 140, and at least the component in the tangential direction of the swirl space 140 If it contains, it may be formed including the component of the other direction (For example, the component of the axial direction of the turning space 140).
- the refrigerant pressure on the central axis side is lower than the refrigerant pressure on the outer peripheral side in the swirling space 140. Therefore, in the present embodiment, during the operation of the refrigeration cycle 10D, the refrigerant pressure on the central axis side in the swirling space 140 is reduced to a pressure that becomes a saturated liquid phase refrigerant or a pressure at which the refrigerant boils under reduced pressure (causes cavitation). I try to let them.
- Such adjustment of the refrigerant pressure on the central axis side in the swirl space 140 can be realized by adjusting the swirl flow velocity of the refrigerant swirling in the swirl space 140 as described in the first embodiment.
- the swirl flow velocity can be adjusted by adjusting the ratio of the flow path cross-sectional area between the passage cross-sectional area of the inflow portion 141 and the axial vertical cross-sectional area of the swirl space 140, 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 140.
- a decompression space 202 is formed in which the refrigerant that has flowed out of the swirl space 140 is decompressed and flows downstream.
- the decompression space 202 is formed in a rotating body shape in which a cylindrical space and a truncated cone-shaped 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 work space 202 is arranged coaxially with the central axis of the swirling space 140.
- a nozzle throat portion (minimum passage area portion) 113 having the smallest refrigerant passage area is formed in the decompression space 202 inside the decompression space 202, and a passage for changing the passage area of the nozzle throat portion 113.
- a forming member 151 is disposed.
- the passage forming member 151 is formed in a substantially conical shape that gradually expands in the radial direction toward the downstream side of the refrigerant flow, and the central axis thereof is arranged coaxially with the central axis of the decompression space 202.
- the passage forming member 151 is formed in a conical shape whose cross-sectional area increases as the distance from the decompression space 202 increases.
- FIG. (Minimum passage area portion) 113 is formed on the upstream side of the refrigerant flow, and is formed on the downstream side of the refrigerant flow from the nozzle throat portion 113 and the tapered portion 111 where the refrigerant passage area gradually reaches the nozzle throat portion 113.
- a divergent portion 112 is formed in which the refrigerant passage area gradually increases.
- the decompression space 202 and the upper side of the passage forming member 151 are overlapped (overlapped) when viewed from the radial direction of the axis 114 of the nozzle portion (the central axis of the passage forming member 151).
- the vertical cross-sectional shape of the axis 114 is an annular shape (a donut shape excluding a small-diameter circular shape arranged coaxially from the circular shape).
- a nozzle that functions as a nozzle by a refrigerant passage formed between the inner peripheral surface of a portion of the nozzle body 220 that forms the pressure reducing space 202 and the upper outer peripheral surface of the passage forming member 151 by this passage shape.
- a passage 110 (corresponding to the nozzle portion 110 described in the above embodiment) is used, and the flow rate of the refrigerant depressurized in the nozzle passage 110 is increased so as to be a sonic velocity.
- the refrigerant flows while swirling along the refrigerant passage having an annular cross section.
- the middle body 230 is provided with a rotating body-shaped through-hole penetrating the front and back at the center, and a drive for displacing the passage forming member 151 on the outer peripheral side of the through-hole. It is formed of a metal disk-like member that accommodates the portion 160.
- the central axis of the through hole is arranged coaxially with the central axes of the swirling space 140 and the decompression space 202.
- the middle body 230 is fixed inside the housing body 210 and below the nozzle body 220 by means such as press fitting.
- an inflow space 203 for retaining the refrigerant flowing in from the refrigerant suction port 212 is formed between the upper surface of the middle body 230 and the inner wall surface of the housing body 210 facing the middle body 230.
- the inflow space 203 is in the direction of the central axis of the swirl space 140 and the decompression space 202 (nozzle passage 110). , When viewed from the direction of the axis 114).
- the outer shape of the tapered tip portion of the nozzle body 220 is adapted.
- the refrigerant passage cross-sectional area gradually decreases in the refrigerant flow direction.
- a suction passage 204 is formed between the inner peripheral surface of the through hole and the outer peripheral surface on the lower side of the nozzle body 220 to communicate the inflow space 203 and the downstream side of the refrigerant flow in the decompression space 202. That is, in the present embodiment, the suction space (suction passage) 120 through which the suction refrigerant flows from the outer peripheral side to the inner peripheral side of the central axis is formed by the inflow space 203 and the suction passage 204. Further, the central axis vertical cross-sectional shape of the suction portion (suction passage) 120 is also annular as shown in the cross-sectional view of FIG.
- the pressurizing space 205 is a space in which the jetted refrigerant jetted from the nozzle passage 110 described above and the sucked refrigerant sucked from the suction unit 120 are mixed and pressurized.
- the lower side of the passage forming member 151 is disposed in the pressurizing space 205.
- the expansion angle of the conical side surface of the passage forming member 151 in the pressure increasing space 205 is smaller than the expansion angle of the frustoconical space of the pressure increasing space 205. Therefore, the refrigerant passage area of this refrigerant passage is downstream of the refrigerant flow. It gradually expands toward the side.
- a diffuser passage 130 that functions as a diffuser corresponding to the diffuser portion 130 described in the above embodiment, and the velocity energy of the injected refrigerant and the suction refrigerant is converted into pressure energy.
- the center axis vertical cross-sectional shape of the diffuser passage 130 is formed in an annular shape as shown in the cross-sectional view of FIG. 13, and in the diffuser passage 130, as shown by thick solid arrows in FIGS. 10 and 13,
- the refrigerant flows while swirling along the refrigerant passage having an annular cross section due to the velocity component in the swirling direction of the refrigerant injected from the refrigerant passage functioning as a nozzle.
- the drive unit 160 includes a circular thin plate-shaped diaphragm 161 and the like. More specifically, as shown in FIG. 9, the diaphragm 161 is fixed by means such as welding so as to partition a cylindrical space formed on the outer peripheral side of the middle body 230 into two upper and lower spaces.
- the space on the upper side constitutes an enclosed space 162 in which a temperature-sensitive medium that changes in pressure according to the temperature of the refrigerant flowing out of the evaporator 16 is enclosed.
- a temperature sensitive medium having the same composition as the refrigerant circulating in the refrigeration cycle 10 is enclosed 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 161 constitutes an introduction space 163 for introducing the refrigerant flowing out of the evaporator 16 through a communication path (not shown). Therefore, the temperature of the refrigerant flowing out of the evaporator 16 is transmitted to the temperature-sensitive medium enclosed in the enclosed space 162 via the lid member 164 and the diaphragm 161 that partition the inflow space 203 and the enclosed space 162.
- the suction part (suction passage) 120 is disposed above the middle body 230 of the present embodiment, and the diffuser passage 130 is disposed below the middle body 230. ing. Therefore, at least a part of the drive unit 160 is disposed at a position sandwiched between the suction unit 120 and the diffuser passage 130 when viewed from the radial direction of the axis.
- the enclosed space 162 of the drive unit 160 is disposed at a position that overlaps with the suction unit 120 and the diffuser passage 130 when viewed from the axial direction and is surrounded by the suction unit 120 and the diffuser passage 130. ing. As a result, the temperature of the refrigerant flowing out of the evaporator 16 is transmitted to the enclosed space 162, and the internal pressure of the enclosed space 162 becomes a pressure corresponding to the temperature of the refrigerant flowing out of the evaporator 16.
- the diaphragm 161 is deformed according to a differential pressure between the internal pressure of the enclosed space 162 and the pressure of the refrigerant flowing out of the evaporator 16 flowing into the introduction space 163.
- the diaphragm 161 is preferably made of a tough material having high elasticity and good heat conduction, and is preferably made of a thin metal plate such as stainless steel (SUS304).
- the diaphragm 161 may be used as an example of a pressure responsive member that is displaced according to the pressure of the temperature-sensitive medium in the enclosed space 162.
- the upper end side of the columnar actuating rod 165 is joined to the center of the diaphragm 161 by means such as welding, and the outer peripheral side of the lowermost side (bottom side) of the passage forming member 151 is joined to the lower end side of the actuating rod 165. It is fixed. Thereby, the diaphragm 161 and the passage forming member 151 are connected, and the passage forming member 151 is displaced in accordance with the displacement of the diaphragm 161, and the refrigerant passage area in the nozzle throat 113 of the decompression space 202 is adjusted.
- the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 162 increases, and the pressure in the introduction space 163 is subtracted from the internal pressure of the enclosed space 162.
- Increased differential pressure As a result, the diaphragm 161 displaces the passage forming member 151 in the direction in which the refrigerant passage area in the nozzle throat portion 113 is enlarged (downward in the vertical direction).
- the diaphragm 161 displaces the passage forming member 151 in a direction (vertical direction upper side) in which the refrigerant passage area in the nozzle throat 113 is reduced.
- the diaphragm 161 displaces the passage forming member 151 in accordance with the degree of superheat of the refrigerant flowing out of the evaporator 16, so that the degree of superheat of the refrigerant on the outlet side of the evaporator 16 approaches the predetermined value.
- the refrigerant passage area at 113 can be adjusted. That is, in this embodiment, the area variable mechanism 150 is configured by the passage forming member 151 and the drive unit 160.
- the gap between the operating rod 165 and the middle body 230 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 165 is displaced.
- a sealing member such as an O-ring (not shown)
- the bottom surface of the passage forming member 151 receives a load of a coil spring 241 fixed to the lower body 240.
- the coil spring 241 applies a load that urges the passage forming member 151 toward the side where the refrigerant passage area in the nozzle throat 113 is reduced. By adjusting this load, the valve opening pressure of the passage forming member 151 is increased. You can also change the target superheat degree.
- a plurality of (specifically, two) columnar spaces are provided on the outer peripheral side of the middle body 230, and two thin drive diaphragms 161 are fixed inside the spaces, respectively.
- 160 is configured, the number of driving units 160 is not limited to this.
- a diaphragm formed of 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 151 may be connected by a plurality of operating rods. Good.
- the lower body 240 is formed of a cylindrical metal member, and is fixed in the housing body 210 by means such as screwing so as to close the bottom surface of the housing body 210.
- a gas-liquid separation space 206 for separating the gas and liquid of the refrigerant flowing out of the diffuser passage 130 is formed.
- the gas-liquid separation space 206 is formed as a substantially cylindrical rotating body-shaped space, and the central axis of the gas-liquid separation space 206 is also arranged coaxially with the central axes of the swirl space 140, the decompression space 202, and the like. Has been.
- the refrigerant flows while swirling along the refrigerant passage having an annular cross section, so that the refrigerant flowing from the diffuser passage 130 into the gas-liquid separation space 206 also has a velocity component in the swirling direction.
- the gas-liquid refrigerant is separated in the gas-liquid separation space 206 by the action of centrifugal force.
- a cylindrical pipe 242 that is coaxially disposed in the gas-liquid separation space 206 and extends upward is provided.
- the liquid refrigerant separated in the gas-liquid separation space 206 is stored on the outer peripheral side of the pipe 242.
- a gas-phase refrigerant outflow passage 243 that guides the gas-phase refrigerant separated in the gas-liquid separation space 206 to the gas-phase refrigerant outlet 214 of the housing body 210 is formed inside the pipe 242.
- the above-described coil spring 241 is fixed to the upper end portion of the pipe 242.
- the coil spring 241 also functions as a vibration buffer member that attenuates vibration of the passage forming member 151 caused by pressure pulsation when the refrigerant is depressurized.
- an oil return hole 244 for returning the refrigeration oil in the liquid-phase refrigerant into the compressor 11 through the gas-phase refrigerant outflow passage 243 is formed in the root portion (lowermost portion) of the pipe 242.
- the energy conversion efficiency (corresponding to the nozzle efficiency) in the nozzle passage 110 can be improved by swirling the refrigerant in the swirling space 140 as in the first embodiment.
- the ejector efficiency can be improved.
- the flow of refrigerant in the gas-liquid mixed state is choked in the vicinity of the nozzle throat portion 113, and the refrigerant in the gas-liquid mixed state that has reached the speed of sound by the choking is accelerated by the divergent portion 112 and injected.
- the energy conversion efficiency in the nozzle passage 110 can be improved by efficiently accelerating the refrigerant in the gas-liquid mixed state to the sound speed by the boiling promotion by both the wall surface boiling and the interface boiling.
- the passage forming member 151 of the ejector 100 of the present embodiment is formed in a substantially conical shape whose cross-sectional area increases as the distance from the decompression space 202 increases, the shape of the diffuser passage 130 is changed to the decompression space 202. It can be set as the shape which spreads to an outer peripheral side as it leaves
- the decompression space 202, the inflow space 203 and the suction passage 204 forming the suction portion 120, the pressurization space 205, and the passage formation member 151 are all formed in a rotating body shape.
- the axes of each other are arranged on the same axis.
- path 130 is made into an annular
- the suction portion 120 can be shaped so that the refrigerant flows from the outer peripheral side of the axis to the inner peripheral side
- the diffuser passage 130 can be shaped so that the refrigerant flows from the inner peripheral side of the axis to the outer peripheral side. That is, passage arrangement that effectively uses the internal space of the body member 200 is possible, and the size of the ejector as a whole can be further prevented from increasing in size.
- the cross-sectional shape of the diffuser passage 130 into an annular shape, the refrigerant flowing through the diffuser passage 130 can be swirled in the same direction as the refrigerant swirling in the swirling space 140.
- the flow path for increasing the pressure of the refrigerant can be formed in a spiral shape. Therefore, as shown in FIG. 14, the diffuser portion is formed in a shape extending in the axial direction of the nozzle portion as in the comparative example. On the other hand, it can suppress that the dimension of the center axis direction of the diffuser part 130 expands. As a result, the enlargement of the physique as the whole ejector 100 can be suppressed further.
- the ejector 100 of the present embodiment includes the drive unit 160, the passage forming member 151 is displaced according to the load fluctuation of the refrigeration cycle 10D, and the refrigerant passage areas of the nozzle passage 110 and the diffuser passage 130 are adjusted. can do. Therefore, it becomes possible to flow the amount of refrigerant according to the load of the refrigeration cycle 10D, and the effective operation of the ejector 100 corresponding to the load of the refrigeration cycle 10D can be derived.
- the enclosed space 162 in which the temperature sensitive medium is enclosed is disposed in the drive unit 160 at a position sandwiched between the suction unit 120 and the diffuser passage 130, it is formed between the suction unit 120 and the diffuser passage 130. Space can be used effectively. As a result, the enlargement of the physique as the whole ejector can be further suppressed.
- the enclosed space 162 is disposed at a position surrounded by the suction part 120 and the diffuser passage 130, the temperature of the refrigerant flowing out of the evaporator 16 flowing through the suction part 120 without being affected by the outside air temperature can be sensed. It is possible to change the pressure in the enclosed space 162 with good transmission to the warm medium. That is, the pressure in the enclosed space 162 can be accurately changed according to the temperature of the refrigerant flowing out of the evaporator 16.
- the refrigerant passage areas of the nozzle passage 110 and the diffuser passage 130 can be changed more appropriately, and the enclosed space 162 can be reduced in size, and the area variable mechanism 150 can be reduced in size.
- the body member 200 of the ejector 100 of the present embodiment is formed with a gas-liquid separation space 206 that separates the gas-liquid of the refrigerant flowing out from the diffuser passage 130, a gas-liquid separation means is provided separately from the ejector 100. Compared with the case of providing, the volume of the gas-liquid separation space 206 can be effectively reduced.
- the refrigerant flowing out from the diffuser passage 130 formed in an annular cross section has already swirled, so that a swirling flow of the refrigerant is generated or grows in the gas-liquid separation space 206.
- the volume of the gas-liquid separation space 206 can be effectively reduced as compared with the case where the gas-liquid separation means is provided separately from the ejector 100.
- the high-pressure refrigerant flowing into the swirling space 140 is a liquid-phase refrigerant
- the present invention is not limited to this, and may be a gas-liquid two-phase refrigerant. Even if the refrigerant flowing into the swirl space 140 is in a gas-liquid two-phase state, in the swirl space 140, it is likely that a larger amount of gas-phase refrigerant exists on the inner peripheral side than the outer peripheral side of the swirl center line due to the swirling flow of the refrigerant The same effect can be obtained with respect to the nozzle efficiency improvement.
- the internal flow path of the diffuser unit 130 extends from the upstream side to the downstream side in a direction intersecting the axial direction of the diffuser unit 130.
- the present invention is not limited to this, and mainly in the axial direction. It is good also as what expands towards.
- the axial cross-sectional shape is not completely an isosceles triangle, and as shown in FIG. 2, FIG.
- the two sides sandwiched are convex on the inner circumference side, of course, it may be convex on the outer circumference side, or may be a shape close to a cone, or partially including a cone shape The shape formed may be sufficient.
- a receiver 12b may be provided as in the third embodiment.
- refrigeration cycle 10, 10A, 10B, 10C, 10D in each of the above embodiments is replaced with a vehicle refrigeration vehicle or a heat pump cycle for a domestic water heater or an indoor air conditioner instead of the vehicle air conditioner as described above. Can be applied to.
- the type of the refrigerant is not particularly specified.
- the refrigerant uses a fluorocarbon refrigerant, an HC refrigerant, a carbon dioxide refrigerant, etc., and is supercritical in addition to the normal cycle. It can be applied to cycles and subcritical cycles.
- the drive unit 160 that displaces the passage forming member 151, the enclosed space 162 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 162
- a drive part is not limited to this.
- thermo wax that changes in volume depending on temperature
- a drive unit that includes a shape memory alloy elastic member may be used as the drive unit.
- a member that displaces the passage forming member 151 by an electric mechanism such as an electric motor or a solenoid may be adopted.
Abstract
Description
(第1実施形態)
図1、図2は、第1実施形態のエジェクタ100を蒸気圧縮式冷凍サイクル(以下、冷凍サイクル)10に適用したものを示している。この冷凍サイクル10は、空調装置用として車両に搭載されるものであって、圧縮機11、凝縮器12、エジェクタ100、気液分離器13、貯液部14、および蒸発器16が、冷媒配管によって接続されて形成されている。
(第2実施形態)
第2実施形態の冷凍サイクル10Aを図3、図4に示す。冷凍サイクル10Aは、上記第1実施形態に対して、エジェクタ100と気液分離器13とを一体的に形成したものである。具体的には、図4に示すように、本実施形態のエジェクタ100と気液分離器13は、円筒状の気液分離器13の上部にエジェクタ100が配置されていることによって一体的に形成されている。
(第3実施形態)
第3実施形態の冷凍サイクル10Bを図5に示す。本実施形態では、上記第2実施形態に対して、凝縮器12から流出した液相冷媒を蓄えるレシーバ(受液部)12bを設けている。なお、気液分離器13によって気液二相に分離された冷媒のうち、液相冷媒は、直接、蒸発器16に流出されるようになっている。
(第4実施形態)
第4実施形態の冷凍サイクル10Cを図6、図7に示す。冷凍サイクル10Cは、第2実施形態のように気液分離器13が一体的に形成されたエジェクタ100に対して、さらに、貯液部14を一体的に設けたものである。
(第5実施形態)
本実施形態では、第4実施形態にて説明した気液分離器13および貯液部14を一体的に設けたエジェクタ100を、図8に示す冷凍サイクル10Dに適用し、具体的に図9の断面図に示すように構成した例を説明する。この冷凍サイクル10Dでは、圧縮機11、凝縮器12、エジェクタ100、および蒸発器16が、冷媒配管によって接続されて形成されている。
(他の実施形態)
以上、本開示の好ましい実施形態について説明したが、本開示は上述した実施形態に何ら制限されることなく、本開示の主旨を逸脱しない範囲において種々変形して実施することが可能である。
Claims (13)
- 蒸気圧縮式の冷凍サイクル(10D)に適用されるエジェクタであって、
冷媒を流入させる冷媒流入口(211)と、前記冷媒流入口(211)から流入した冷媒を旋回させる旋回空間(140)と、前記旋回空間(140)から流出した冷媒を減圧させる減圧用空間(202)と、前記減圧用空間(202)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(120)と、前記減圧用空間(202)から噴射された噴射冷媒と前記吸引用通路(120)から吸引された吸引冷媒とを混合させて昇圧させる昇圧用空間(205)とを有するボデー部材(200)と、
前記減圧用空間(202)の内部および前記昇圧用空間(205)の内部に配置される部分を少なくとも有する通路形成部材(151)と、
前記ボデー部材(200)のうち前記減圧用空間(202)を形成する部位の内周面と前記通路形成部材(151)の外周面との間の空間に形成され、前記旋回空間(140)から流出した冷媒を減圧させて噴射するノズル部として機能するノズル通路(110)と、
前記ボデー部材(200)のうち前記昇圧用空間(205)を形成する部位の内周面と前記通路形成部材(151)の外周面との間の空間に形成され、前記噴射冷媒および前記吸引冷媒を混合して昇圧させるディフューザ部として機能するディフューザ通路(130)とを備え、
前記通路形成部材(151)は、前記減圧用空間(202)から離れる方向に断面積が拡大する形状を有するエジェクタ。 - 前記通路形成部材(151)は、前記減圧用空間(202)から離れる方向に断面積が拡大する円錐形状を有しており、
前記ノズル通路(110)、前記吸引用通路(120)および前記ディフューザ通路(130)は、前記通路形成部材(151)の軸方向に垂直な断面における断面形状が環状になっている請求項1に記載のエジェクタ。 - 前記通路形成部材(151)は、前記減圧用空間(202)から離れる方向に断面積が拡大する円錐形状を有しており、
前記ディフューザ通路(130)は、前記通路形成部材(151)の軸方向に垂直な断面において環状の断面形状を有しており、
前記ディフューザ通路(130)を流通する冷媒は、前記旋回空間(140)にて旋回する冷媒と同方向に旋回している請求項1または2に記載のエジェクタ。 - 前記通路形成部材(151)を変位させる駆動部(160)を備え、
前記通路形成部材(151)は、前記減圧用空間(202)から離れるに伴って断面積が拡大する円錐形状を有しており、
前記吸引用通路(120)および前記ディフューザ通路(130)は、前記通路形成部材(151)の軸方向に垂直な断面において環状の断面形状を有しており、
前記吸引用通路(120)は、前記通路形成部材(151)の軸の外周側から内周側へ向かって冷媒が流れる形状を有しており、
前記ディフューザ通路(130)は、前記通路形成部材(151)の軸の内周側から外周側へ向かって冷媒が流れる形状を有しており、
前記吸引用通路(120)および前記ディフューザ通路(130)は前記駆動部(160)の外周に沿って設けられており、
前記駆動部(160)の少なくとも一部は、前記通路形成部材(151)の軸方向において前記吸引用通路(120)および前記ディフューザ通路(130)の間に配置されている請求項1ないし3のいずれか1つに記載のエジェクタ。 - 前記駆動部(160)は、温度変化に伴って圧力変化する感温媒体が封入された封入空間(162)および前記封入空間(162)内の前記感温媒体の圧力に応じて変位する圧力応動部材(161)を有し、
前記圧力応動部材(161)は、前記通路形成部材(151)に連結されており、
前記感温媒体は、前記吸引用通路(120)を流通する冷媒の温度および前記ディフューザ通路(130)を流通する冷媒の温度が伝達されることによって圧力変化するものである請求項4に記載のエジェクタ。 - 前記減圧用空間(202)、前記吸引用通路(120)、前記昇圧用空間(205)、および前記通路形成部材(151)は、いずれも回転体形状で形成されており、互いの軸線が同軸上に配置されている請求項1ないし5のいずれか1つに記載のエジェクタ。
- 前記ボデー部材(200)は、前記ディフューザ通路(130)から流出した冷媒の気液を分離する気液分離空間(206)を有している請求項1ないし6のいずれか1つに記載のエジェクタ。
- 蒸気圧縮式の冷凍サイクル(10、10A~10C)に適用されて、
前記冷凍サイクル(10、10A~10C)の高圧側から流入する高圧冷媒を減圧膨張させるノズル部(110)と、
前記高圧冷媒よりも低圧である低圧冷媒を、前記ノズル部(110)から噴出される噴出冷媒の吸引力によって吸引する吸引部(120)と、
前記ノズル部(110)の下流側に配設されて、断面積が下流側に向けて徐々に拡大する内部流路を有し、前記ノズル部(110)から噴出される前記噴出冷媒と前記吸引部(120)から吸引される前記低圧冷媒とが混合された混合冷媒を減速して圧力上昇させるディフューザ部(130)と、
前記ノズル部(110)の上流側に配設されて、前記高圧冷媒を旋回させ、仮想される旋回中心線の外周側よりも内周側に気相冷媒が多く存在するようにして、気液混相状態の冷媒を前記ノズル部(110)に流入させる旋回空間(140)と、
前記ノズル部(110)と前記ディフューザ部(130)との流路面積を変更可能とする面積可変機構(150)とを備えるエジェクタ。 - 前記高圧冷媒は、液相冷媒である請求項8に記載のエジェクタ。
- 前記面積可変機構(150)は、前記ノズル部(110)と前記ディフューザ部(130)との流路面積を同時に変更可能とする請求項8または9に記載のエジェクタ。
- 前記ディフューザ部(130)の前記内部流路の断面積の拡大率は、下流側に向けて順次大きくなるように設定されており、
前記面積可変機構(150)は、前記ノズル部(110)および前記ディフューザ部(130)の内周面に沿う曲面を有する通路形成部材(151)を備えており、
前記通路形成部材(151)の外周面に沿って設けられる前記ディフューザ部(130)の前記内部流路は、前記ディフューザ部(130)の軸線方向に対して交差する方向に拡がるように設けられている請求項8ないし10のいずれか1つに記載のエジェクタ。 - 前記ディフューザ部(130)から流出される前記混合冷媒の気液を分離する気液分離器(13)を備える請求項8ないし11のいずれか1つに記載のエジェクタ。
- 前記気液分離器(13)によって気液分離された冷媒を溜める貯液部(14)を備え、
前記貯液部(14)は、前記気液分離器(13)と一体的に形成された請求項12に記載のエジェクタ。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/373,862 US9394921B2 (en) | 2012-02-02 | 2013-01-29 | Ejector |
CN201380007138.8A CN104081064B (zh) | 2012-02-02 | 2013-01-29 | 喷射器 |
DE112013000817.3T DE112013000817B4 (de) | 2012-02-02 | 2013-01-29 | Ejektor |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012020882 | 2012-02-02 | ||
JP2012-020882 | 2012-02-02 | ||
JP2012184950A JP5920110B2 (ja) | 2012-02-02 | 2012-08-24 | エジェクタ |
JP2012-184950 | 2012-08-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013114856A1 true WO2013114856A1 (ja) | 2013-08-08 |
Family
ID=48904903
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/000453 WO2013114856A1 (ja) | 2012-02-02 | 2013-01-29 | エジェクタ |
Country Status (5)
Country | Link |
---|---|
US (1) | US9394921B2 (ja) |
JP (1) | JP5920110B2 (ja) |
CN (1) | CN104081064B (ja) |
DE (1) | DE112013000817B4 (ja) |
WO (1) | WO2013114856A1 (ja) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014122779A (ja) * | 2012-11-20 | 2014-07-03 | Denso Corp | エジェクタ |
JP2014206147A (ja) * | 2013-04-16 | 2014-10-30 | 株式会社デンソー | エジェクタ |
WO2015015782A1 (ja) * | 2013-08-01 | 2015-02-05 | 株式会社デンソー | エジェクタ |
WO2015015755A1 (ja) * | 2013-07-31 | 2015-02-05 | 株式会社デンソー | エジェクタ |
WO2015019564A1 (ja) * | 2013-08-09 | 2015-02-12 | 株式会社デンソー | エジェクタ |
WO2015029394A1 (ja) * | 2013-08-29 | 2015-03-05 | 株式会社デンソー | エジェクタ式冷凍サイクルおよびエジェクタ |
CN105579788A (zh) * | 2013-09-23 | 2016-05-11 | 株式会社电装 | 喷射器式制冷循环 |
US20180080482A1 (en) * | 2015-03-09 | 2018-03-22 | Denso Corporation | Ejector and ejector-type refrigeration cycle |
Families Citing this family (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6090104B2 (ja) | 2012-12-13 | 2017-03-08 | 株式会社デンソー | エジェクタ |
JP6119566B2 (ja) | 2012-12-27 | 2017-04-26 | 株式会社デンソー | エジェクタ |
JP5999071B2 (ja) | 2012-12-27 | 2016-09-28 | 株式会社デンソー | エジェクタ |
JP6064862B2 (ja) * | 2013-01-11 | 2017-01-25 | 株式会社デンソー | エジェクタ |
JP5949641B2 (ja) * | 2013-04-05 | 2016-07-13 | 株式会社デンソー | エジェクタ |
JP6119489B2 (ja) | 2013-07-30 | 2017-04-26 | 株式会社デンソー | エジェクタ |
JP6011484B2 (ja) * | 2013-07-31 | 2016-10-19 | 株式会社デンソー | エジェクタ |
JP6048339B2 (ja) | 2013-08-01 | 2016-12-21 | 株式会社デンソー | エジェクタ |
JP2015137566A (ja) * | 2014-01-21 | 2015-07-30 | 株式会社デンソー | エジェクタ |
JP6176127B2 (ja) * | 2014-01-21 | 2017-08-09 | 株式会社デンソー | エジェクタ |
JP6191491B2 (ja) * | 2014-02-07 | 2017-09-06 | 株式会社デンソー | エジェクタ |
JP2016035376A (ja) * | 2014-08-04 | 2016-03-17 | 株式会社デンソー | 蒸発器 |
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 |
JP2016050761A (ja) * | 2014-08-28 | 2016-04-11 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP2016048156A (ja) * | 2014-08-28 | 2016-04-07 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP6459807B2 (ja) | 2014-08-28 | 2019-01-30 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP6327088B2 (ja) * | 2014-09-29 | 2018-05-23 | 株式会社デンソー | エジェクタ式冷凍サイクル |
GR20140100517A (el) * | 2014-10-13 | 2016-06-01 | Εμμανουηλ Αριστειδη Δερμιτζακης | Υβριδικος διανεμητης και μεθοδος ενσωματωσης σταλακτων και εξαρτηματων σε αρδευτικο αγωγο |
JP2016084966A (ja) * | 2014-10-24 | 2016-05-19 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP6319043B2 (ja) | 2014-10-24 | 2018-05-09 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP6319042B2 (ja) * | 2014-10-24 | 2018-05-09 | 株式会社デンソー | エジェクタ式冷凍サイクル |
JP6319041B2 (ja) * | 2014-10-24 | 2018-05-09 | 株式会社デンソー | エジェクタ式冷凍サイクル |
KR102303676B1 (ko) * | 2014-12-30 | 2021-09-23 | 삼성전자주식회사 | 이젝터 및 이를 갖는 냉동장치 |
JP2016142189A (ja) * | 2015-02-03 | 2016-08-08 | 株式会社デンソー | エジェクタ |
JP6610313B2 (ja) | 2015-03-09 | 2019-11-27 | 株式会社デンソー | エジェクタ、エジェクタの製造方法、およびエジェクタ式冷凍サイクル |
JP6398802B2 (ja) | 2015-03-09 | 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 |
JP6384374B2 (ja) | 2015-03-23 | 2018-09-05 | 株式会社デンソー | エジェクタ式冷凍サイクル |
KR102379642B1 (ko) * | 2015-10-12 | 2022-03-28 | 삼성전자주식회사 | 선회류를 이용한 이젝터 |
JP6481678B2 (ja) * | 2016-02-02 | 2019-03-13 | 株式会社デンソー | エジェクタ |
WO2017135093A1 (ja) * | 2016-02-02 | 2017-08-10 | 株式会社デンソー | エジェクタ |
WO2017135092A1 (ja) * | 2016-02-02 | 2017-08-10 | 株式会社デンソー | エジェクタ |
JP6481679B2 (ja) * | 2016-02-02 | 2019-03-13 | 株式会社デンソー | エジェクタ |
JP2017190707A (ja) * | 2016-04-13 | 2017-10-19 | 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 |
JP6638607B2 (ja) * | 2016-09-12 | 2020-01-29 | 株式会社デンソー | エジェクタ |
JP2018044442A (ja) * | 2016-09-12 | 2018-03-22 | 株式会社デンソー | エジェクタ |
DE102017215085A1 (de) * | 2017-08-29 | 2019-02-28 | Efficient Energy Gmbh | Wärmepumpe mit einer Kühlvorrichtung zum Kühlen eines Leitraums oder eines Saugmunds |
JP7353275B2 (ja) | 2017-09-25 | 2023-09-29 | ジョンソン コントロールズ テクノロジー カンパニー | 2段階の油原動力エダクタシステム |
DE102019126302A1 (de) * | 2019-09-30 | 2021-04-01 | Audi Ag | Ejektor sowie Brennstoffzellensystem und Kraftfahrzeug mit einem solchen |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59123700U (ja) * | 1983-02-10 | 1984-08-20 | 株式会社日立製作所 | エジエクタ− |
JPS6176800A (ja) * | 1984-09-25 | 1986-04-19 | Sakou Giken:Kk | 蒸気エゼクタ− |
JPH01250000A (ja) * | 1988-03-30 | 1989-10-05 | Kobe Steel Ltd | エジェクター装置 |
JP2002333000A (ja) * | 2001-05-11 | 2002-11-22 | Nkk Corp | エジェクタおよび冷凍システム |
JP2003336915A (ja) * | 2002-05-20 | 2003-11-28 | Nippon Soken Inc | エジェクタ方式の減圧装置 |
JP2008008599A (ja) * | 2006-06-30 | 2008-01-17 | Denso Corp | 気液二相流体の分配器 |
JP2009144607A (ja) * | 2007-12-14 | 2009-07-02 | Tlv Co Ltd | 蒸気エゼクタ |
JP2010181136A (ja) * | 2009-01-12 | 2010-08-19 | Denso Corp | 蒸発器ユニット |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58104767A (ja) | 1981-12-16 | 1983-06-22 | Matsushita Electric Ind Co Ltd | 磁性流動体記録装置 |
JP3331604B2 (ja) | 1991-11-27 | 2002-10-07 | 株式会社デンソー | 冷凍サイクル装置 |
US5343711A (en) | 1993-01-04 | 1994-09-06 | Virginia Tech Intellectual Properties, Inc. | Method of reducing flow metastability in an ejector nozzle |
JPH11257299A (ja) | 1998-03-13 | 1999-09-21 | Daikin Ind Ltd | 抽気用エジェクタ |
JP3322263B1 (ja) | 2000-03-15 | 2002-09-09 | 株式会社デンソー | エジェクタサイクル、これに用いる気液分離器、並びにこのエジェクタサイクルを用いた給湯器及び熱管理システム |
EP1589301B1 (en) | 2000-03-15 | 2017-06-14 | Denso Corporation | Ejector cycle system with critical refrigerant pressure |
JP2003014318A (ja) | 2000-06-01 | 2003-01-15 | Denso Corp | エジェクタサイクル |
AU758419B2 (en) | 2000-06-01 | 2003-03-20 | Denso Corporation | Ejector cycle system |
AU2001270167A1 (en) * | 2000-06-30 | 2002-01-14 | Fmc Corporation | Steam injection heater and method |
JP3966157B2 (ja) * | 2002-10-25 | 2007-08-29 | 株式会社デンソー | エジェクタ |
JP4232484B2 (ja) * | 2003-03-05 | 2009-03-04 | 株式会社日本自動車部品総合研究所 | エジェクタおよび蒸気圧縮式冷凍機 |
JP2006170051A (ja) * | 2004-12-15 | 2006-06-29 | Tlv Co Ltd | エゼクタ |
JP4306739B2 (ja) | 2007-02-16 | 2009-08-05 | 三菱電機株式会社 | 冷凍サイクル装置 |
JP4812665B2 (ja) * | 2007-03-16 | 2011-11-09 | 三菱電機株式会社 | エジェクタ及び冷凍サイクル装置 |
US7922161B2 (en) | 2007-06-19 | 2011-04-12 | Kabushiki Kaisha Toshiba | Sheet finisher, image forming apparatus using the same, and sheet finishing method |
IL187911A0 (en) * | 2007-12-05 | 2008-11-03 | Bron Dan | An automatic vacuum pump |
DE102008016056A1 (de) * | 2008-03-28 | 2009-10-01 | Voith Patent Gmbh | Strahlpumpe zum Fördern von Arbeitsmedium in einem Arbeitsmediumkreislauf einer hydrodynamischen Maschine |
JP5182159B2 (ja) | 2009-03-06 | 2013-04-10 | 株式会社デンソー | エジェクタ方式の減圧装置およびこれを備えた冷凍サイクル |
JP5316465B2 (ja) * | 2010-04-05 | 2013-10-16 | 株式会社デンソー | 蒸発器ユニット |
JP5816890B2 (ja) | 2011-03-03 | 2015-11-18 | 株式会社 カロリアジャパン | 汚泥の分析要素量測定方法及び汚泥の分析要素量測定装置 |
-
2012
- 2012-08-24 JP JP2012184950A patent/JP5920110B2/ja not_active Expired - Fee Related
-
2013
- 2013-01-29 US US14/373,862 patent/US9394921B2/en active Active
- 2013-01-29 CN CN201380007138.8A patent/CN104081064B/zh not_active Expired - Fee Related
- 2013-01-29 WO PCT/JP2013/000453 patent/WO2013114856A1/ja active Application Filing
- 2013-01-29 DE DE112013000817.3T patent/DE112013000817B4/de not_active Expired - Fee Related
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59123700U (ja) * | 1983-02-10 | 1984-08-20 | 株式会社日立製作所 | エジエクタ− |
JPS6176800A (ja) * | 1984-09-25 | 1986-04-19 | Sakou Giken:Kk | 蒸気エゼクタ− |
JPH01250000A (ja) * | 1988-03-30 | 1989-10-05 | Kobe Steel Ltd | エジェクター装置 |
JP2002333000A (ja) * | 2001-05-11 | 2002-11-22 | Nkk Corp | エジェクタおよび冷凍システム |
JP2003336915A (ja) * | 2002-05-20 | 2003-11-28 | Nippon Soken Inc | エジェクタ方式の減圧装置 |
JP2008008599A (ja) * | 2006-06-30 | 2008-01-17 | Denso Corp | 気液二相流体の分配器 |
JP2009144607A (ja) * | 2007-12-14 | 2009-07-02 | Tlv Co Ltd | 蒸気エゼクタ |
JP2010181136A (ja) * | 2009-01-12 | 2010-08-19 | Denso Corp | 蒸発器ユニット |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014122779A (ja) * | 2012-11-20 | 2014-07-03 | Denso Corp | エジェクタ |
JP2014206147A (ja) * | 2013-04-16 | 2014-10-30 | 株式会社デンソー | エジェクタ |
WO2015015755A1 (ja) * | 2013-07-31 | 2015-02-05 | 株式会社デンソー | エジェクタ |
JP2015031404A (ja) * | 2013-07-31 | 2015-02-16 | 株式会社デンソー | エジェクタ |
WO2015015782A1 (ja) * | 2013-08-01 | 2015-02-05 | 株式会社デンソー | エジェクタ |
US10344777B2 (en) | 2013-08-01 | 2019-07-09 | Denso Corporation | Ejector with temperature-sensitive drive device |
US9816738B2 (en) | 2013-08-09 | 2017-11-14 | Denso Corporation | Ejector |
CN105492778A (zh) * | 2013-08-09 | 2016-04-13 | 株式会社电装 | 喷射器 |
JP2015034672A (ja) * | 2013-08-09 | 2015-02-19 | 株式会社デンソー | エジェクタ |
WO2015019564A1 (ja) * | 2013-08-09 | 2015-02-12 | 株式会社デンソー | エジェクタ |
WO2015029394A1 (ja) * | 2013-08-29 | 2015-03-05 | 株式会社デンソー | エジェクタ式冷凍サイクルおよびエジェクタ |
JP2015045477A (ja) * | 2013-08-29 | 2015-03-12 | 株式会社デンソー | エジェクタ式冷凍サイクルおよびエジェクタ |
CN105492841A (zh) * | 2013-08-29 | 2016-04-13 | 株式会社电装 | 喷射器式制冷循环以及喷射器 |
US10465957B2 (en) | 2013-08-29 | 2019-11-05 | Denso Corporation | Ejector-type refrigeration cycle, and ejector |
CN105579788A (zh) * | 2013-09-23 | 2016-05-11 | 株式会社电装 | 喷射器式制冷循环 |
US20180080482A1 (en) * | 2015-03-09 | 2018-03-22 | Denso Corporation | Ejector and ejector-type refrigeration cycle |
US10935051B2 (en) * | 2015-03-09 | 2021-03-02 | Denso Corporation | Ejector and ejector-type refrigeration cycle |
Also Published As
Publication number | Publication date |
---|---|
DE112013000817T5 (de) | 2014-12-04 |
JP2013177879A (ja) | 2013-09-09 |
CN104081064B (zh) | 2016-08-24 |
US9394921B2 (en) | 2016-07-19 |
DE112013000817B4 (de) | 2019-05-09 |
JP5920110B2 (ja) | 2016-05-18 |
US20150033790A1 (en) | 2015-02-05 |
CN104081064A (zh) | 2014-10-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5920110B2 (ja) | エジェクタ | |
US7334427B2 (en) | Ejector with tapered nozzle and tapered needle | |
JP6052156B2 (ja) | エジェクタ | |
JP6048339B2 (ja) | エジェクタ | |
WO2015015752A1 (ja) | エジェクタ | |
WO2014103276A1 (ja) | エジェクタ | |
JP5962571B2 (ja) | エジェクタ | |
WO2014091701A1 (ja) | エジェクタ | |
WO2014010162A1 (ja) | エジェクタ | |
JP5929814B2 (ja) | エジェクタ | |
WO2014108974A1 (ja) | エジェクタ | |
WO2014080596A1 (ja) | エジェクタ | |
JP6176127B2 (ja) | エジェクタ | |
WO2015111113A1 (ja) | エジェクタ | |
WO2014185069A1 (ja) | エジェクタ | |
JP6512071B2 (ja) | エジェクタ式冷凍サイクル | |
WO2017135093A1 (ja) | エジェクタ | |
WO2017135092A1 (ja) | エジェクタ | |
JP6511873B2 (ja) | エジェクタ、およびエジェクタ式冷凍サイクル | |
WO2016185664A1 (ja) | エジェクタ、およびエジェクタ式冷凍サイクル | |
JP6485550B2 (ja) | エジェクタ | |
JP6481679B2 (ja) | エジェクタ | |
WO2015015755A1 (ja) | エジェクタ | |
JP6500697B2 (ja) | エジェクタ | |
JP6481678B2 (ja) | エジェクタ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13743083 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14373862 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112013000817 Country of ref document: DE Ref document number: 1120130008173 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 13743083 Country of ref document: EP Kind code of ref document: A1 |