WO2017135093A1 - Ejector - Google Patents

Ejector Download PDF

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Publication number
WO2017135093A1
WO2017135093A1 PCT/JP2017/002204 JP2017002204W WO2017135093A1 WO 2017135093 A1 WO2017135093 A1 WO 2017135093A1 JP 2017002204 W JP2017002204 W JP 2017002204W WO 2017135093 A1 WO2017135093 A1 WO 2017135093A1
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WO
WIPO (PCT)
Prior art keywords
passage
refrigerant
forming member
ejector
space
Prior art date
Application number
PCT/JP2017/002204
Other languages
French (fr)
Japanese (ja)
Inventor
西嶋 春幸
高野 義昭
佳之 横山
押谷 洋
陽平 長野
中嶋 亮太
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016248885A external-priority patent/JP6481678B2/en
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112017000625.2T priority Critical patent/DE112017000625B4/en
Priority to US16/073,824 priority patent/US11053956B2/en
Priority to CN201780008954.9A priority patent/CN108603519B/en
Publication of WO2017135093A1 publication Critical patent/WO2017135093A1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/02Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
    • F04F5/04Jet 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46Arrangements of nozzles
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04FPUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/48Control

Definitions

  • the present application includes Japanese Patent Application 2016-018067 filed on February 2, 2016 and Japanese Patent Application 2016- filed on December 22, 2016, the disclosures of which are incorporated herein by reference. Based on 248885.
  • the present 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.
  • Patent Document 1 discloses an ejector applied to a vapor compression refrigeration cycle apparatus.
  • coolant suction port formed in the body is attracted
  • coolant is attracted
  • coolant coolant.
  • the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant that is, the evaporator outlet side refrigerant
  • a passage forming member which is a substantially conical valve body, is disposed inside the body, and a cross-sectional circle is formed between the inner side surface of the body and the conical side surface of the passage forming member.
  • An annular refrigerant passage is formed.
  • a portion on the most upstream side of the refrigerant flow is used as a nozzle passage, and a portion on the downstream side of the refrigerant flow in the nozzle passage is used as a diffuser passage.
  • the body of the ejector of Patent Document 1 is formed with a swirling space for swirling the refrigerant flowing into the nozzle passage around the central axis of the passage forming member.
  • this swirling space the liquid-phase refrigerant that has flowed out of the radiator is swirled, whereby the swirling center side refrigerant is boiled under reduced pressure.
  • coolant (henceforth an air column) in the turning center side is made to flow in into a nozzle channel
  • the ejector disclosed in Patent Document 1 promotes boiling of the refrigerant in the nozzle passage, and attempts to improve energy conversion efficiency when the pressure energy of the refrigerant is converted into kinetic energy in the nozzle passage.
  • the energy conversion efficiency hereinafter referred to as ejector efficiency
  • the ejector of Patent Document 1 includes a drive mechanism that changes the passage cross-sectional area of the refrigerant passage by displacing the passage formation member.
  • a drive mechanism that changes the passage cross-sectional area of the refrigerant passage by displacing the passage formation member.
  • Patent Document 1 when the ejector of Patent Document 1 is applied to a refrigeration cycle apparatus that employs refrigerants having different physical properties, the amount of refrigerant necessary for causing the refrigeration cycle apparatus to exhibit a desired refrigeration capacity changes. Therefore, even if refrigerants with different physical properties are swirled in the same swirling space, an appropriate air column cannot be stably generated, and energy conversion efficiency in the nozzle passage cannot be improved. End up.
  • the jet refrigerant injected at a supersonic speed from the nozzle passage has a velocity component in the swirl direction. For this reason, an oblique shock wave generated in the jet refrigerant is also generated along the swirl flow, and the velocity component in the swirl direction of the jet refrigerant is accelerated. As a result, the speed difference between the flow rate of the injected refrigerant and the flow rate of the suction refrigerant increases, and energy loss (hereinafter referred to as mixing loss) when mixing the injected refrigerant and the suction refrigerant is likely to increase.
  • mixing loss energy loss
  • the ejector of Patent Document 1 includes a passage forming member, and the refrigerant outlet of the suction passage is opened in an annular shape on the outer peripheral side of the refrigerant injection port of the nozzle passage. For this reason, in the ejector of Patent Document 1, it is difficult to sufficiently reduce the mixing loss even if the suction refrigerant is merely accelerated to reduce the speed difference.
  • an ejector applied to a vapor compression refrigeration cycle apparatus includes a body, a passage forming member, and a drive mechanism.
  • the body includes an inflow space into which liquid phase refrigerant flows, a decompression space for decompressing the refrigerant flowing out of the inflow space, and a suction passage for communicating the refrigerant sucked from the refrigerant suction port in communication with the refrigerant flow downstream side of the decompression space.
  • a pressure increasing space for allowing the jetted refrigerant injected from the pressure reducing space and the suctioned refrigerant sucked through the suction passage to flow in.
  • At least a part of the passage forming member is disposed inside the decompression space and forms a refrigerant passage between the passage forming member and the body.
  • the drive mechanism displaces the passage forming member.
  • 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 functions as a nozzle that decompresses and injects the refrigerant.
  • An upstream operating rod that extends toward the inflow space and is slidably supported by the body is connected to the passage forming member.
  • the central axis of the inflow space, the central axis of the upstream operating rod, and the central axis of the passage forming member are arranged coaxially.
  • the drive mechanism displaces the passage forming member, the passage sectional area of the nozzle passage can be adjusted according to the load fluctuation of the applied refrigeration cycle apparatus.
  • the upstream operating rod extends toward the inflow space and the central axis of the upstream operating rod and the central axis of the inflow space are coaxially arranged, it is difficult for the refrigerant in the inflow space to generate a swirling flow. It can be set as the structure which an air column does not generate
  • the refrigerant passage may be a diffuser passage that functions as a pressure increasing unit that increases the pressure by mixing the injected refrigerant and the suction refrigerant.
  • the cross-sectional area of the diffuser passage can be adjusted according to the load fluctuation of the applied refrigeration cycle apparatus. Therefore, high energy conversion efficiency can be more stably exhibited regardless of the load fluctuation of the applied refrigeration cycle apparatus.
  • a downstream operating rod that extends downstream from the diffuser passage and is slidably supported by the body may be connected to the passage forming member. According to this, since the passage forming member can be supported on both ends of the central axis by the upstream side operating rod and the downstream side operating rod, the central axis of the passage forming member is more reliably inclined. Can be suppressed.
  • FIG. 3 is a cross-sectional view taken along the line III-III in FIG. It is typical sectional drawing of the IV section of FIG. It is a Mollier diagram which shows the change of the state of the refrigerant
  • FIGS. 1-8 1st Embodiment of this indication is described using FIGS. 1-8.
  • 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 the blown air blown into the vehicle interior, which is the air-conditioning target space. Therefore, the cooling target fluid of the ejector refrigeration cycle 10 of the present embodiment is blown air.
  • the ejector refrigeration cycle 10 of the present embodiment employs an HFO refrigerant (specifically, R1234yf) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. is doing.
  • This refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
  • the compressor 11 sucks refrigerant and discharges it until it becomes high-pressure refrigerant.
  • the compressor 11 is disposed in an engine room together with an engine (internal combustion engine) that outputs a driving force for vehicle travel. Further, the compressor 11 is an engine-driven compressor that is driven by a rotational driving force output from the engine via a pulley, a belt, or the like.
  • a swash plate type variable displacement compressor configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity is adopted as the compressor 11.
  • the compressor 11 has a discharge capacity control valve (not shown) for changing the discharge capacity.
  • the operation of the discharge capacity control valve is controlled by a control current output from a control device described later.
  • 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 the outside air (outside air) blown by the cooling fan 12d. .
  • the radiator 12 is arranged on the vehicle front side in the engine room.
  • the radiator 12 is configured as a so-called subcool type condenser having a condensing unit 12a, a receiver unit 12b, and a supercooling unit 12c.
  • the condensing unit 12a is a heat exchange unit for condensation that exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d, and dissipates the high-pressure gas-phase refrigerant to condense.
  • the receiver unit 12b is a refrigerant container that separates the gas-liquid refrigerant flowing out from the condensing unit 12a and stores excess liquid-phase refrigerant.
  • the supercooling unit 12c is a heat exchange unit for supercooling that heat-exchanges the liquid refrigerant flowing out from 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 (that is, 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 refrigerant that has flowed out of the radiator 12 and flows it downstream. Further, the ejector 13 has a function as a refrigerant transporting device that sucks and transports a refrigerant (that is, an outlet side refrigerant of the evaporator 14) that flows out from the evaporator 14 (described later) by the suction action of the jetted refrigerant that is injected at a high speed. Fulfill.
  • a refrigerant that is, an outlet side refrigerant of the evaporator 14
  • the ejector 13 of the present embodiment also has a function as a gas-liquid separator that separates the gas-liquid of the decompressed refrigerant.
  • the ejector 13 of the present embodiment is configured as an ejector with a gas-liquid separation function in which the ejector and the gas-liquid separator are integrated (that is, modularized).
  • the ejector 13 is disposed in the engine room together with the compressor 11 and the radiator 12.
  • the up and down arrows in FIG. 1 indicate the up and down directions in a state where the ejector 13 is mounted on the vehicle, and the up and down arrows in the state where other components of the ejector refrigeration cycle 10 are mounted on the vehicle. Each direction is not limited to this.
  • FIGS. 2 and 3 are axial sectional views of the ejector 13, FIG. 2 is a sectional view taken along the line II-II in FIG. 3, and FIG. 3 is a sectional view taken along the line III-III in FIG.
  • FIG. 4 is a schematic partially enlarged cross-sectional view for explaining the refrigerant passage formed inside the ejector 13, and parts having the same functions as those in FIGS. 2 and 3 have the same reference numerals. Is attached.
  • the ejector 13 of the present embodiment includes a body 30 formed by combining a plurality of constituent members as shown in FIGS.
  • the body 30 includes an upper body 311, a lower body 312, a gas-liquid separation body 313, and the like.
  • Each of these bodies 311 to 313 functions as a housing that forms an outer shell of the ejector 13 and accommodates other constituent members therein.
  • the housing bodies 311 to 313 are formed of a hollow member made of metal (in this embodiment, made of an aluminum alloy).
  • the housing bodies 311 to 313 may be made of resin.
  • constituent members of the body 30 such as a nozzle 32 and a diffuser body 33 described later are fixed.
  • the upper body 311 is formed with a plurality of refrigerant inlets such as a refrigerant inlet 31a and a refrigerant suction port 31b.
  • the refrigerant inlet 31a is a refrigerant inlet through which the refrigerant that has flowed out of the radiator 12 flows.
  • the refrigerant suction port 31b is a refrigerant inflow port that sucks the refrigerant that has flowed out of the evaporator 14.
  • the gas-liquid separation body 313 is formed with a plurality of refrigerant inflow / outflow ports such as a liquid phase refrigerant outflow port 31c and a gas phase refrigerant outflow port 31d.
  • the liquid-phase refrigerant outlet 31 c is a refrigerant outlet that allows the liquid-phase refrigerant separated in the gas-liquid separation space 30 f formed in the gas-liquid separation body 313 to flow out to the refrigerant inlet side of the evaporator 14.
  • the gas-phase refrigerant outlet 31d is a refrigerant outlet through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out to the suction port side of the compressor 11.
  • the nozzle 32 is formed of a cylindrical member made of metal (in this embodiment, stainless steel). As shown in FIGS. 2 and 3, the nozzle 32 is disposed on the bottom surface of one end side in the axial direction of the upper body 311 (opposite side of the lower body 312). The nozzle 32 is fixed by being press-fitted into a hole formed in the upper body 311, and the refrigerant does not leak from the gap between the upper body 311 and the nozzle 32.
  • an inflow space 30a for allowing the refrigerant that has flowed in from the refrigerant inflow port 31a to flow is formed.
  • the inflow space 30a is formed in a substantially cylindrical rotating body shape.
  • a central axis of the inflow space 30a is arranged coaxially with a central axis CL of a passage forming member 35 described later.
  • the central axis CL of the present embodiment extends in a substantially horizontal direction.
  • the rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (center axis) on the same plane.
  • the upper body 311 is formed with a refrigerant inflow passage 31e that guides the refrigerant flowing in from the refrigerant inflow port 31a to the inflow space 30a side.
  • the refrigerant inflow passage 31e is formed in a shape extending in the radial direction when viewed from the central axis direction of the inflow space 30a, and causes the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a. Is formed.
  • a decompression space 30b is formed on the downstream side of the refrigerant flow in the inflow space 30a to depressurize the refrigerant that has flowed out of the inflow space 30a and flow out to the downstream side.
  • the decompression space 30b is formed in a rotating body shape in which the top sides of two frustoconical spaces are joined together.
  • the central axis of the decompression space 30b is also arranged coaxially with the central axis CL of the passage forming member 35.
  • the passage forming member 35 is a valve body portion arranged in a refrigerant passage formed inside the body 30.
  • the passage forming member 35 functions to change the passage sectional area of the refrigerant passage by being displaced in the direction of the central axis CL.
  • the passage forming member 35 is formed of a conical member made of resin (in this embodiment, nylon 6 or nylon 66) that is resistant to the refrigerant.
  • the passage forming member 35 is formed in a conical shape in which the outer diameter increases as the distance from the decompression space 30b increases (that is, toward the downstream side of the refrigerant flow).
  • a substantially frustoconical space is formed inside the passage forming member 35 from the bottom surface side. That is, the passage forming member 35 is formed in a cup shape (that is, a cup shape). Further, a shaft 351 is connected to the passage forming member 35.
  • the shaft 351 is formed of a cylindrical rod-shaped member made of metal (in this embodiment, stainless steel). The central axis of the shaft 351 is disposed coaxially with the central axis CL of the passage forming member 35.
  • the shaft 351 is insert-molded in the passage forming member 35. Thereby, the channel
  • the upstream operating rod 351a extends from the top of the passage forming member 35 so as to penetrate the inflow space 30a, and is slidably supported in the bearing hole of the upper body 311.
  • the downstream operation rod 351b extends from the top of the passage forming member 35 toward the downstream side of a diffuser passage 13c described later, and is slidably supported in a bearing hole of a support member 36 provided in the lower body 312. Yes. That is, the shaft 351 is slidably supported by the body 30 at both axial ends.
  • the support member 36 is formed of a cylindrical member made of metal (in this embodiment, an aluminum alloy), and is fixed to the lower body 312 via a fixing member (not shown). Furthermore, a coil spring 36a that applies a load toward the inflow space 30a with respect to the downstream operation rod 351b is accommodated inside the support member 36. The load of the coil spring 36 a can be adjusted by an adjustment screw provided on the support member 36.
  • the leading end of the upstream operating rod 351a on the inflow space 30a side is connected to the drive mechanism 37.
  • the drive mechanism 37 outputs a driving force for displacing the shaft 351 and the passage forming member 35 in the axial direction. Details of the drive mechanism 37 will be described later.
  • This refrigerant passage is a nozzle passage 13a that functions as a nozzle for depressurizing and injecting the refrigerant.
  • the nozzle passage 13a is formed in an annular shape (a shape excluding a small-diameter circular shape arranged coaxially from a circular shape) in a vertical cross section in the axial direction. As shown in FIG. 4, the nozzle passage 13 a is formed with a tapered portion 131 and a divergent portion 132.
  • the tapered portion 131 is formed on the upstream side of the refrigerant flow with respect to the minimum passage area portion 30m having the smallest passage cross-sectional area in the nozzle passage 13a, and the passage cross-sectional area up to the minimum passage area portion 30m is gradually reduced. It is a refrigerant passage.
  • the divergent portion 132 is a refrigerant passage that is formed on the downstream side of the refrigerant flow from the minimum passage area portion 30m, and the passage cross-sectional area gradually increases.
  • the passage cross-sectional area changes like the Laval nozzle.
  • the pressure of the refrigerant is reduced and the flow rate of the refrigerant is increased to be supersonic and injected.
  • a diffuser body 33 is arranged on the downstream side of the refrigerant flow from the nozzle 32 inside the upper body 311.
  • the diffuser body 33 is formed of a cylindrical member made of metal (in this embodiment, aluminum alloy).
  • the diffuser body 33 may be divided into a plurality of members so that the refrigerant injection port 13e side of the nozzle 32 can be accommodated in a through hole 33a formed inside.
  • the diffuser body 33 is fixed to the upper body 311 by press-fitting the outer peripheral side thereof to the inner peripheral side surface of the upper body 311. Note that an O-ring as a sealing member (not shown) is arranged between the diffuser body 33 and the upper body 311 so that the refrigerant does not leak from the gap between these members.
  • a through hole 33a penetrating in the axial direction is formed.
  • the through hole 33 a is formed in a substantially truncated cone-shaped rotating body shape, and its central axis is arranged coaxially with the central axis CL of the passage forming member 35.
  • coolant injection port 13e of the nozzle 32 is extended to the inside of the through-hole 33a of the diffuser body 33.
  • coolant suction port 31b of the pressure reduction space 30b (namely, nozzle passage 13a).
  • a suction passage 13b leading to the downstream side of the refrigerant flow is formed.
  • the suction refrigerant outlet 13f which is the most downstream portion of the suction passage 13b opens in an annular shape on the outer peripheral side of the refrigerant injection port 13e.
  • a pressure increasing space 30e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction is formed.
  • the pressurizing space 30e is a space into which the injection refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the suction passage 13b flow.
  • the lower side of the passage forming member 35 is disposed inside the pressurizing space 30e.
  • a mixing passage 13d and a diffuser passage 13c are formed between the inner peripheral surface of the diffuser body 33 forming the pressurizing space 30e and the lower outer peripheral surface of the passage forming member 35.
  • the mixing passage 13d is a refrigerant passage for mixing the injection refrigerant and the suction refrigerant.
  • the diffuser passage 13c is a refrigerant passage that pressurizes the mixed refrigerant of the injection refrigerant and the suction refrigerant.
  • the mixing passage 13d is disposed upstream of the refrigerant flow in the diffuser passage 13c.
  • the mixing passage 13d is formed in a shape in which the passage cross-sectional area gradually decreases toward the downstream side of the refrigerant flow.
  • the line drawn in the axial cross section including the central axis CL of the wall surface forming the mixing passage 13d in the diffuser body 33 is the passage forming member 35 side toward the refrigerant flow downstream side. Inclined to approach. Thereby, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow.
  • the minimum passage sectional area of the mixing passage 13d is formed smaller than the total value of the passage sectional area of the refrigerant injection port 13e and the passage sectional area of the suction refrigerant outlet 13f.
  • the diffuser passage 13c is formed in a shape that gradually increases the cross-sectional area of the passage toward the downstream side of the refrigerant flow. Thereby, the velocity energy of the mixed refrigerant can be converted into pressure energy in the diffuser passage 13c. Therefore, the diffuser passage 13c functions as a diffuser part (a boosting part).
  • the mixing passage 13d and the diffuser passage 13c are both formed in an annular shape in cross section perpendicular to the central axis.
  • the nozzle passage 13 a is formed in a range where a line segment extending in the normal direction from the outer peripheral surface of the passage forming member 35 intersects a portion of the nozzle 32 that forms the decompression space 30 b. It may be defined as a refrigerant passage.
  • the diffuser passage 13c may be defined as a refrigerant passage formed in a range where a line segment extending in the normal direction from the outer peripheral surface of the passage forming member 35 intersects a portion of the diffuser body 33 that forms the pressure increasing space 30e.
  • the suction refrigerant outlet 13f of the suction passage 13b in the cross-sectional view of FIG. 4 is a line segment extending in the normal direction of the outer peripheral surface of the passage forming member 35, and extends from the tip of the refrigerant injection port 13e of the nozzle 32 to the diffuser body 33. It may be defined by a line segment leading to.
  • the mixing passage 13d may be defined as a refrigerant passage connecting the nozzle passage 13a, the suction passage 13b, and the diffuser passage 13c. Furthermore, the minimum passage sectional area of the mixing passage 13d is a passage sectional area in the most downstream portion of the refrigerant flow in the mixing passage 13d (that is, the most upstream portion of the refrigerant flow in the diffuser passage 13c).
  • the nozzle passage 13a, the suction passage 13b, the diffuser passage 13c, and the mixing passage 13d are formed on the outer peripheral surface of the passage forming member 35 and the inner peripheral surface of the body 30 (specifically, the nozzle 32 and the diffuser body 33). Is formed between.
  • the refrigerant flows toward the downstream side.
  • the radial width (flow passage width) of each passage can be increased or decreased toward the downstream side of the refrigerant flow.
  • the drive mechanism 37 changes the refrigerant passage cross-sectional area such as the minimum passage area portion 30m of the nozzle passage 13a by displacing the passage forming member 35. As shown in FIGS. 2 and 3, the drive mechanism 37 is disposed outside the upper body 311 and on an axial extension line of the upstream operation rod 351a.
  • the drive mechanism 37 includes a diaphragm 371, an upper cover 372, a lower cover 373, and the like.
  • the upper cover 372 is a sealed space forming member that forms a part of the sealed space 37a together with the diaphragm 371.
  • the upper cover 372 is a cup-shaped member formed of metal (in this embodiment, stainless steel).
  • the enclosed space 37a is a space in which a temperature-sensitive medium whose pressure changes with temperature change is enclosed. More specifically, the enclosed space 37a is a space in which a temperature-sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed so as to have a predetermined enclosure density.
  • a medium mainly composed of R1234yf (for example, a mixed medium of R1234yf and helium) can be employed as the temperature sensitive medium of the present embodiment. Further, the density of the temperature sensitive medium is set so that the passage forming member 35 can be appropriately displaced during the normal operation of the cycle, as will be described later.
  • the lower cover 373 is an introduction space forming member that forms the introduction space 37b together with the diaphragm 371.
  • the lower cover 373 is formed of the same metal member as the upper cover 372.
  • the introduction space 37b is a space for introducing the suction refrigerant sucked from the refrigerant suction port 31b through a communication path (not shown).
  • the outer peripheral edges of the upper cover 372 and the lower cover 373 are fixed by caulking or the like. Further, the outer peripheral side edge of the diaphragm 371 is sandwiched between the upper cover 372 and the lower cover 373. Thereby, the diaphragm 371 partitions the space formed between the upper cover 372 and the lower cover 373 into an enclosed space 37a and an introduction space 37b.
  • the diaphragm 371 is a pressure responsive member that is displaced according to the pressure difference between the internal pressure of the enclosed space 37a and the pressure of the suction refrigerant flowing through the suction passage 13b. Accordingly, it is desirable that the diaphragm 371 is made of a material that is rich in elasticity and excellent in pressure resistance and airtightness.
  • a metal thin plate made of stainless steel (SUS304) is adopted as the diaphragm 371.
  • gum base materials such as EPDM (ethylene propylene diene rubber) and HNBR (hydrogenated nitrile rubber) containing base fabric (polyester).
  • a disk-shaped plate member 374 made of metal (in this embodiment, an aluminum alloy) is disposed on the introduction space 37b side of the diaphragm 371.
  • the plate member 374 is arranged so as to contact the diaphragm 371. Further, the tip end portion of the upstream operation rod 351a is coupled to the plate member 374. Therefore, the shaft 351 and the passage forming member 35 of the present embodiment are displaced so that the total load of the load received from the drive mechanism 37 (specifically, the diaphragm 371) and the load received from the coil spring 36a is balanced.
  • the passage forming member 35 is displaced in a direction of reducing the passage cross-sectional area in the minimum passage area portion 30m.
  • the drive mechanism 37 of this embodiment is configured by a mechanical mechanism, and the diaphragm 371 displaces the passage forming member 35 according to the superheat degree SH of the evaporator 14 outlet side refrigerant.
  • the passage cross-sectional area in the minimum passage area part 30m is adjusted so that the superheat degree SH of the evaporator 14 outlet side refrigerant
  • coolant may approach the predetermined reference
  • the reference superheat degree KSH can be changed by adjusting the load of the coil spring 36a.
  • a cover member 375 that covers the drive mechanism 37 is disposed on the outer peripheral side of the drive mechanism 37. Thereby, it is suppressed that the temperature-sensitive medium in the enclosed space 37a is affected by the outside air temperature in the engine room.
  • the lower body 312 is formed with a mixed refrigerant outlet 31g.
  • the mixed refrigerant outlet 31g is a refrigerant outlet through which the gas-liquid mixed refrigerant flowing out of the diffuser passage 13c flows out to the gas-liquid separation space 31f formed in the gas-liquid separation body 313.
  • the passage sectional area of the mixed refrigerant outlet 31g is formed smaller than the passage sectional area of the most downstream portion of the diffuser passage 13c.
  • the gas-liquid separation body 313 is formed in a cylindrical shape.
  • a gas-liquid separation space 30 f is formed inside the gas-liquid separation body 313.
  • the gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space.
  • the central axes of the gas-liquid separation body 313 and the gas-liquid separation space 30f extend in the vertical direction. For this reason, the gas-liquid separation body 313, the gas-liquid separation space 30f, and the central axis are orthogonal to the central axis of the passage forming member 35 and the like.
  • the gas-liquid separation body 313 is arranged so that the refrigerant that has flowed into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g of the lower body 312 flows along the outer peripheral wall surface of the gas-liquid separation space 30f. Yes. Thereby, in the gas-liquid separation space 30f, the gas-liquid of the refrigerant is separated by the action of the centrifugal force generated by the refrigerant turning around the central axis.
  • a cylindrical pipe 313a that is arranged coaxially with the gas-liquid separation space 30f and extends in the vertical direction.
  • a liquid-phase refrigerant outlet through which the liquid-phase refrigerant separated in the gas-liquid separation space 30f flows out along the outer peripheral side wall surface of the gas-liquid separation space 30f is formed on the cylindrical side surface on the bottom side of the gas-liquid separation body 313.
  • 31c is formed.
  • a gas-phase refrigerant outlet 31d through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out is formed at the lower end of the pipe 313a.
  • a gas-phase refrigerant passage formed in the gas-liquid separation space 30f and the pipe 313a is formed at the root of the pipe 313a in the gas-liquid separation space 30f (that is, the lowermost portion in the gas-liquid separation space 30f).
  • An oil return hole 313b is formed.
  • the oil return hole 313b is a communication path for returning the refrigeration oil dissolved in the liquid refrigerant to the compressor 11 through the gas-phase refrigerant outlet 31d together with the liquid refrigerant.
  • the refrigerant 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 port side of the compressor 11 is connected to the gas-phase refrigerant outlet 31 d of the ejector 13.
  • a control device (not shown) 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 a control program stored in the ROM. Then, the operation of the above-described various electric actuators 11, 12d, 14a and the like is controlled.
  • a plurality of air conditioning control sensor groups such as an inside air temperature sensor, an outside air temperature sensor, a solar radiation sensor, an evaporator temperature sensor, and a discharge pressure sensor are connected to the control device, and detection values of these sensor groups are input.
  • the inside air temperature sensor is an inside air temperature detecting unit that detects the temperature inside the vehicle.
  • the outside air temperature sensor is an outside air temperature detecting unit that detects the outside air temperature.
  • a solar radiation sensor is a solar radiation amount detection part which detects the solar radiation amount in a vehicle interior.
  • the evaporator temperature sensor is an evaporator temperature detector that detects the temperature of the blown air (evaporator temperature) of the evaporator 14.
  • the discharge pressure sensor is an outlet-side pressure detection unit that detects the pressure of the radiator 12 outlet-side refrigerant.
  • an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input to the control device.
  • various operation switches provided on the operation panel there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.
  • control device of the present embodiment is configured integrally with a control unit that controls the operation of various control target devices connected to the output side of the control device.
  • a configuration (hardware and software) for controlling the operation constitutes a control unit of each control target device.
  • the configuration for controlling the refrigerant discharge capacity of the compressor 11 by controlling the operation of the discharge capacity control valve of the compressor 11 constitutes the discharge capacity control unit.
  • the control device when the operation switch of the operation panel is turned on (ON), the control device operates the discharge capacity control valve of the compressor 11, the cooling fan 12d, the blower fan 14a, and the like. Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the condenser 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, and dissipates heat to condense.
  • the refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b.
  • the liquid phase refrigerant separated from the gas and liquid by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d by the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a in FIG. 5).
  • 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 (point b ⁇ point c in FIG. 5).
  • the passage cross-sectional area in the minimum passage area 30m of the decompression space 30b is adjusted so that the superheat degree of the evaporator 14 outlet side refrigerant (point h in FIG. 5) approaches the reference superheat degree KSH.
  • the refrigerant flowing out of the evaporator 14 (point h in FIG. 5) is sucked through the refrigerant suction port 31b and the suction passage 13b by the suction action of the injection refrigerant injected from the nozzle passage 13a.
  • the injection refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b flow into the diffuser passage 13c and join (point c ⁇ d point, h1 point ⁇ d point in FIG. 5).
  • the most downstream portion of the suction passage 13b of the present embodiment is formed in a shape in which the passage cross-sectional area gradually decreases in the refrigerant flow direction. For this reason, the suction refrigerant passing through the suction passage 13b increases the flow velocity while decreasing the pressure (point h ⁇ point h1 in FIG. 5).
  • the kinetic energy of the refrigerant is converted into pressure energy by expanding the sectional area of the refrigerant passage.
  • the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d ⁇ point e in FIG. 5).
  • the refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (e point ⁇ f point, e point ⁇ g point in FIG. 5).
  • the liquid-phase refrigerant separated in the gas-liquid separation space 30f flows into the evaporator 14 with pressure loss when flowing through the refrigerant flow path from the ejector 13 to the evaporator 14 (g point ⁇ g1 in FIG. 5). point).
  • the refrigerant flowing into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates (g1 point ⁇ h point in FIG. 5). Thereby, blowing air is cooled.
  • 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 f ⁇ a 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.
  • the refrigerant whose pressure has been increased in the diffuser passage 13c is sucked into the compressor 11. Therefore, according to the ejector-type refrigeration cycle 10, the power consumption of the compressor 11 can be reduced compared with the normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the refrigerant sucked by the compressor are substantially equal.
  • Coefficient of performance (COP) can be improved.
  • the passage forming member 35 is displaced according to the load fluctuation of the ejector refrigeration cycle 10, and the passage sectional area of the nozzle passage 13a and the diffuser passage The passage cross-sectional area of 13c can be adjusted.
  • the passage cross-sectional areas of the refrigerant passages (specifically, the nozzle passage 13a and the diffuser passage 13c) formed inside are changed to appropriately adjust the ejector 13. Can be operated.
  • the central axis CL of the passage forming member 35 has the inflow space 30a and the pressure reducing portion. There is a risk of tilting with respect to the central axis of the space 30b, the boosting space 30e, and the like.
  • the passage forming member 35 and the upstream operating rod 351a of the shaft 351 are integrated, and the central axis CL of the passage forming member 35 and the central axis of the upstream operating rod 351a are It is arranged on the same axis.
  • the passage forming member 35 can be supported on both ends of the central axis CL. Therefore, it is possible to suppress the inclination of the central axis CL of the passage forming member 35 more reliably. As a result, it is possible to suppress the ejector efficiency from becoming unstable.
  • the upstream operating rod 351a passes through the inflow space 30a, and the central axis of the upstream operating rod 351a and the central axis of the inflow space 30a are arranged coaxially. This not only makes it difficult for the refrigerant in the inflow space 30a to turn around the central axis, but also suppresses the occurrence of an air column at the center of the inflow space 30a even if it turns. be able to.
  • the central axis CL of the passage forming member 35 is not inclined and the form of the air column does not become unstable. As a result, it is possible to suppress the ejector efficiency from becoming unstable. Further, since the swirl flow around the central axis is unlikely to occur in the refrigerant in the inflow space 30a, it occurs due to the difference in the flow direction between the injected refrigerant and the sucked refrigerant when the injected refrigerant and the sucked refrigerant are mixed in the mixing passage 13d. An increase in mixing loss can be suppressed.
  • the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow. According to this, the loss generated in the mixing passage 13d and the diffuser passage 13c can be suppressed.
  • the jet refrigerant injected from the nozzle passage 13a to the mixing passage 13d has a liquid volume ratio in the vicinity of the wall due to the inertial force of the liquid droplets, and the flow velocity tends to be larger than the center of the flow path. That is, the flow velocity of the droplets of the injected refrigerant immediately after being injected from the nozzle passage 13a is larger than the two-phase sonic velocity, and the flow velocity of the gas (that is, the gas phase refrigerant of the injected refrigerant) may be larger than the sonic velocity of the gas. .
  • the flow rate of the suction refrigerant sucked from the suction passage 13b to the mixing passage 13d is smaller than the speed of sound. That is, the suction refrigerant immediately after being sucked into the mixing passage 13d is in a subsonic speed state.
  • the refrigerant in the mixing passage 13d is formed with a velocity boundary layer between the supersonic state refrigerant and the subsonic state refrigerant as shown by a thick broken line in FIG.
  • the road cross-sectional area becomes a flow that decreases in the flow direction (that is, a tapered flow), and the Mach number of the supersonic gas refrigerant decreases, so that an oblique shock wave as shown by a double thin line in FIG. 6 is generated.
  • the Mach number of the wake of the shock wave exceeds 1, an expansion wave as shown by a thin line in FIG. 6 is further generated, and a shock wave is further generated in the wake.
  • the interval between shock waves can be shortened, and the number of occurrences can be suppressed (occurrence twice in FIG. 6).
  • FIG. 7 it is an ejector of a comparative example in which the refrigerant flow in the mixing passage 13d is not a tapered flow, and the passage forming member 35 does not intersect the ridge line on the outlet side of the nozzle passage 13a indicated by the thin broken line.
  • the number of occurrences of the shock wave is likely to increase (in FIG. 7, it is generated three times).
  • the Mach number upstream of the shock wave is 1. For this reason, the expansion of the area is reduced and the pressure increase of the ejector is reduced.
  • the loss of the shock wave (entropy generation amount) will be described using the general formula (F1) of the shock wave entropy generation amount.
  • the amount of entropy generated that becomes a loss with respect to the pressure rise tends to increase as the shock wave angle and Mach number increase.
  • the amount of entropy generation increases by the number of shock waves generated.
  • the injected refrigerant shifts to the subsonic state while generating shock waves twice in the order of N1 ⁇ N2, as indicated by the solid arrow in the upper part of FIG.
  • the injected refrigerant enters the subsonic state while generating shock waves three times at a Mach number higher than that of the present embodiment in the order of n 1 ⁇ n 2 ⁇ n 3. Transition.
  • the entropy generation amount by shock waves (by repeating the collision) is obtained by reducing the Mach number of the flow by reducing the flow of refrigerant in the mixing passage 13d as in the present embodiment. Energy loss) can be reduced, and energy conversion efficiency can be improved.
  • the ejector 13 of the present embodiment high energy conversion efficiency can be stably exhibited regardless of the load fluctuation of the applied ejector refrigeration cycle 10. Further, as described above, the suppression of the increase in mixing loss is extremely effective in the ejector 13 in which the suction refrigerant outlet 13f of the suction passage 13b is annularly opened on the outer peripheral side of the refrigerant injection port 13e of the nozzle passage 13a. .
  • the passage forming member 35 and the shaft 351 are connected to the ejector 13. The assembling property when assembling inside can be improved.
  • the tip of the upstream operating rod 351a is connected to the plate member 374 of the drive mechanism 37, it is easier to connect the passage forming member 35 and the drive mechanism 37 via a plurality of operating rods. Can be linked.
  • the refrigerant inflow passage 31e causes the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a when viewed from the central axis direction of the inflow space 30a. Is formed. According to this, it is possible to further suppress the swirling flow around the central axis from occurring in the refrigerant in the inflow space 30a.
  • rigid bodies such as the upstream operation rod 351a and the passage forming member 35 are arranged at the center of the inflow space 30a, the pressure reducing space 30b, and the pressure increasing space 30e. Accordingly, the axial vertical cross-sectional shapes of all the refrigerant passages formed by the inflow space 30a, the decompression space 30b, and the pressurization space 30e are annular.
  • the minimum passage sectional area of the mixing passage 13d is formed smaller than the total value of the passage sectional area of the refrigerant injection port 13e and the passage sectional area of the suction refrigerant outlet 13f. According to this, the mixing property of the injection refrigerant and the mixed refrigerant in the mixing passage 13d can be improved.
  • the passage sectional area of the mixed refrigerant outlet 31g is formed to be smaller than the passage sectional area of the most downstream portion of the diffuser passage 13c, and further the gas-liquid mixture flowing out of the diffuser passage 13c
  • the refrigerant in the state is caused to flow along the outer peripheral wall surface of the gas-liquid separation space 30f. According to this, the pressure loss of the refrigerant generated in the gas-liquid separation space 30f can be reduced.
  • the static pressure of the refrigerant decreases due to the reduction of the passage cross-sectional area, but the refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g It flows along the inner peripheral wall surface of the liquid separation body 313 (that is, the outer peripheral wall surface of the gas-liquid separation space 30f).
  • FIG. 9 is a drawing corresponding to FIG. 4 described in the first embodiment. Moreover, in FIG. 9, the same code
  • the recessed portion of the present embodiment is formed by a through hole 35a that is formed on the top side of the passage forming member 35 and penetrates the conical side surface of the passage forming member 35 in a direction perpendicular to the central axis CL. ing.
  • the through hole 35a is formed so as to be positioned upstream of the refrigerant flow with respect to the minimum passage area 30m of the nozzle passage 13a.
  • the passage forming member 35 of the ejector 13 of the present embodiment is provided with a through hole 35a, the boiling passage nuclei can be generated by rapidly expanding the refrigerant passage cross-sectional area of the nozzle passage 13a. Therefore, the boiling of the refrigerant in the nozzle passage 13a can be promoted, and the energy conversion efficiency in the nozzle passage 13a can be improved.
  • the through hole 35a is provided, the pressure distribution in the circumferential direction of the nozzle passage 13a formed in an annular cross section can be suppressed. Therefore, even if the central axis CL of the passage forming member 35 is inclined, it is possible to prevent the ejector efficiency from being greatly reduced.
  • the number of through holes 35a is not limited to one, and a plurality of through holes 35a may be provided in the circumferential direction and arranged at equal angular intervals.
  • FIG. 10 is a drawing corresponding to FIG. 4 described in the first embodiment.
  • the recess portion of the present embodiment is formed by a groove portion 35 b formed on the top side of the passage forming member 35 and formed over the entire circumference around the central axis CL of the passage forming member 35. .
  • the groove 35b is formed to be positioned upstream of the refrigerant flow with respect to the minimum passage area 30m of the nozzle passage 13a.
  • the channel forming member 35 of the ejector 13 of the present embodiment is provided with the groove 35b, it is possible to generate a boiling nucleus by rapidly expanding the refrigerant channel cross-sectional area of the nozzle channel 13a. Therefore, the boiling of the refrigerant in the nozzle passage 13a can be promoted, and the energy conversion efficiency in the nozzle passage 13a can be improved.
  • the ejector 13 of the present embodiment since the groove portion 35b is provided, even if the central axis CL of the passage forming member 35 is inclined, the amount of boiling nuclei generated is adjusted according to the inclination. . Thereby, similarly to 2nd Embodiment, the pressure distribution of the circumferential direction of the nozzle channel
  • the shape of the groove part 35b is not limited to this.
  • a plurality of annular groove portions may be formed over the entire circumference around the central axis, or a plurality of groove portions may be formed in an annular shape discontinuously around the central axis of the passage forming member 35.
  • a line drawn on a cross section including the central axis CL of the wall surface forming the mixing passage 13d in the passage forming member 35 of the present embodiment is inclined so as to approach the diffuser body 33 side toward the downstream side of the refrigerant flow. is doing. Thereby, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow.
  • FIG. 11 is a schematic enlarged cross-sectional view corresponding to FIG. 6 described in the first embodiment. Moreover, in FIG. 11, the cross-sectional shape corresponding to the conical side surface of the channel
  • the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow by inclining the conical side surface of the passage forming member 35. Even if the mixing passage 13d is formed in this way, the boosting performance of the diffuser passage 13c can be stabilized and the ejector efficiency can be prevented from becoming unstable, as in the first embodiment. Mixing loss that occurs when the injection refrigerant and the suction refrigerant are mixed can be suppressed.
  • FIG. 12 is an enlarged cross-sectional view of the ejector 13 of the present embodiment, and is a schematic enlarged cross-sectional view of a portion corresponding to the XII portion of FIG. 4 described in the first embodiment.
  • a line (hereinafter referred to as an inner line) 350 drawn on a cross section including a central axis CL of the wall surface forming the nozzle passage 13a in the passage forming member 35 is the nozzle passage 13a.
  • the inner line 350 is formed by combining a plurality of straight lines or curves, and forms corners 350a and 350b that protrude toward the nozzle passage 13a.
  • a line (hereinafter, referred to as an outer line) 320 drawn on a cross section including the central axis CL of the wall surface forming the nozzle passage 13a of the nozzle 32 has a sharp shape toward the nozzle passage 13a.
  • the outer line 320 has a shape formed by combining a plurality of straight lines or curves, and forms corners 320a and 320b that protrude toward the nozzle passage 13a.
  • the inner line 350 and the outer line 320 are formed so as to be line-symmetric with respect to a virtual reference line that is virtually determined in a cross section including the central axis CL.
  • the corner portions 350a and 350b are formed in the passage forming member 35 of the ejector 13 of the present embodiment, the flow direction of the refrigerant flowing through the nozzle passage 13a is turned to the central axis side of the nozzle passage 13a. Boiling nuclei can be generated. That is, the boiling of the refrigerant in the nozzle passage 13a can be promoted with the corner portions 350a and 350b as the boiling start points.
  • the flow direction of the refrigerant flowing through the nozzle passage 13a can be turned to generate boiling nuclei on the outer peripheral side of the nozzle passage 13a. That is, the boiling of the refrigerant in the nozzle passage 13a can be promoted with the corner portions 320a and 320b as the boiling start points.
  • the inner line and the outer line are formed so as to be line symmetric with respect to the reference line, so that the refrigerant flowing through the nozzle passage 13a is viewed from both the inner and outer peripheral sides.
  • boiling nuclei can be supplied. Therefore, it is easy to supply the boiling nuclei equally to the refrigerant flowing through the nozzle passage 13a.
  • the boiling of the refrigerant in the nozzle passage 13a can be effectively promoted, and the energy conversion efficiency in the nozzle passage 13a can be further improved.
  • FIG. 13 is a schematic enlarged cross-sectional view corresponding to FIG. 4 described in the first embodiment.
  • path 13a of the nozzle 32 is made into the minimum internal diameter part 30q.
  • the annular member 352 is an annular member formed of the same material as the passage forming member 35.
  • the outer shape of the annular member 352 is formed in a rotating body shape in which the bottom sides of the two truncated cones are coupled to each other.
  • the annular member 352 is formed in a shape having a maximum outer diameter portion 30n at a substantially central portion in the central axis direction and a minimum outer diameter portion 30p at the most downstream portion of the refrigerant flow.
  • the annular member 352 and the passage forming member 35 are formed as separate members. However, if the passage forming member 35 or the like can be assembled inside the body 30, the annular member 352 and the passage forming are formed.
  • the member 35 may be integrally formed.
  • the nozzle passage 13a of this embodiment will be described.
  • An annular member 352 is disposed on the top side of the passage forming member 35.
  • the shape that the wall surface of the nozzle passage 13a on the center axis CL side (that is, the passage forming member 35 and the annular member 352 side) draws in the axial cross section is the largest from the upstream side of the annular member 352 as shown in FIG. In the range reaching the outer diameter portion 30n, the shape is separated from the central axis CL toward the downstream side of the refrigerant flow.
  • the shape approaches the central axis CL toward the refrigerant flow downstream side.
  • the shape is separated from the central axis CL toward the downstream side of the refrigerant flow from the minimum outer diameter portion 30p.
  • the shape of the wall surface on the opposite side of the central axis CL of the nozzle passage 13a (that is, the side of the nozzle 32 forming the decompression space 30b) in the axial cross section is as shown in FIG.
  • the shape approaches the central axis CL toward the refrigerant flow downstream side. Further, the shape is separated from the central axis CL from the minimum inner diameter portion 30q toward the downstream side of the refrigerant flow.
  • the tapered portion 131 of the nozzle passage 13a of the present embodiment is roughly divided into a first tapered portion 131a and a second tapered portion 131b as shown in FIG.
  • the first tapered portion 131a is a refrigerant passage that is formed in a range from the refrigerant flow upstream side of the annular member 352 to the maximum outer diameter portion 30n, and the passage cross-sectional area gradually decreases.
  • the second tapered portion 131b is formed in a range from the maximum outer diameter portion 30n of the annular member 352 to the minimum inner diameter portion 30q of the nozzle 32, and is enlarged after the passage sectional area immediately after the first tapered portion 131a is reduced. It is a refrigerant passage.
  • the maximum outer diameter portion 30n of the annular member 352 is the most upstream throat portion arranged on the most upstream side of the refrigerant flow. Further, since the maximum outer diameter portion 30n is formed, the nozzle passage 13a has a shape that enlarges the passage sectional area toward the central axis CL. Further, the maximum outer diameter portion 30n is disposed in a region where the subsonic refrigerant flows in the nozzle passage 13a.
  • the minimum inner diameter portion 30q of the nozzle 32 is a downstream throat portion arranged downstream of the refrigerant flow with respect to the most upstream throat portion.
  • the minimum inner diameter portion 30q is formed in a shape that enlarges the passage cross-sectional area of the nozzle passage 13a to the side away from the central axis CL of the passage forming member 35.
  • the passage cross-sectional area of the nozzle passage 13a of the present embodiment changes so as to function as a two-stage throttle type Laval nozzle having a plurality of (two in the present embodiment) throat portions (throat portions).
  • the pressure of the refrigerant is reduced and the flow rate of the refrigerant is increased to be supersonic and injected.
  • the minimum passage cross-sectional area of the refrigerant passage formed by the most upstream throat portion (that is, the maximum outer diameter portion 30n of the annular member 352) is the downstream throat portion (that is, the nozzle
  • the dimensions of the annular member 352 and the nozzle 32 are set to be smaller than the minimum passage cross-sectional area of the refrigerant passage formed by the 32 minimum inner diameter portion 30q).
  • the maximum outer diameter portion 30n of the annular member 352 constituting the most upstream throat portion is formed in a region where the subsonic refrigerant flows in the nozzle passage 13a.
  • the outer diameter portion 30n functions as an edge that rapidly expands the cross-sectional area of the nozzle passage 13a to generate a separation vortex. Therefore, boiling nuclei can be generated in the liquid-phase refrigerant flowing through the nozzle passage 13a.
  • the maximum outer diameter portion 30n of the annular member 352 constituting the most upstream throat portion is formed on the passage forming member 35 side (that is, the central axis CL side).
  • the shape of at least a part of the nozzle passage 13 a is formed to turn the refrigerant flow direction toward the central axis CL of the passage forming member 35.
  • the boiling nuclei can be supplied from the central axis CL side to the liquid refrigerant flowing through the nozzle passage 13a. Therefore, even if an air column or the like is not generated in the refrigerant in the inflow space 30a, the boiling of the refrigerant flowing through the nozzle passage 13a can be promoted, and the ejector efficiency can be improved.
  • the minimum inner diameter portion 30q of the nozzle 32 constituting the downstream throat portion is formed in a portion where the pressure reducing space 30b of the nozzle 32 is formed.
  • the shape of at least a part of the nozzle passage 13 a is formed to turn the refrigerant flow direction away from the central axis CL of the passage forming member 35.
  • boiling nuclei can be supplied from the outer peripheral side to the liquid-phase refrigerant flowing through the nozzle passage 13a. Therefore, the boiling of the refrigerant flowing through the nozzle passage 13a can be further promoted.
  • the minimum passage sectional area of the refrigerant passage formed by the maximum outer diameter portion 30n of the annular member 352 is the minimum passage sectional area of the refrigerant passage formed by the minimum inner diameter portion 30q of the nozzle 32. Is smaller than
  • the flow rate of the refrigerant flowing through the nozzle passage 13a can be adjusted by changing the passage sectional area of the refrigerant passage formed by the maximum outer diameter portion 30n. Further, the subsonic refrigerant flows through the refrigerant passage formed by the maximum outer diameter portion 30n, and the refrigerant enters a supersonic critical state downstream of the maximum outer diameter portion 30n. Therefore, the refrigerant is formed by the maximum outer diameter portion 30n. The refrigerant flow rate can be accurately adjusted in the refrigerant passage.
  • FIG. 14 is a drawing corresponding to FIG. 13 described in the sixth embodiment.
  • the outer shape of the annular member 353 of the present embodiment is formed in a rotating body shape in which the top sides of the two truncated cones are coupled to each other. Therefore, the annular member 353 of the present embodiment is formed in a shape having the maximum outer diameter portion 30n on the most upstream side of the refrigerant flow and the minimum outer diameter portion 30p in the substantially central portion in the central axis direction. Furthermore, the outer diameter of the upstream operating rod 351a of the shaft 351 of the present embodiment is the same thickness as the maximum outer diameter portion 30n.
  • the axial sectional shape of the nozzle passage 13a on the center axis CL side (passage forming member 35 and annular member 353 side) is minimum from the maximum outer diameter portion 30n on the most upstream side of the annular member 353 as shown in FIG.
  • the shape approaches the center axis CL toward the downstream side of the refrigerant flow.
  • the shape is away from the central axis CL from the smallest inner diameter portion 30o toward the downstream side of the refrigerant flow.
  • the part forming the decompression space 30b of the nozzle 32 of the present embodiment has two reduced diameter portions, that is, an upstream minimum inner diameter portion 30q and a downstream minimum inner diameter portion 30r.
  • the inner diameter of the upstream minimum inner diameter portion 30q is smaller than the inner diameter of the downstream minimum inner diameter portion 30r.
  • the axial cross-sectional shape of the nozzle passage 13a on the opposite side of the central axis CL is the upstream minimum inner diameter portion from the inflow space 30a side.
  • the shape approaches the central axis CL toward the downstream side of the refrigerant flow.
  • the refrigerant flows toward the downstream side and becomes a shape that approaches after leaving the central axis CL.
  • the shape is separated from the central axis CL from the downstream-side minimum inner diameter portion 30r toward the downstream side of the refrigerant flow.
  • the second tapered portion 131b is formed in a shape in which the passage sectional area gradually decreases toward the downstream side of the refrigerant flow.
  • the throat portion 132 of the present embodiment is formed with two throat portions, an upstream minimum inner diameter portion 30q and a downstream minimum inner diameter portion 30r. That is, in the present embodiment, two downstream throat portions are formed which are arranged on the downstream side of the refrigerant flow with respect to the most upstream throat portion.
  • the passage cross-sectional area of the nozzle passage 13a of the present embodiment changes so as to function as a multistage throttle nozzle having a plurality of throat portions (throat portions).
  • Other configurations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.
  • the refrigerant is depressurized in multiple stages. That is, in the first taper 131a of the present embodiment, the subsonic liquid phase refrigerant is decompressed.
  • the second tapered portion 131b of the present embodiment has a tapered shape in which the passage sectional area gradually decreases toward the downstream side of the refrigerant flow. For this reason, in the 2nd taper 131b, a refrigerant
  • a separation vortex is generated with the maximum outer diameter portion 30n of the annular member 353 forming the most upstream portion of the second tapered portion 131b as an edge, and the refrigerant on the central axis CL side Boiling nuclei are generated.
  • an upstream minimum inner diameter part 30q of the nozzle 32 forming the uppermost stream part of the divergent part 132 becomes an edge to generate a separation vortex, and boiling nuclei are generated in the outer refrigerant. .
  • the refrigerant whose boiling has been promoted is blocked (choked). This choking causes the refrigerant to reach the speed of sound. Further, the downstream minimum inner diameter portion 30r becomes an edge to generate boiling nuclei, whereby the boiling of the refrigerant is further promoted and the refrigerant is injected from the refrigerant injection port 13e.
  • the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, also in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment, the same effect as in the sixth embodiment can be obtained. That is, the plurality of throat portions are not limited to two as in the sixth embodiment, but may be provided as three or more as in the present embodiment.
  • FIG. 15 is an axial sectional view corresponding to FIG. 2 described in the first embodiment.
  • the shape of the passage forming member 35 is changed with respect to the first embodiment.
  • the passage forming member 35 of the present embodiment is formed in a shape that decreases after the cross-sectional area perpendicular to the central axis increases from the refrigerant flow upstream side to the downstream side. More specifically, the outer shape of the passage forming member 35 of the present embodiment is formed in a rotating body shape in which the truncated cone-shaped member and the bottom surfaces of the conical members are combined.
  • a maximum outer diameter portion 30n is formed at a substantially central portion in the central axis direction of the passage forming member 35.
  • the maximum outer diameter portion 30n functions as the most upstream throat portion described in the sixth embodiment.
  • At least a part of the passage forming member 35 is disposed in the decompression space 30 b formed in the nozzle 32.
  • the nozzle 32 of this embodiment is formed integrally with the upper body 311.
  • the nozzle 32 is formed with a minimum passage area portion 30m that reduces the passage sectional area of the nozzle passage 13a the most.
  • the minimum passage area portion 30m fulfills the function as the downstream throat portion described in the sixth embodiment.
  • the maximum outer diameter portion 30n of the passage forming member 35 is positioned upstream of the refrigerant flow with respect to the minimum passage area portion 30m.
  • the nozzle passage 13a formed between the outer peripheral surface of the passage forming member 35 and the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle 32 is the same as the Laval nozzle, as in the first embodiment.
  • the cross-sectional area changes.
  • a portion of the nozzle passage 13a formed on the upstream side of the refrigerant flow with respect to the smallest passage area portion 30m having the smallest passage cross-sectional area has a tapered portion in which the cross-sectional area of the passage gradually decreases toward the downstream side of the refrigerant flow.
  • path area part 30m becomes a divergent part where a channel
  • the upstream side operating rod 351a of the shaft 351 is integrally and coaxially connected to the top side of the truncated cone-shaped part disposed on the upstream side of the refrigerant flow from the maximum outer diameter part 30n.
  • a stepping motor 370 is connected to the upstream operating rod 351a.
  • the stepping motor 370 is a drive mechanism that displaces the passage forming member 35.
  • the operation of the stepping motor 370 is controlled by a control signal (control pulse) output from the control device.
  • the outer diameter of the maximum outer diameter portion 30n of the passage forming member 35 is formed larger than the inner diameter of the minimum passage area portion 30m of the nozzle 32. For this reason, when the stepping motor 370 displaces the passage forming member 35 and closes the nozzle passage 13a, the maximum outer diameter portion 30n of the passage forming member 35 contacts the nozzle 32.
  • the passage cross-sectional area of the mixing passage 13d arranged on the downstream side of the refrigerant flow in the nozzle passage 13a is reduced toward the downstream side of the refrigerant flow. Furthermore, the minimum passage sectional area of the mixing passage 13d is formed smaller than the total value of the passage sectional area of the refrigerant injection port 13e and the passage sectional area of the suction refrigerant outlet 13f.
  • the passage forming member 35 of the present embodiment is disposed in the decompression space 30b, but is not disposed in the boosting space 30e. Therefore, in the ejector 13 of this embodiment, as shown in FIG. 15, the shape of the pressurizing space 30e is formed such that the passage sectional area gradually decreases toward the downstream side of the refrigerant flow.
  • the pressure increasing space 30e functions as the diffuser passage 13c.
  • the passage forming member 35 is disposed in the decompression space 30b without being disposed in the pressurization space 30e. Therefore, the passage forming member 35 can be downsized as compared with the case where the passage forming member 35 is disposed in both the pressure reducing space 30b and the pressure increasing space 30e. Thereby, size reduction and simplification of the configuration of the ejector 13 as a whole can be achieved.
  • the upstream operation rod 351a is integrally and coaxially connected to the passage forming member 35. Therefore, as in the first embodiment, the central axis CL of the passage forming member 35 can be prevented from being inclined with respect to the central axes of the decompression space 30b, the boosting space 30e, and the like.
  • the passage forming member 35 can be downsized. Therefore, since the load (that is, the action of dynamic pressure) received by the passage forming member 35 from the refrigerant is reduced, the center axis CL of the passage forming member 35 can be further prevented from being inclined.
  • the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow. Therefore, as in the first embodiment, the pressure rising performance of the diffuser passage 13c can be stabilized to prevent the ejector efficiency from becoming unstable, and the injection refrigerant and the suction refrigerant are mixed. The mixing loss occurring in
  • the compression wave reflected on the velocity boundary layer and traveling toward the central axis CL side is on the central axis (so-called slip surface) of the mixing passage 13d even if the passage forming member 35 or the like is not present. ), It collides with the compression wave traveling from the opposite side, reflects, and turns to the outer peripheral side. Therefore, even if the passage forming member 35 is not disposed in the mixing passage 13d, the same effect as in the first embodiment can be obtained.
  • the passage forming member 35 is formed with a maximum outer diameter portion 30n that functions as the most upstream throat portion. Therefore, the boiling nuclei can be supplied from the central axis CL side to the liquid-phase refrigerant flowing through the nozzle passage 13a. Further, a minimum passage area portion 30m that functions as a downstream throat portion is formed in the nozzle 32. Therefore, the minimum inner diameter portion 30q can supply boiling nuclei from the outer peripheral side to the liquid-phase refrigerant flowing through the nozzle passage 13a.
  • the arrangement of the ejector 13 is not limited thereto.
  • the central axis of the passage forming member 35 may be arranged in the vertical direction. In this case, it is desirable that the liquid-phase refrigerant outlet 31c is disposed on the lowermost side of the gas-liquid separation body.
  • the ejector 13 is not limited to the one disclosed in the above embodiment.
  • the upstream operation rod 351a and the downstream operation rod 351b are formed by the shaft 351 that is a common cylindrical member.
  • the upstream operation rod 351a and the downstream operation rod 351b You may form with another member.
  • one downstream operation rod 351b is provided in the same manner as the upstream operation rod 351a, but a plurality of downstream operation rods 351b may be provided.
  • the outer diameter of the upstream operating rod 351a and the outer diameter of the downstream operating rod 351b may be set to the same value or may be set to different values.
  • a bearing member formed of a cylindrical metal may be disposed in each bearing hole.
  • the drive mechanism 37 displaces the passage forming member 35 in accordance with the temperature and pressure of the evaporator 14 outlet-side refrigerant, so that the superheat degree SH of the evaporator 14 outlet-side refrigerant becomes the reference superheat degree.
  • the adjustment of the passage sectional area by the drive mechanism 37 is not limited to this.
  • the nozzle passage is arranged so that the degree of supercooling of the refrigerant on the outlet side of the radiator 12 approaches a predetermined reference subcooling degree by displacing the passage forming member 35 according to the temperature and pressure of the refrigerant on the outlet side of the radiator 12.
  • the passage cross-sectional area of 13a may be adjusted.
  • the drive mechanism 37 is not limited to the one described in the above embodiment.
  • a thermo wax that changes in volume depending on temperature may be employed as the temperature-sensitive medium employed in the drive mechanisms of the first to seventh embodiments.
  • a mechanism having a shape memory alloy elastic member may be adopted as the drive mechanism.
  • the eighth embodiment the example in which the electrically operated stepping motor 370 is employed as the driving mechanism has been described.
  • the first to seventh embodiments are used as the driving mechanism of the ejector 13 described in the eighth embodiment. You may employ
  • Each component device constituting the ejector refrigeration cycle 10 is not limited to that disclosed in the above-described embodiment.
  • a normal radiator including only the condensing unit 12a may be employed.
  • a receiver-integrated condenser that integrates a receiver (receiver) that separates the gas-liquid of the refrigerant radiated by this radiator and stores excess liquid phase refrigerant is adopted. Also good.
  • R1234yf is adopted as the refrigerant
  • the refrigerant is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. can be employed.
  • a supercritical refrigeration cycle in which carbon dioxide is employed as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.
  • the ejector refrigeration cycle 10 according to the present disclosure is applied to a vehicle air conditioner has been described, but the application of the ejector refrigeration cycle 10 is not limited thereto.
  • 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 of the ejector refrigeration cycle 10 including the ejector 13 according to the present disclosure is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 14 cools the blown air.
  • Use side heat exchanger the evaporator 14 may be used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 may be used as a use side heat exchanger that heats a heated fluid such as air or water.
  • each of the above embodiments may be appropriately combined within a practicable range.
  • the passage forming member 35 of the fourth embodiment may be applied to the second, third, and fifth to seventh embodiments.
  • the recess (through hole 35a) described in the second embodiment may be formed in the passage forming member 35 of the fifth to eighth embodiments.

Abstract

An ejector equipped with a body (30) in which a flow space (30a) through which a coolant flows is formed, a channel-forming member (35) having a conical shape and positioned inside the body, and further equipped, in the interval between the inner-wall surface of the body and the conical lateral surface of the channel-forming member, with a nozzle channel (13a) that functions as a nozzle and has a ring-shaped cross-section, and a diffuser channel (13c) that functions as a pressurization unit and has a ring-shaped cross-section. In addition, a drive mechanism (37) for shifting the channel-forming member in the direction of the center axis (CL) is connected to an upstream-side operating rod (351a) that is slidably supported by the body and extends from the channel-forming member toward the flow-space side. Furthermore, the channel-forming member, the upstream-side operating rod and the center axis of the flow space are positioned coaxially with one another. Thus, it is possible to suppress tilting of the center axis when shifting the position of the channel-forming member. As a result, it is possible to stably achieve high energy conversion efficiency, regardless of fluctuations in the load of the refrigeration cycle device being used.

Description

エジェクタEjector 関連出願の相互参照Cross-reference of related applications
 本出願は、当該開示内容が参照によって本出願に組み込まれた、2016年2月2日に出願された日本特許出願2016-018067および、2016年12月22日に出願された日本特許出願2016-248885を基にしている。 The present application includes Japanese Patent Application 2016-018067 filed on February 2, 2016 and Japanese Patent Application 2016- filed on December 22, 2016, the disclosures of which are incorporated herein by reference. Based on 248885.
 本開示は、流体を減圧するとともに、高速度で噴射される噴射流体の吸引作用によって流体を吸引するエジェクタに関する。 The present 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.
 従来、特許文献1に、蒸気圧縮式の冷凍サイクル装置に適用されたエジェクタが開示されている。この特許文献1のエジェクタでは、冷媒を減圧させるノズル通路から噴射される超音速の噴射冷媒の吸引作用によって、ボデーに形成された冷媒吸引口から蒸発器から流出した冷媒を吸引する。そして、ディフューザ通路にて、噴射冷媒と吸引冷媒(すなわち、蒸発器出口側冷媒)との混合冷媒を昇圧させて、圧縮機の吸入側へ流出させる。 Conventionally, Patent Document 1 discloses an ejector applied to a vapor compression refrigeration cycle apparatus. With the ejector of this patent document 1, the refrigerant | coolant which flowed out from the evaporator from the refrigerant | coolant suction port formed in the body is attracted | sucked by the suction effect | action of the supersonic injection refrigerant | coolant injected from the nozzle channel | path which decompresses a refrigerant | coolant. Then, in the diffuser passage, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant (that is, the evaporator outlet side refrigerant) is increased and flows out to the suction side of the compressor.
 より詳細には、特許文献1のエジェクタでは、ボデーの内部に略円錐形状の弁体部である通路形成部材を配置し、ボデーの内側面と通路形成部材の円錐状側面との間に断面円環状の冷媒通路を形成している。そして、この冷媒通路のうち、冷媒流れ最上流側の部位をノズル通路として利用し、ノズル通路の冷媒流れ下流側の部位をディフューザ通路として利用している。 More specifically, in the ejector of Patent Document 1, a passage forming member, which is a substantially conical valve body, is disposed inside the body, and a cross-sectional circle is formed between the inner side surface of the body and the conical side surface of the passage forming member. An annular refrigerant passage is formed. Of these refrigerant passages, a portion on the most upstream side of the refrigerant flow is used as a nozzle passage, and a portion on the downstream side of the refrigerant flow in the nozzle passage is used as a diffuser passage.
 さらに、特許文献1のエジェクタのボデーには、ノズル通路へ流入する冷媒を通路形成部材の中心軸周りに旋回させる旋回空間が形成されている。この旋回空間では、放熱器から流出した液相冷媒を旋回させることによって、旋回中心側の冷媒を減圧沸騰させる。そして、旋回中心側に柱状の気相冷媒(以下、気柱という。)を生じさせた二相分離状態の冷媒をノズル通路へ流入させる。 Furthermore, the body of the ejector of Patent Document 1 is formed with a swirling space for swirling the refrigerant flowing into the nozzle passage around the central axis of the passage forming member. In this swirling space, the liquid-phase refrigerant that has flowed out of the radiator is swirled, whereby the swirling center side refrigerant is boiled under reduced pressure. And the refrigerant | coolant of the two-phase separation state which produced the columnar gaseous-phase refrigerant | coolant (henceforth an air column) in the turning center side is made to flow in into a nozzle channel | path.
 これにより、特許文献1のエジェクタでは、ノズル通路における冷媒の沸騰を促進し、ノズル通路にて冷媒の圧力エネルギを運動エネルギに変換する際のエネルギ変換効率を向上させようとしている。延いては、エジェクタ全体としてのエネルギ変換効率(以下、エジェクタ効率という。)を向上させようとしている。 Thus, the ejector disclosed in Patent Document 1 promotes boiling of the refrigerant in the nozzle passage, and attempts to improve energy conversion efficiency when the pressure energy of the refrigerant is converted into kinetic energy in the nozzle passage. As a result, the energy conversion efficiency (hereinafter referred to as ejector efficiency) of the entire ejector is being improved.
 また、特許文献1のエジェクタは、通路形成部材を変位させて冷媒通路の通路断面積を変化させる駆動機構を備えている。これにより、特許文献1のエジェクタでは、適用された冷凍サイクル装置の負荷変動に応じて、冷媒通路の通路断面積を変化させてエジェクタを適切に作動させようとしている。 Moreover, the ejector of Patent Document 1 includes a drive mechanism that changes the passage cross-sectional area of the refrigerant passage by displacing the passage formation member. Thereby, in the ejector of patent document 1, it is going to operate the ejector appropriately by changing the passage cross-sectional area of a refrigerant passage according to the load fluctuation of the applied refrigeration cycle device.
特開2013-177879号公報JP 2013-177879 A
 ところが、本発明者らが更なるエジェクタ効率の向上のために、特許文献1のエジェクタについて検討を進めたところ、特許文献1のエジェクタでは、高いエジェクタ効率を安定的に発揮できないことがあった。そこで、本発明者らがその原因について調査したところ、以下のような原因が判った。 However, when the present inventors have studied the ejector of Patent Document 1 in order to further improve the ejector efficiency, the ejector of Patent Document 1 sometimes cannot stably exhibit high ejector efficiency. Then, when the present inventors investigated the cause, the following causes were found.
 まず、特許文献1のエジェクタでは、複数の作動棒を介して、通路形成部材の外周側の部位と駆動機構とを連結している。このため、冷凍サイクル装置の負荷変動に応じて通路形成部材を変位させると、通路形成部材の中心軸が旋回空間の中心軸等に対して傾いてしまうことがあった。そして、通路形成部材の中心軸が傾いてしまうと、断面円環状の冷媒通路の通路断面積が周方向に変化してしまう。 First, in the ejector of Patent Document 1, a portion on the outer peripheral side of the passage forming member and the drive mechanism are connected via a plurality of operating rods. For this reason, when the passage forming member is displaced according to the load fluctuation of the refrigeration cycle apparatus, the central axis of the passage forming member may be inclined with respect to the central axis of the swirling space. And if the central axis of a channel | path formation member inclines, the channel | path cross-sectional area of a cross-sectional annular | circular shaped refrigerant channel will change to the circumferential direction.
 そのため、ノズルから噴射される噴射冷媒に周方向の速度分布が生じてしまい、ノズル通路におけるエネルギ変換効率を低下させてしまうとともに、吸引冷媒を周方向に均一に吸引することができなくなってしまう。さらに、通路形成部材の中心軸が傾いてしまうと、旋回空間内に生じる気柱の形態が蛇行して不安定となってしまう。その結果、エジェクタ効率が低下してしまう。 For this reason, a circumferential velocity distribution is generated in the refrigerant injected from the nozzle, and the energy conversion efficiency in the nozzle passage is lowered, and the suction refrigerant cannot be uniformly sucked in the circumferential direction. Furthermore, if the central axis of the passage forming member is tilted, the form of the air column generated in the swirling space will meander and become unstable. As a result, the ejector efficiency decreases.
 また、特許文献1のエジェクタを、異なる物性の冷媒を採用する冷凍サイクル装置に適用した場合、冷凍サイクル装置に所望の冷凍能力を発揮させるために必要な冷媒の量等が変化してしまう。そのため、同一の形状の旋回空間にて異なる物性の冷媒を旋回させたとしても、適切な気柱を安定的に発生させることができず、ノズル通路におけるエネルギ変換効率を向上させることができなくなってしまう。 In addition, when the ejector of Patent Document 1 is applied to a refrigeration cycle apparatus that employs refrigerants having different physical properties, the amount of refrigerant necessary for causing the refrigeration cycle apparatus to exhibit a desired refrigeration capacity changes. Therefore, even if refrigerants with different physical properties are swirled in the same swirling space, an appropriate air column cannot be stably generated, and energy conversion efficiency in the nozzle passage cannot be improved. End up.
 また、特許文献1のエジェクタでは、ノズル通路から超音速となって噴射される噴射冷媒が旋回方向の速度成分を有する。このため、噴射冷媒に生じる斜め衝撃波も旋回流れに沿って発生して、噴射冷媒の旋回方向の速度成分を加速させる。その結果、噴射冷媒の流速と吸引冷媒の流速との速度差が拡大して、噴射冷媒と吸引冷媒とを混合させる際のエネルギ損失(以下、混合損失という。)が増加しやすい。 Further, in the ejector disclosed in Patent Document 1, the jet refrigerant injected at a supersonic speed from the nozzle passage has a velocity component in the swirl direction. For this reason, an oblique shock wave generated in the jet refrigerant is also generated along the swirl flow, and the velocity component in the swirl direction of the jet refrigerant is accelerated. As a result, the speed difference between the flow rate of the injected refrigerant and the flow rate of the suction refrigerant increases, and energy loss (hereinafter referred to as mixing loss) when mixing the injected refrigerant and the suction refrigerant is likely to increase.
 ここで、混合損失の増加を抑制するためには、吸引冷媒を加速させて速度差を低減させることが考えられる。しかしながら、特許文献1のエジェクタでは、通路形成部材を備えており、吸引用通路の冷媒出口をノズル通路の冷媒噴射口の外周側に円環状に開口させている。このため、特許文献1のエジェクタでは、単に吸引冷媒を加速させて速度差を縮小させたとしても、混合損失を充分に低減させることが難しい。 Here, in order to suppress an increase in mixing loss, it is conceivable to accelerate the suction refrigerant to reduce the speed difference. However, the ejector of Patent Document 1 includes a passage forming member, and the refrigerant outlet of the suction passage is opened in an annular shape on the outer peripheral side of the refrigerant injection port of the nozzle passage. For this reason, in the ejector of Patent Document 1, it is difficult to sufficiently reduce the mixing loss even if the suction refrigerant is merely accelerated to reduce the speed difference.
 その理由は、吸引冷媒を加速させて噴射冷媒の外周側から合流させると、噴射冷媒と吸引冷媒とを混合させる混合通路へ流入した噴射冷媒中の液滴が通路形成部材側に偏在あるいは付着してしまうからである。従って、特許文献1のエジェクタでは、吸引冷媒を加速させたとしても、液滴を混合通路中に均質に分布させにくく、混合損失を充分に低減させることが難しい。 The reason is that when the suction refrigerant is accelerated and merged from the outer peripheral side of the jet refrigerant, the droplets in the jet refrigerant flowing into the mixing passage for mixing the jet refrigerant and the suction refrigerant are unevenly distributed or attached to the passage forming member side. Because it will end up. Therefore, in the ejector of Patent Document 1, even if the suction refrigerant is accelerated, it is difficult to uniformly distribute the droplets in the mixing passage, and it is difficult to sufficiently reduce the mixing loss.
 本開示は、上記点に鑑み、安定的に高いエネルギ変換効率を発揮可能なエジェクタを提供することを目的とする。 In view of the above points, it is an object of the present disclosure to provide an ejector that can stably exhibit high energy conversion efficiency.
 本開示の一態様によると、蒸気圧縮式の冷凍サイクル装置に適用されるエジェクタは、ボデーと、通路形成部材と、駆動機構と、を備える。ボデーは、液相冷媒を流入させる流入空間、流入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冷媒吸引口から吸引した冷媒を流通させる吸引用通路、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を介して吸引された吸引冷媒とを流入させる昇圧用空間を有する。通路形成部材は、少なくとも一部が減圧用空間の内部に配置されて、ボデーとの間に冷媒通路を形成する。駆動機構は、通路形成部材を変位させる。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、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である。通路形成部材には、流入空間側へ延びてボデーに摺動可能に支持された上流側作動棒が連結されている。流入空間の中心軸、上流側作動棒の中心軸、および通路形成部材の中心軸は、同軸上に配置されている。 According to one aspect of the present disclosure, an ejector applied to a vapor compression refrigeration cycle apparatus includes a body, a passage forming member, and a drive mechanism. The body includes an inflow space into which liquid phase refrigerant flows, a decompression space for decompressing the refrigerant flowing out of the inflow space, and a suction passage for communicating the refrigerant sucked from the refrigerant suction port in communication with the refrigerant flow downstream side of the decompression space. And a pressure increasing space for allowing the jetted refrigerant injected from the pressure reducing space and the suctioned refrigerant sucked through the suction passage to flow in. At least a part of the passage forming member is disposed inside the decompression space and forms a refrigerant passage between the passage forming member and the body. The drive mechanism displaces the passage forming member. 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 functions as a nozzle that decompresses and injects the refrigerant. An upstream operating rod that extends toward the inflow space and is slidably supported by the body is connected to the passage forming member. The central axis of the inflow space, the central axis of the upstream operating rod, and the central axis of the passage forming member are arranged coaxially.
 これによれば、駆動機構が通路形成部材を変位させるので、適用された冷凍サイクル装置の負荷変動に応じて、ノズル通路の通路断面積を調整することができる。 According to this, since the drive mechanism displaces the passage forming member, the passage sectional area of the nozzle passage can be adjusted according to the load fluctuation of the applied refrigeration cycle apparatus.
 この際、通路形成部材が、同軸上に配置された上流側作動棒によって支持されているので、駆動機構が通路形成部材を変位させても、通路形成部材の中心軸が傾いてしまうことを抑制することができる。従って、通路形成部材の中心軸が傾いてしまうことで、エジェクタ効率が不安定となってしまうことを抑制することができる。 At this time, since the passage forming member is supported by the upstream operation rod arranged on the same axis, even if the drive mechanism displaces the passage forming member, the central axis of the passage forming member is prevented from being inclined. can do. Therefore, it is possible to suppress the ejector efficiency from becoming unstable due to the central axis of the passage forming member being inclined.
 さらに、上流側作動棒が流入空間側へ延びるとともに、上流側作動棒の中心軸と流入空間の中心軸が同軸上に配置されているので、流入空間内の冷媒に旋回流れが生じにくく、流入空間内に気柱が発生しない構成とすることができる。従って、気柱の形態が不安定となってしまうことで、エジェクタ効率が不安定となってしまうことがない。 Furthermore, since the upstream operating rod extends toward the inflow space and the central axis of the upstream operating rod and the central axis of the inflow space are coaxially arranged, it is difficult for the refrigerant in the inflow space to generate a swirling flow. It can be set as the structure which an air column does not generate | occur | produce in space. Therefore, the ejector efficiency does not become unstable because the form of the air column becomes unstable.
 また、流入空間内の冷媒に旋回流れが生じにくいので、噴射冷媒と吸引冷媒とを混合させる際の混合損失の増加を抑制することができる。これにより、エジェクタ効率を向上させることができる。 Also, since a swirl flow is unlikely to occur in the refrigerant in the inflow space, an increase in mixing loss when mixing the injected refrigerant and the suction refrigerant can be suppressed. Thereby, ejector efficiency can be improved.
 すなわち、上記態様のエジェクタによれば、適用された冷凍サイクル装置の負荷変動によらず、安定的に高いエネルギ変換効率を発揮させることができる。 That is, according to the ejector of the above aspect, high energy conversion efficiency can be stably exhibited regardless of the load fluctuation of the applied refrigeration cycle apparatus.
 また、通路形成部材は、少なくとも一部が昇圧用空間の内部に配置されており、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、噴射冷媒および吸引冷媒を混合させて昇圧させる昇圧部として機能するディフューザ通路であってもよい。 Further, at least a part of the passage forming member is disposed inside the pressurizing space, and is formed between an inner peripheral surface of a portion of the body forming the pressurizing space and an outer peripheral surface of the passage forming member. The refrigerant passage may be a diffuser passage that functions as a pressure increasing unit that increases the pressure by mixing the injected refrigerant and the suction refrigerant.
 これによれば、適用された冷凍サイクル装置の負荷変動に応じて、ディフューザ通路の通路断面積を調整することができる。従って、適用された冷凍サイクル装置の負荷変動によらず、より一層、安定的に高いエネルギ変換効率を発揮させることができる。 According to this, the cross-sectional area of the diffuser passage can be adjusted according to the load fluctuation of the applied refrigeration cycle apparatus. Therefore, high energy conversion efficiency can be more stably exhibited regardless of the load fluctuation of the applied refrigeration cycle apparatus.
 また、通路形成部材には、ディフューザ通路の下流側へ延びてボデーに摺動可能に支持された下流側作動棒が連結されていてもよい。これによれば、上流側作動棒および下流側作動棒によって、通路形成部材を中心軸の両端側で支持することができるので、より一層確実に、通路形成部材の中心軸が傾いてしまうことを抑制することができる。 Further, a downstream operating rod that extends downstream from the diffuser passage and is slidably supported by the body may be connected to the passage forming member. According to this, since the passage forming member can be supported on both ends of the central axis by the upstream side operating rod and the downstream side operating rod, the central axis of the passage forming member is more reliably inclined. Can be suppressed.
第1実施形態のエジェクタ式冷凍サイクルの概略図である。It is the schematic of the ejector type refrigerating cycle of 1st Embodiment. 第1実施形態のエジェクタの断面図である。It is sectional drawing of the ejector of 1st Embodiment. 図2のIII-III断面図である。FIG. 3 is a cross-sectional view taken along the line III-III in FIG. 図2のIV部の模式的な断面図である。It is typical sectional drawing of the IV section of FIG. 第1実施形態のエジェクタ式冷凍サイクルにおける冷媒の状態の変化を示すモリエル線図である。It is a Mollier diagram which shows the change of the state of the refrigerant | coolant in the ejector type refrigeration cycle of 1st Embodiment. 図4のVI部の模式的な拡大図である。It is a typical enlarged view of the VI section of FIG. 比較例のエジェクタの図6に対応する部位の模式的な拡大図である。It is a typical enlarged view of the site | part corresponding to FIG. 6 of the ejector of a comparative example. 冷媒が角を曲がる際に発生する衝撃波の特性とエントロピ生成量を説明するための説明図である。It is explanatory drawing for demonstrating the characteristic and the amount of entropy generation | occurrence | production of the shock wave which generate | occur | produce when a refrigerant | coolant turns a corner. 第2実施形態のエジェクタの一部の模式的な断面図である。It is typical sectional drawing of a part of ejector of 2nd Embodiment. 第3実施形態のエジェクタの一部の模式的な断面図である。It is typical sectional drawing of a part of ejector of 3rd Embodiment. 第4実施形態のエジェクタの混合通路を示す模式的な断面図である。It is typical sectional drawing which shows the mixing channel | path of the ejector of 4th Embodiment. 第5実施形態のエジェクタのノズル通路を示す模式的な断面図である。It is typical sectional drawing which shows the nozzle channel | path of the ejector of 5th Embodiment. 第6実施形態のエジェクタの一部の模式的な断面図である。It is typical sectional drawing of a part of ejector of 6th Embodiment. 第7実施形態のエジェクタの一部の模式的な断面図である。It is typical sectional drawing of a part of ejector of 7th Embodiment. 第8実施形態のエジェクタの断面図である。It is sectional drawing of the ejector of 8th Embodiment. 他の実施形態のエジェクタ式冷凍サイクルの概略図である。It is the schematic of the ejector-type refrigerating cycle of other embodiment.
 以下に、図面を参照しながら本開示を実施するための複数の形態を説明する。各形態において先行する形態で説明した事項に対応する部分には同一の参照符号を付して重複する説明を省略する場合がある。各形態において構成の一部のみを説明している場合は、構成の他の部分については先行して説明した他の形態を適用することができる。各実施形態で具体的に組合せが可能であることを明示している部分同士の組合せばかりではなく、特に組合せに支障が生じなければ、明示してなくとも実施形態同士を部分的に組み合せることも可能である。 Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.
 (第1実施形態)
 図1~図8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ており、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。従って、本実施形態のエジェクタ式冷凍サイクル10の冷却対象流体は、送風空気である。
(First embodiment)
1st Embodiment of this indication is described using FIGS. 1-8. As shown in FIG. 1, the ejector 13 of the present embodiment is applied to a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression apparatus, that is, an ejector refrigeration cycle 10. Furthermore, this ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling the blown air blown into the vehicle interior, which is the air-conditioning target space. Therefore, the cooling target fluid of the ejector refrigeration cycle 10 of the present embodiment is blown air.
 また、本実施形態のエジェクタ式冷凍サイクル10では、冷媒としてHFO系冷媒(具体的には、R1234yf)を採用しており、高圧側冷媒圧力が冷媒の臨界圧力を超えない亜臨界冷凍サイクルを構成している。この冷媒には、圧縮機11を潤滑するための冷凍機油が混入されており、冷凍機油の一部は冷媒とともにサイクルを循環している。 Further, the ejector refrigeration cycle 10 of the present embodiment employs an HFO refrigerant (specifically, R1234yf) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. is doing. This refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
 エジェクタ式冷凍サイクル10の構成機器のうち、圧縮機11は、冷媒を吸入して高圧冷媒となるまで昇圧して吐出するものである。圧縮機11は、車両走行用の駆動力を出力するエンジン(内燃機関)とともにエンジンルーム内に配置されている。さらに、圧縮機11は、プーリ、ベルト等を介してエンジンから出力される回転駆動力によって駆動されるエンジン駆動式の圧縮機である。 Of the constituent devices of the ejector refrigeration cycle 10, the compressor 11 sucks refrigerant and discharges it until it becomes high-pressure refrigerant. The compressor 11 is disposed in an engine room together with an engine (internal combustion engine) that outputs a driving force for vehicle travel. Further, the compressor 11 is an engine-driven compressor that is driven by a rotational driving force output from the engine via a pulley, a belt, or the like.
 より具体的には、本実施形態では、圧縮機11として、吐出容量を変化させることによって冷媒吐出能力を調整可能に構成された斜板式の可変容量型圧縮機を採用している。この圧縮機11では、吐出容量を変化させるための図示しない吐出容量制御弁を有している。吐出容量制御弁は、後述する制御装置から出力される制御電流によって、その作動が制御される。 More specifically, in the present embodiment, a swash plate type variable displacement compressor configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity is adopted as the compressor 11. The compressor 11 has a discharge capacity control valve (not shown) for changing the discharge capacity. The operation of the discharge capacity control valve is controlled by a control current output from a control device described later.
 圧縮機11の吐出口には、放熱器12の凝縮部12aの冷媒入口側が接続されている。放熱器12は、圧縮機11から吐出された高圧冷媒と冷却ファン12dによって送風される車室外空気(外気)を熱交換させることによって、高圧冷媒を放熱させて冷却する放熱用熱交換器である。放熱器12は、エンジンルーム内の車両前方側に配置されている。 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 the outside air (outside air) blown by the cooling fan 12d. . The radiator 12 is arranged on the vehicle front side in the engine room.
 より具体的には、放熱器12は、凝縮部12a、レシーバ部12b、および過冷却部12cを有する、いわゆるサブクール型の凝縮器として構成されている。 More specifically, the radiator 12 is configured as a so-called subcool type condenser having a condensing unit 12a, a receiver unit 12b, and a supercooling unit 12c.
 凝縮部12aは、圧縮機11から吐出された高圧気相冷媒と冷却ファン12dから送風された外気とを熱交換させ、高圧気相冷媒を放熱させて凝縮させる凝縮用の熱交換部である。レシーバ部12bは、凝縮部12aから流出した冷媒の気液を分離して余剰液相冷媒を蓄える冷媒容器である。過冷却部12cは、レシーバ部12bから流出した液相冷媒と冷却ファン12dから送風される外気とを熱交換させ、液相冷媒を過冷却する過冷却用の熱交換部である。 The condensing unit 12a is a heat exchange unit for condensation that exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d, and dissipates the high-pressure gas-phase refrigerant to condense. The receiver unit 12b is a refrigerant container that separates the gas-liquid refrigerant flowing out from the condensing unit 12a and stores excess liquid-phase refrigerant. The supercooling unit 12c is a heat exchange unit for supercooling that heat-exchanges the liquid refrigerant flowing out from the receiver unit 12b and the outside air blown from the cooling fan 12d to supercool the liquid refrigerant.
 冷却ファン12dは、制御装置から出力される制御電圧によって回転数(すなわち、送風空気量)が制御される電動送風機である。放熱器12の過冷却部12cの冷媒出口側には、エジェクタ13の冷媒流入口31aが接続されている。 The cooling fan 12d is an electric blower in which the rotation speed (that is, 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.
 エジェクタ13は、放熱器12から流出した過冷却状態の高圧冷媒を減圧させて下流側へ流出させる冷媒減圧装置としての機能を果たす。さらに、エジェクタ13は、高速度で噴射される噴射冷媒の吸引作用によって後述する蒸発器14から流出した冷媒(すなわち、蒸発器14出口側冷媒)を吸引して輸送する冷媒輸送装置としての機能を果たす。 The ejector 13 functions as a refrigerant decompression device that decompresses the supercooled high-pressure refrigerant that has flowed out of the radiator 12 and flows it downstream. Further, the ejector 13 has a function as a refrigerant transporting device that sucks and transports a refrigerant (that is, an outlet side refrigerant of the evaporator 14) that flows out from the evaporator 14 (described later) by the suction action of the jetted refrigerant that is injected at a high speed. Fulfill.
 これに加えて、本実施形態のエジェクタ13は、減圧させた冷媒の気液を分離する気液分離器としての機能も兼ね備えている。換言すると、本実施形態のエジェクタ13は、エジェクタと気液分離器とを一体化(すなわち、モジュール化)させた、気液分離機能付きエジェクタとして構成されている。 In addition to this, the ejector 13 of the present embodiment also has a function as a gas-liquid separator that separates the gas-liquid of the decompressed refrigerant. In other words, the ejector 13 of the present embodiment is configured as an ejector with a gas-liquid separation function in which the ejector and the gas-liquid separator are integrated (that is, modularized).
 エジェクタ13は、圧縮機11および放熱器12とともに、エンジンルーム内に配置されている。なお、図1における上下の各矢印は、エジェクタ13を車両に搭載した状態における上下の各方向を示したものであり、他のエジェクタ式冷凍サイクル10の構成機器を車両に搭載した状態における上下の各方向は、これに限定されない。 The ejector 13 is disposed in the engine room together with the compressor 11 and the radiator 12. In addition, the up and down arrows in FIG. 1 indicate the up and down directions in a state where the ejector 13 is mounted on the vehicle, and the up and down arrows in the state where other components of the ejector refrigeration cycle 10 are mounted on the vehicle. Each direction is not limited to this.
 エジェクタ13の具体的構成については、図2~図4を用いて説明する。図2における上下の各矢印は、エジェクタ式冷凍サイクル10を車両用空調装置に搭載した状態における上下の各方向を示している。図2、図3はいずれもエジェクタ13の軸方向断面図であり、図2は、図3のII-II断面図であり、図3は、図2のIII-III断面図である。 The specific configuration of the ejector 13 will be described with reference to FIGS. The up and down arrows in FIG. 2 indicate the up and down directions in a state where the ejector refrigeration cycle 10 is mounted on the vehicle air conditioner. 2 and 3 are axial sectional views of the ejector 13, FIG. 2 is a sectional view taken along the line II-II in FIG. 3, and FIG. 3 is a sectional view taken along the line III-III in FIG.
 また、図4は、エジェクタ13の内部に形成された冷媒通路を説明するための模式的な一部拡大断面図であって、図2、図3と同一の機能を果たす部分には同一の符号を付している。 FIG. 4 is a schematic partially enlarged cross-sectional view for explaining the refrigerant passage formed inside the ejector 13, and parts having the same functions as those in FIGS. 2 and 3 have the same reference numerals. Is attached.
 本実施形態のエジェクタ13は、図2、図3に示すように、複数の構成部材を組み合わせることによって形成されたボデー30を備えている。 The ejector 13 of the present embodiment includes a body 30 formed by combining a plurality of constituent members as shown in FIGS.
 より具体的には、ボデー30は、アッパーボデー311、ロワーボデー312、気液分離ボデー313等を有している。これらの各ボデー311~313は、エジェクタ13の外殻を形成するとともに、内部に他の構成部材を収容するハウジングとしての機能を果たす。ハウジング用のボデー311~313は、金属製(本実施形態では、アルミニウム合金製)の中空部材で形成されている。なお、ハウジング用のボデー311~313は、樹脂にて形成されていてもよい。 More specifically, the body 30 includes an upper body 311, a lower body 312, a gas-liquid separation body 313, and the like. Each of these bodies 311 to 313 functions as a housing that forms an outer shell of the ejector 13 and accommodates other constituent members therein. The housing bodies 311 to 313 are formed of a hollow member made of metal (in this embodiment, made of an aluminum alloy). The housing bodies 311 to 313 may be made of resin.
 アッパーボデー311とロワーボデー312とを組み合わせることによって形成される内部空間には、後述するノズル32、ディフューザボデー33等のボデー30の構成部材が固定されている。 In the internal space formed by combining the upper body 311 and the lower body 312, constituent members of the body 30 such as a nozzle 32 and a diffuser body 33 described later are fixed.
 アッパーボデー311には、冷媒流入口31a、冷媒吸引口31bといった複数の冷媒流入口が形成されている。冷媒流入口31aは、放熱器12から流出した冷媒を流入させる冷媒流入口である。冷媒吸引口31bは、蒸発器14から流出した冷媒を吸引する冷媒流入口である。 The upper body 311 is formed with a plurality of refrigerant inlets such as a refrigerant inlet 31a and a refrigerant suction port 31b. The refrigerant inlet 31a is a refrigerant inlet through which the refrigerant that has flowed out of the radiator 12 flows. The refrigerant suction port 31b is a refrigerant inflow port that sucks the refrigerant that has flowed out of the evaporator 14.
 気液分離ボデー313には、液相冷媒流出口31c、気相冷媒流出口31dといった複数の冷媒流入出口が形成されている。液相冷媒流出口31cは、気液分離ボデー313内に形成された気液分離空間30fにて分離された液相冷媒を蒸発器14の冷媒入口側へ流出させる冷媒流出口である。気相冷媒流出口31dは、気液分離空間30fにて分離された気相冷媒を圧縮機11の吸入口側へ流出させる冷媒流出口である。 The gas-liquid separation body 313 is formed with a plurality of refrigerant inflow / outflow ports such as a liquid phase refrigerant outflow port 31c and a gas phase refrigerant outflow port 31d. The liquid-phase refrigerant outlet 31 c is a refrigerant outlet that allows the liquid-phase refrigerant separated in the gas-liquid separation space 30 f formed in the gas-liquid separation body 313 to flow out to the refrigerant inlet side of the evaporator 14. The gas-phase refrigerant outlet 31d is a refrigerant outlet through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out to the suction port side of the compressor 11.
 ノズル32は、金属製(本実施形態では、ステンレス製)の円筒状部材で形成されている。ノズル32は、図2、図3に示すように、アッパーボデー311の軸方向一端側(ロワーボデー312の反対側)の底面に配置されている。ノズル32は、アッパーボデー311に形成された穴部に圧入によって固定されており、アッパーボデー311とノズル32との隙間から冷媒が漏れることはない。 The nozzle 32 is formed of a cylindrical member made of metal (in this embodiment, stainless steel). As shown in FIGS. 2 and 3, the nozzle 32 is disposed on the bottom surface of one end side in the axial direction of the upper body 311 (opposite side of the lower body 312). The nozzle 32 is fixed by being press-fitted into a hole formed in the upper body 311, and the refrigerant does not leak from the gap between the upper body 311 and the nozzle 32.
 ノズル32の内部には、冷媒流入口31aから流入した冷媒を流入させる流入空間30aが形成されている。流入空間30aは、略円柱状の回転体形状に形成されている。流入空間30aの中心軸は、後述する通路形成部材35の中心軸CLと同軸上に配置されている。図2、図3から明らかなように、本実施形態の中心軸CLは略水平方向に延びている。なお、回転体形状とは、平面図形を同一平面上の1つの直線(中心軸)周りに回転させた際に形成される立体形状である。 In the nozzle 32, an inflow space 30a for allowing the refrigerant that has flowed in from the refrigerant inflow port 31a to flow is formed. The inflow space 30a is formed in a substantially cylindrical rotating body shape. A central axis of the inflow space 30a is arranged coaxially with a central axis CL of a passage forming member 35 described later. As is clear from FIGS. 2 and 3, the central axis CL of the present embodiment extends in a substantially horizontal direction. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (center axis) on the same plane.
 また、アッパーボデー311には、冷媒流入口31aから流入した冷媒を流入空間30a側へ導く冷媒流入通路31eが形成されている。冷媒流入通路31eは、流入空間30aの中心軸方向から見たときに、径方向に延びる形状に形成され、流入空間30aへ流入する冷媒を、流入空間30aの中心軸に向かって流入させるように形成されている。 In addition, the upper body 311 is formed with a refrigerant inflow passage 31e that guides the refrigerant flowing in from the refrigerant inflow port 31a to the inflow space 30a side. The refrigerant inflow passage 31e is formed in a shape extending in the radial direction when viewed from the central axis direction of the inflow space 30a, and causes the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a. Is formed.
 ノズル32の内部であって、流入空間30aの冷媒流れ下流側には、流入空間30aから流出した冷媒を減圧させて下流側へ流出させる減圧用空間30bが形成されている。減圧用空間30bは、2つの円錐台形状の空間の頂部側同士を結合させた回転体形状に形成されている。この減圧用空間30bの中心軸も、通路形成部材35の中心軸CLと同軸上に配置されている。 Inside the nozzle 32, a decompression space 30b is formed on the downstream side of the refrigerant flow in the inflow space 30a to depressurize the refrigerant that has flowed out of the inflow space 30a and flow out to the downstream side. The decompression space 30b is formed in a rotating body shape in which the top sides of two frustoconical spaces are joined together. The central axis of the decompression space 30b is also arranged coaxially with the central axis CL of the passage forming member 35.
 減圧用空間30bの内部には、円錐状に形成された通路形成部材35の頂部側が配置されている。通路形成部材35は、ボデー30の内部に形成された冷媒通路内に配置された弁体部である。通路形成部材35は、中心軸CL方向に変位することによって、冷媒通路の通路断面積を変化させる機能を果たす。 In the decompression space 30b, the top side of the passage forming member 35 formed in a conical shape is disposed. The passage forming member 35 is a valve body portion arranged in a refrigerant passage formed inside the body 30. The passage forming member 35 functions to change the passage sectional area of the refrigerant passage by being displaced in the direction of the central axis CL.
 より具体的には、通路形成部材35は、冷媒に対して耐性を有する樹脂製(本実施形態では、ナイロン6またはナイロン66製)の円錐状部材で形成されている。通路形成部材35は、減圧用空間30bから離れるに伴って(すなわち、冷媒流れ下流側へ向かって)、外径が拡大する円錐形状に形成されている。 More specifically, the passage forming member 35 is formed of a conical member made of resin (in this embodiment, nylon 6 or nylon 66) that is resistant to the refrigerant. The passage forming member 35 is formed in a conical shape in which the outer diameter increases as the distance from the decompression space 30b increases (that is, toward the downstream side of the refrigerant flow).
 また、通路形成部材35の内部には、その底面側から略円錐台状の空間が形成されている。つまり、通路形成部材35は、杯状(すなわち、カップ状)に形成されている。さらに、通路形成部材35には、シャフト351が連結されている。シャフト351は、金属製(本実施形態では、ステンレス製)の円柱棒状部材で形成されている。シャフト351の中心軸は、通路形成部材35の中心軸CLと同軸上に配置されている。 In addition, a substantially frustoconical space is formed inside the passage forming member 35 from the bottom surface side. That is, the passage forming member 35 is formed in a cup shape (that is, a cup shape). Further, a shaft 351 is connected to the passage forming member 35. The shaft 351 is formed of a cylindrical rod-shaped member made of metal (in this embodiment, stainless steel). The central axis of the shaft 351 is disposed coaxially with the central axis CL of the passage forming member 35.
 シャフト351は、通路形成部材35にインサート成形されている。これにより、通路形成部材35とシャフト351は一体化されている。さらに、シャフト351は、上流側作動棒351aおよび下流側作動棒351bを有している。従って、上流側作動棒351aの中心軸と下流側作動棒351bの中心軸も同軸上に配置されている。 The shaft 351 is insert-molded in the passage forming member 35. Thereby, the channel | path formation member 35 and the shaft 351 are integrated. Furthermore, the shaft 351 has an upstream operation rod 351a and a downstream operation rod 351b. Accordingly, the central axis of the upstream operating rod 351a and the central axis of the downstream operating rod 351b are also arranged coaxially.
 上流側作動棒351aは、通路形成部材35の頂部から流入空間30aを貫通するように延びて、アッパーボデー311の軸受穴に摺動可能に支持されている。また、下流側作動棒351bは、通路形成部材35の頂部から後述するディフューザ通路13cの下流側へ向かって延びて、ロワーボデー312に設けられた支持部材36の軸受穴に摺動可能に支持されている。つまり、シャフト351は、軸方向の両端側でボデー30に摺動可能に支持されている。 The upstream operating rod 351a extends from the top of the passage forming member 35 so as to penetrate the inflow space 30a, and is slidably supported in the bearing hole of the upper body 311. The downstream operation rod 351b extends from the top of the passage forming member 35 toward the downstream side of a diffuser passage 13c described later, and is slidably supported in a bearing hole of a support member 36 provided in the lower body 312. Yes. That is, the shaft 351 is slidably supported by the body 30 at both axial ends.
 支持部材36は、金属製(本実施形態では、アルミニウム合金)の円筒状部材で形成され、図示しない固定部材を介してロワーボデー312に固定されている。さらに、支持部材36の内部には、下流側作動棒351bに対して流入空間30a側へ向かう荷重をかけるコイルバネ36aが収容されている。コイルバネ36aの荷重は、支持部材36に設けられた調整ネジによって調整することができる。 The support member 36 is formed of a cylindrical member made of metal (in this embodiment, an aluminum alloy), and is fixed to the lower body 312 via a fixing member (not shown). Furthermore, a coil spring 36a that applies a load toward the inflow space 30a with respect to the downstream operation rod 351b is accommodated inside the support member 36. The load of the coil spring 36 a can be adjusted by an adjustment screw provided on the support member 36.
 上流側作動棒351aの流入空間30a側の先端部は、駆動機構37に連結されている。駆動機構37は、シャフト351および通路形成部材35を軸方向に変位させるための駆動力を出力するものである。駆動機構37の詳細については後述する。 The leading end of the upstream operating rod 351a on the inflow space 30a side is connected to the drive mechanism 37. The drive mechanism 37 outputs a driving force for displacing the shaft 351 and the passage forming member 35 in the axial direction. Details of the drive mechanism 37 will be described later.
 次に、通路形成部材35の頂部側(すなわち、流入空間30a側)の外周面とノズル32の減圧用空間30bを形成する部位の内周面との間に形成されて、流入空間30aから流出した冷媒が流通する冷媒通路について説明する。 Next, it is formed between the outer peripheral surface on the top side (that is, the inflow space 30a side) of the passage forming member 35 and the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle 32, and flows out from the inflow space 30a. A refrigerant passage through which the refrigerant flows will be described.
 この冷媒通路は、冷媒を減圧させて噴射するノズルとして機能するノズル通路13aである。ノズル通路13aは、軸方向垂直断面の形状が円環状(円形状から同軸上に配置された小径の円形状を除いた形状)に形成されている。ノズル通路13aには、図4に示すように、先細部131および末広部132が形成されている。 This refrigerant passage is a nozzle passage 13a that functions as a nozzle for depressurizing and injecting the refrigerant. The nozzle passage 13a is formed in an annular shape (a shape excluding a small-diameter circular shape arranged coaxially from a circular shape) in a vertical cross section in the axial direction. As shown in FIG. 4, the nozzle passage 13 a is formed with a tapered portion 131 and a divergent portion 132.
 先細部131は、ノズル通路13aのうち通路断面積が最も縮小した最小通路面積部30mよりも冷媒流れ上流側に形成されて、最小通路面積部30mに至るまでの通路断面積が徐々に縮小する冷媒通路である。末広部132は、最小通路面積部30mから冷媒流れ下流側に形成されて、通路断面積が徐々に拡大する冷媒通路である。 The tapered portion 131 is formed on the upstream side of the refrigerant flow with respect to the minimum passage area portion 30m having the smallest passage cross-sectional area in the nozzle passage 13a, and the passage cross-sectional area up to the minimum passage area portion 30m is gradually reduced. It is a refrigerant passage. The divergent portion 132 is a refrigerant passage that is formed on the downstream side of the refrigerant flow from the minimum passage area portion 30m, and the passage cross-sectional area gradually increases.
 つまり、本実施形態のノズル通路13aでは、ラバールノズルと同様に通路断面積が変化する。これにより、ノズル通路13aでは、冷媒を減圧させるとともに、冷媒の流速を超音速となるように増速させて噴射している。 That is, in the nozzle passage 13a of the present embodiment, the passage cross-sectional area changes like the Laval nozzle. Thus, in the nozzle passage 13a, the pressure of the refrigerant is reduced and the flow rate of the refrigerant is increased to be supersonic and injected.
 次に、アッパーボデー311の内部のノズル32よりも冷媒流れ下流側には、図2、図3に示すように、ディフューザボデー33が配置されている。ディフューザボデー33は、金属製(本実施形態では、アルミニウム合金性)の円筒状部材で形成されている。ディフューザボデー33は、内部に形成された貫通穴33aにノズル32の冷媒噴射口13e側を収容できるように、複数の部材に分割されていてもよい。 Next, as shown in FIGS. 2 and 3, a diffuser body 33 is arranged on the downstream side of the refrigerant flow from the nozzle 32 inside the upper body 311. The diffuser body 33 is formed of a cylindrical member made of metal (in this embodiment, aluminum alloy). The diffuser body 33 may be divided into a plurality of members so that the refrigerant injection port 13e side of the nozzle 32 can be accommodated in a through hole 33a formed inside.
 ディフューザボデー33は、その外周側がアッパーボデー311の内周側面に圧入されることによって、アッパーボデー311に固定されている。なお、ディフューザボデー33とアッパーボデー311との間には、図示しないシール部材としてのO-リングが配置されており、これらの部材の隙間から冷媒が漏れることはない。 The diffuser body 33 is fixed to the upper body 311 by press-fitting the outer peripheral side thereof to the inner peripheral side surface of the upper body 311. Note that an O-ring as a sealing member (not shown) is arranged between the diffuser body 33 and the upper body 311 so that the refrigerant does not leak from the gap between these members.
 ディフューザボデー33の中心部には、軸方向に貫通する貫通穴33aが形成されている。貫通穴33aは略円錐台状の回転体形状に形成されており、その中心軸が通路形成部材35の中心軸CLと同軸上に配置されている。さらに、本実施形態では、ノズル32の冷媒噴射口13e側の先端部が、ディフューザボデー33の貫通穴33aの内部まで延びている。 At the center of the diffuser body 33, a through hole 33a penetrating in the axial direction is formed. The through hole 33 a is formed in a substantially truncated cone-shaped rotating body shape, and its central axis is arranged coaxially with the central axis CL of the passage forming member 35. Furthermore, in this embodiment, the front-end | tip part by the side of the refrigerant | coolant injection port 13e of the nozzle 32 is extended to the inside of the through-hole 33a of the diffuser body 33. FIG.
 そして、ディフューザボデー33の貫通穴33aの内周面とノズル32の先端部の外周面との間には、冷媒吸引口31bから吸引された冷媒を減圧用空間30b(すなわち、ノズル通路13a)の冷媒流れ下流側へ導く吸引用通路13bが形成されている。このため、中心軸CL方向から見たときに、吸引用通路13bの最下流部となる吸引冷媒出口13fは、冷媒噴射口13eの外周側に円環状に開口している。 And between the inner peripheral surface of the through-hole 33a of the diffuser body 33 and the outer peripheral surface of the front-end | tip part of the nozzle 32, the refrigerant | coolant attracted | sucked from the refrigerant | coolant suction port 31b of the pressure reduction space 30b (namely, nozzle passage 13a). A suction passage 13b leading to the downstream side of the refrigerant flow is formed. For this reason, when viewed from the direction of the central axis CL, the suction refrigerant outlet 13f which is the most downstream portion of the suction passage 13b opens in an annular shape on the outer peripheral side of the refrigerant injection port 13e.
 ディフューザボデー33の貫通穴33aのうち、吸引用通路13bの冷媒流れ下流側には、冷媒流れ方向に向かって徐々に広がる略円錐台形状に形成された昇圧用空間30eが形成されている。昇圧用空間30eは、上述したノズル通路13aから噴射された噴射冷媒と吸引用通路13bから吸引された吸引冷媒とを流入させる空間である。 In the through hole 33a of the diffuser body 33, on the downstream side of the refrigerant flow in the suction passage 13b, a pressure increasing space 30e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction is formed. The pressurizing space 30e is a space into which the injection refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the suction passage 13b flow.
 昇圧用空間30eの内部には、通路形成部材35の下方側が配置されている。ディフューザボデー33の昇圧用空間30eを形成する部位の内周面と通路形成部材35の下方側の外周面との間には、混合通路13d、およびディフューザ通路13cが形成されている。混合通路13dは、噴射冷媒と吸引冷媒とを混合させる冷媒通路である。ディフューザ通路13cは、噴射冷媒と吸引冷媒との混合冷媒を昇圧させる冷媒通路である。 The lower side of the passage forming member 35 is disposed inside the pressurizing space 30e. A mixing passage 13d and a diffuser passage 13c are formed between the inner peripheral surface of the diffuser body 33 forming the pressurizing space 30e and the lower outer peripheral surface of the passage forming member 35. The mixing passage 13d is a refrigerant passage for mixing the injection refrigerant and the suction refrigerant. The diffuser passage 13c is a refrigerant passage that pressurizes the mixed refrigerant of the injection refrigerant and the suction refrigerant.
 混合通路13dは、ディフューザ通路13cの冷媒流れ上流側に配置されている。混合通路13dは、冷媒流れ下流側へ向かって通路断面積が徐々に縮小する形状に形成されている。具体的には、図4に示すように、ディフューザボデー33のうち混合通路13dを形成する壁面が中心軸CLを含む軸方向断面に描く線は、冷媒流れ下流側へ向かって通路形成部材35側に近づくように傾斜している。これにより、混合通路13dの通路断面積は、冷媒流れ下流側へ向かって縮小している。 The mixing passage 13d is disposed upstream of the refrigerant flow in the diffuser passage 13c. The mixing passage 13d is formed in a shape in which the passage cross-sectional area gradually decreases toward the downstream side of the refrigerant flow. Specifically, as shown in FIG. 4, the line drawn in the axial cross section including the central axis CL of the wall surface forming the mixing passage 13d in the diffuser body 33 is the passage forming member 35 side toward the refrigerant flow downstream side. Inclined to approach. Thereby, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow.
 さらに、混合通路13dの最小通路断面積は、冷媒噴射口13eの通路断面積および吸引冷媒出口13fの通路断面積の合計値よりも小さく形成されている。 Furthermore, the minimum passage sectional area of the mixing passage 13d is formed smaller than the total value of the passage sectional area of the refrigerant injection port 13e and the passage sectional area of the suction refrigerant outlet 13f.
 ディフューザ通路13cは、冷媒流れ下流側に向かって通路断面積を徐々に拡大させる形状に形成されている。これにより、ディフューザ通路13cでは、混合冷媒の速度エネルギを圧力エネルギに変換することができる。従って、ディフューザ通路13cは、ディフューザ部(昇圧部)としての機能を果たす。また、混合通路13dおよびディフューザ通路13cは、いずれも中心軸に垂直な断面形状が円環状に形成されている。 The diffuser passage 13c is formed in a shape that gradually increases the cross-sectional area of the passage toward the downstream side of the refrigerant flow. Thereby, the velocity energy of the mixed refrigerant can be converted into pressure energy in the diffuser passage 13c. Therefore, the diffuser passage 13c functions as a diffuser part (a boosting part). The mixing passage 13d and the diffuser passage 13c are both formed in an annular shape in cross section perpendicular to the central axis.
 ここで、図4に示すように、ノズル通路13aは、通路形成部材35の外周面から法線方向に延びる線分がノズル32のうち減圧用空間30bを形成する部位と交わる範囲に形成される冷媒通路と定義してもよい。ディフューザ通路13cは、通路形成部材35の外周面から法線方向に延びる線分がディフューザボデー33のうち昇圧用空間30eを形成する部位と交わる範囲に形成される冷媒通路と定義してもよい。 Here, as shown in FIG. 4, the nozzle passage 13 a is formed in a range where a line segment extending in the normal direction from the outer peripheral surface of the passage forming member 35 intersects a portion of the nozzle 32 that forms the decompression space 30 b. It may be defined as a refrigerant passage. The diffuser passage 13c may be defined as a refrigerant passage formed in a range where a line segment extending in the normal direction from the outer peripheral surface of the passage forming member 35 intersects a portion of the diffuser body 33 that forms the pressure increasing space 30e.
 図4の断面図における吸引用通路13bの吸引冷媒出口13fは、通路形成部材35の外周面の法線方向に延びる線分であって、ノズル32の冷媒噴射口13eの先端部からディフューザボデー33へ至る線分で定義してもよい。 The suction refrigerant outlet 13f of the suction passage 13b in the cross-sectional view of FIG. 4 is a line segment extending in the normal direction of the outer peripheral surface of the passage forming member 35, and extends from the tip of the refrigerant injection port 13e of the nozzle 32 to the diffuser body 33. It may be defined by a line segment leading to.
 混合通路13dは、ノズル通路13a、吸引用通路13b、およびディフューザ通路13cを接続する冷媒通路と定義してもよい。さらに、混合通路13dの最小通路断面積は、混合通路13dの冷媒流れ最下流部(すなわち、ディフューザ通路13cの冷媒流れ最上流部)における通路断面積となる。 The mixing passage 13d may be defined as a refrigerant passage connecting the nozzle passage 13a, the suction passage 13b, and the diffuser passage 13c. Furthermore, the minimum passage sectional area of the mixing passage 13d is a passage sectional area in the most downstream portion of the refrigerant flow in the mixing passage 13d (that is, the most upstream portion of the refrigerant flow in the diffuser passage 13c).
 さらに、ノズル通路13a、吸引用通路13b、ディフューザ通路13c、および混合通路13dは、通路形成部材35の外周面とボデー30(具体的には、ノズル32、およびディフューザボデー33)の内周面との間に形成されている。 Further, the nozzle passage 13a, the suction passage 13b, the diffuser passage 13c, and the mixing passage 13d are formed on the outer peripheral surface of the passage forming member 35 and the inner peripheral surface of the body 30 (specifically, the nozzle 32 and the diffuser body 33). Is formed between.
 このため、中心軸CLと通路形成部材35の外周面との間の角度、および中心軸CLとボデー30の内周面との間の角度を調整することで、仮に冷媒流れ下流側に向かって通路断面積を一定に形成したとしても、各通路の径方向の幅(流路幅)等を冷媒流れ下流側に向かって増加させることも減少させることもできる。 For this reason, by adjusting the angle between the central axis CL and the outer peripheral surface of the passage forming member 35 and the angle between the central axis CL and the inner peripheral surface of the body 30, the refrigerant flows toward the downstream side. Even if the passage cross-sectional area is formed constant, the radial width (flow passage width) of each passage can be increased or decreased toward the downstream side of the refrigerant flow.
 次に、駆動機構37について説明する。駆動機構37は、通路形成部材35を変位させることによって、ノズル通路13aの最小通路面積部30m等の冷媒通路断面積を変化させるものである。図2、図3に示すように、駆動機構37は、アッパーボデー311の外側であって、上流側作動棒351aの軸方向延長線上に配置されている。駆動機構37は、ダイヤフラム371、アッパーカバー372、ロワーカバー373等を有している。 Next, the drive mechanism 37 will be described. The drive mechanism 37 changes the refrigerant passage cross-sectional area such as the minimum passage area portion 30m of the nozzle passage 13a by displacing the passage forming member 35. As shown in FIGS. 2 and 3, the drive mechanism 37 is disposed outside the upper body 311 and on an axial extension line of the upstream operation rod 351a. The drive mechanism 37 includes a diaphragm 371, an upper cover 372, a lower cover 373, and the like.
 アッパーカバー372は、ダイヤフラム371とともに、封入空間37aの一部を形成する封入空間形成部材である。アッパーカバー372は、金属(本実施形態では、ステンレス)で形成されたカップ状部材である。 The upper cover 372 is a sealed space forming member that forms a part of the sealed space 37a together with the diaphragm 371. The upper cover 372 is a cup-shaped member formed of metal (in this embodiment, stainless steel).
 封入空間37a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空間である。より詳細には、封入空間37aは、エジェクタ式冷凍サイクル10を循環する冷媒と同等の組成の感温媒体が予め定めた封入密度となるように封入された空間である。 The enclosed space 37a is a space in which a temperature-sensitive medium whose pressure changes with temperature change is enclosed. More specifically, the enclosed space 37a is a space in which a temperature-sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed so as to have a predetermined enclosure density.
 従って、本実施形態の感温媒体としては、R1234yfを主成分とする媒体(例えば、R1234yfとヘリウムとの混合媒体)を採用することができる。さらに、感温媒体の封入密度は、後述するようにサイクルの通常作動時に通路形成部材35を適切に変位させることができるように設定されている。 Therefore, a medium mainly composed of R1234yf (for example, a mixed medium of R1234yf and helium) can be employed as the temperature sensitive medium of the present embodiment. Further, the density of the temperature sensitive medium is set so that the passage forming member 35 can be appropriately displaced during the normal operation of the cycle, as will be described later.
 ロワーカバー373は、ダイヤフラム371とともに、導入空間37bを形成する導入空間形成部材である。ロワーカバー373は、アッパーカバー372と同様の金属部材で形成されている。導入空間37bは、図示しない連通路を介して、冷媒吸引口31bから吸引された吸引冷媒を導入させる空間である。 The lower cover 373 is an introduction space forming member that forms the introduction space 37b together with the diaphragm 371. The lower cover 373 is formed of the same metal member as the upper cover 372. The introduction space 37b is a space for introducing the suction refrigerant sucked from the refrigerant suction port 31b through a communication path (not shown).
 アッパーカバー372およびロワーカバー373は、かしめ等により外周縁部同士が固定されている。さらに、ダイヤフラム371の外周側縁部は、アッパーカバー372とロワーカバー373との間に挟持される。これにより、ダイヤフラム371が、アッパーカバー372とロワーカバー373との間に形成される空間を封入空間37aと導入空間37bとに仕切っている。 The outer peripheral edges of the upper cover 372 and the lower cover 373 are fixed by caulking or the like. Further, the outer peripheral side edge of the diaphragm 371 is sandwiched between the upper cover 372 and the lower cover 373. Thereby, the diaphragm 371 partitions the space formed between the upper cover 372 and the lower cover 373 into an enclosed space 37a and an introduction space 37b.
 ダイヤフラム371は、封入空間37aの内圧と吸引用通路13bを流通する吸引冷媒の圧力との圧力差に応じて変位する圧力応動部材である。従って、ダイヤフラム371は弾性に富み、かつ耐圧性および気密性に優れる材質で形成されていることが望ましい。 The diaphragm 371 is a pressure responsive member that is displaced according to the pressure difference between the internal pressure of the enclosed space 37a and the pressure of the suction refrigerant flowing through the suction passage 13b. Accordingly, it is desirable that the diaphragm 371 is made of a material that is rich in elasticity and excellent in pressure resistance and airtightness.
 そこで、本実施形態では、ダイヤフラム371として、ステンレス(SUS304)製の金属薄板を採用している。また、基布(ポリエステル)入りのEPDM(エチレンプロピレンジエンゴム)やHNBR(水素添加ニトリルゴム)等のゴム製の基材で形成されたものを採用してもよい。 Therefore, in this embodiment, a metal thin plate made of stainless steel (SUS304) is adopted as the diaphragm 371. Moreover, you may employ | adopt what was formed with rubber | gum base materials, such as EPDM (ethylene propylene diene rubber) and HNBR (hydrogenated nitrile rubber) containing base fabric (polyester).
 ダイヤフラム371の導入空間37b側には、金属(本実施形態では、アルミニウム合金)で形成された円板状のプレート部材374が配置されている。プレート部材374は、ダイヤフラム371に接触するように配置されている。さらに、プレート部材374には、上流側作動棒351aの先端部が連結されている。従って、本実施形態のシャフト351および通路形成部材35は、駆動機構37(具体的には、ダイヤフラム371)から受ける荷重とコイルバネ36aから受ける荷重との合計荷重が釣り合うように変位する。 A disk-shaped plate member 374 made of metal (in this embodiment, an aluminum alloy) is disposed on the introduction space 37b side of the diaphragm 371. The plate member 374 is arranged so as to contact the diaphragm 371. Further, the tip end portion of the upstream operation rod 351a is coupled to the plate member 374. Therefore, the shaft 351 and the passage forming member 35 of the present embodiment are displaced so that the total load of the load received from the drive mechanism 37 (specifically, the diaphragm 371) and the load received from the coil spring 36a is balanced.
 より具体的には、蒸発器14出口側冷媒の温度(過熱度SH)が上昇すると、封入空間37aに封入された感温媒体の飽和圧力が上昇し、封入空間37a内の内圧から導入空間37b内の内圧を差し引いた圧力差が大きくなる。これにより、ダイヤフラム371が導入空間37b側へ変位して、上流側作動棒351aが駆動機構37から受ける荷重が増加する。 More specifically, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) rises, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37a rises, and the introduction space 37b from the internal pressure in the enclosed space 37a. The pressure difference obtained by subtracting the internal pressure increases. As a result, the diaphragm 371 is displaced toward the introduction space 37b, and the load received by the upstream operating rod 351a from the drive mechanism 37 increases.
 従って、蒸発器14出口側冷媒の温度(過熱度SH)が上昇すると、通路形成部材35は、最小通路面積部30mにおける通路断面積を拡大させる方向に変位する。 Therefore, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) rises, the passage forming member 35 is displaced in a direction in which the passage sectional area in the minimum passage area portion 30m is enlarged.
 一方、蒸発器14出口側冷媒の温度(過熱度SH)が低下すると、封入空間37aに封入された感温媒体の飽和圧力が低下し、封入空間37a内の内圧から導入空間37b内の内圧を差し引いた圧力差が小さくなる。これにより、ダイヤフラム371が封入空間37a側へ変位して、上流側作動棒351aが駆動機構37から受ける荷重が減少する。 On the other hand, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) decreases, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37a decreases, and the internal pressure in the introduction space 37b is reduced from the internal pressure in the enclosed space 37a. The subtracted pressure difference becomes smaller. As a result, the diaphragm 371 is displaced toward the enclosed space 37a, and the load received by the upstream operating rod 351a from the drive mechanism 37 is reduced.
 従って、蒸発器14出口側冷媒の温度(過熱度SH)が低下すると、通路形成部材35は、最小通路面積部30mにおける通路断面積を縮小させる方向に変位する。 Therefore, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) is lowered, the passage forming member 35 is displaced in a direction of reducing the passage cross-sectional area in the minimum passage area portion 30m.
 つまり、本実施形態の駆動機構37は、機械的機構で構成されており、蒸発器14出口側冷媒の過熱度SHに応じて、ダイヤフラム371が通路形成部材35を変位させる。そして、蒸発器14出口側冷媒の過熱度SHが予め定めた基準過熱度KSHに近づくように、最小通路面積部30mにおける通路断面積を調整している。なお、基準過熱度KSHは、前述のコイルバネ36aの荷重を調整することによって、変更することができる。 That is, the drive mechanism 37 of this embodiment is configured by a mechanical mechanism, and the diaphragm 371 displaces the passage forming member 35 according to the superheat degree SH of the evaporator 14 outlet side refrigerant. And the passage cross-sectional area in the minimum passage area part 30m is adjusted so that the superheat degree SH of the evaporator 14 outlet side refrigerant | coolant may approach the predetermined reference | standard superheat degree KSH. The reference superheat degree KSH can be changed by adjusting the load of the coil spring 36a.
 さらに、本実施形態では、駆動機構37の外周側に、駆動機構37を覆うカバー部材375を配置している。これにより封入空間37a内の感温媒体がエンジンルーム内の外気温の影響を受けてしまうことを抑制している。 Furthermore, in this embodiment, a cover member 375 that covers the drive mechanism 37 is disposed on the outer peripheral side of the drive mechanism 37. Thereby, it is suppressed that the temperature-sensitive medium in the enclosed space 37a is affected by the outside air temperature in the engine room.
 次に、図2、図3に示すように、ロワーボデー312には、混合冷媒流出口31gが形成されている。混合冷媒流出口31gは、ディフューザ通路13cから流出した気液混合状態の冷媒を気液分離ボデー313内に形成された気液分離空間31f側へ流出させる冷媒流出口である。混合冷媒流出口31gの通路断面積は、ディフューザ通路13cの最下流部の通路断面積よりも小さく形成されている。 Next, as shown in FIGS. 2 and 3, the lower body 312 is formed with a mixed refrigerant outlet 31g. The mixed refrigerant outlet 31g is a refrigerant outlet through which the gas-liquid mixed refrigerant flowing out of the diffuser passage 13c flows out to the gas-liquid separation space 31f formed in the gas-liquid separation body 313. The passage sectional area of the mixed refrigerant outlet 31g is formed smaller than the passage sectional area of the most downstream portion of the diffuser passage 13c.
 気液分離ボデー313は、円筒状に形成されている。気液分離ボデー313の内部には、気液分離空間30fが形成されている。気液分離空間30fは、略円筒状の回転体形状の空間として形成されている。気液分離ボデー313および気液分離空間30fの中心軸は上下方向に延びている。このため、気液分離ボデー313と気液分離空間30fと中心軸は、通路形成部材35等の中心軸に直交している。 The gas-liquid separation body 313 is formed in a cylindrical shape. A gas-liquid separation space 30 f is formed inside the gas-liquid separation body 313. The gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space. The central axes of the gas-liquid separation body 313 and the gas-liquid separation space 30f extend in the vertical direction. For this reason, the gas-liquid separation body 313, the gas-liquid separation space 30f, and the central axis are orthogonal to the central axis of the passage forming member 35 and the like.
 さらに、気液分離ボデー313は、ロワーボデー312の混合冷媒流出口31gから気液分離空間30f内へ流入した冷媒が、気液分離空間30fの外周側の壁面に沿って流入するように配置されている。これにより、気液分離空間30fでは、冷媒が中心軸周りに旋回することで生じる遠心力の作用によって、冷媒の気液を分離している。 Further, the gas-liquid separation body 313 is arranged so that the refrigerant that has flowed into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g of the lower body 312 flows along the outer peripheral wall surface of the gas-liquid separation space 30f. Yes. Thereby, in the gas-liquid separation space 30f, the gas-liquid of the refrigerant is separated by the action of the centrifugal force generated by the refrigerant turning around the central axis.
 気液分離ボデー313の軸中心部には、気液分離空間30fに対して同軸上に配置されて、上下方向へ延びる円筒状のパイプ313aが設けられている。そして、気液分離ボデー313の底面側の筒状側面には、気液分離空間30fにて分離された液相冷媒を気液分離空間30fの外周側壁面に沿って流出させる液相冷媒流出口31cが形成されている。さらに、パイプ313aの下方側端部には、気液分離空間30fにて分離された気相冷媒を流出させる気相冷媒流出口31dが形成されている。 At the axial center of the gas-liquid separation body 313, there is provided a cylindrical pipe 313a that is arranged coaxially with the gas-liquid separation space 30f and extends in the vertical direction. A liquid-phase refrigerant outlet through which the liquid-phase refrigerant separated in the gas-liquid separation space 30f flows out along the outer peripheral side wall surface of the gas-liquid separation space 30f is formed on the cylindrical side surface on the bottom side of the gas-liquid separation body 313. 31c is formed. Further, a gas-phase refrigerant outlet 31d through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out is formed at the lower end of the pipe 313a.
 また、気液分離空間30f内のパイプ313aの根元部(すなわち、気液分離空間30f内の最下方側の部位)には、気液分離空間30fとパイプ313a内に形成された気相冷媒通路とを連通させるオイル戻し穴313bが形成されている。オイル戻し穴313bは、液相冷媒に溶け込んだ冷凍機油を、液相冷媒とともに気相冷媒流出口31dを介して圧縮機11内へ戻すための連通路である。 In addition, a gas-phase refrigerant passage formed in the gas-liquid separation space 30f and the pipe 313a is formed at the root of the pipe 313a in the gas-liquid separation space 30f (that is, the lowermost portion in the gas-liquid separation space 30f). An oil return hole 313b is formed. The oil return hole 313b is a communication path for returning the refrigeration oil dissolved in the liquid refrigerant to the compressor 11 through the gas-phase refrigerant outlet 31d together with the liquid refrigerant.
 エジェクタ13の液相冷媒流出口31cには、図1に示すように、蒸発器14の冷媒入口側が接続されている。蒸発器14は、エジェクタ13にて減圧された低圧冷媒と送風ファン14aから車室内へ送風される送風空気とを熱交換させることによって、低圧冷媒を蒸発させて吸熱作用を発揮させる吸熱用熱交換器である。 As shown in FIG. 1, the refrigerant 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.
 送風ファン14aは、制御装置から出力される制御電圧によって回転数(送風空気量)が制御される電動送風機である。蒸発器14の出口側には、エジェクタ13の冷媒吸引口31bが接続されている。さらに、エジェクタ13の気相冷媒流出口31dには圧縮機11の吸入口側が接続されている。 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 port side of the compressor 11 is connected to the gas-phase refrigerant outlet 31 d of the ejector 13.
 次に、図示しない制御装置は、CPU、ROMおよびRAM等を含む周知のマイクロコンピュータとその周辺回路から構成される。この制御装置は、そのROM内に記憶された制御プログラムに基づいて各種演算、処理を行う。そして、上述の各種電気式のアクチュエータ11、12d、14a等の作動を制御する。 Next, a control device (not shown) 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 a control program stored in the ROM. Then, the operation of the above-described various electric actuators 11, 12d, 14a and the like is controlled.
 また、制御装置には、内気温センサ、外気温センサ、日射センサ、蒸発器温度センサ、吐出圧力センサ等の複数の空調制御用のセンサ群が接続され、これらのセンサ群の検出値が入力される。 In addition, a plurality of air conditioning control sensor groups such as an inside air temperature sensor, an outside air temperature sensor, a solar radiation sensor, an evaporator temperature sensor, and a discharge pressure sensor are connected to the control device, and detection values of these sensor groups are input. The
 より具体的には、内気温センサは、車室内温度を検出する内気温検出部である。外気温センサは、外気温を検出する外気温検出部である。日射センサは、車室内の日射量を検出する日射量検出部である。蒸発器温度センサは、蒸発器14の吹出空気温度(蒸発器温度)を検出する蒸発器温度検出部である。吐出圧力センサは、放熱器12出口側冷媒の圧力を検出する出口側圧力検出部である。 More specifically, the inside air temperature sensor is an inside air temperature detecting unit that detects the temperature inside the vehicle. The outside air temperature sensor is an outside air temperature detecting unit that detects the outside air temperature. A solar radiation sensor is a solar radiation amount detection part which detects the solar radiation amount in a vehicle interior. The evaporator temperature sensor is an evaporator temperature detector that detects the temperature of the blown air (evaporator temperature) of the evaporator 14. The discharge pressure sensor is an outlet-side pressure detection unit that detects the pressure of the radiator 12 outlet-side refrigerant.
 さらに、制御装置の入力側には、車室内前部の計器盤付近に配置された図示しない操作パネルが接続され、この操作パネルに設けられた各種操作スイッチからの操作信号が制御装置へ入力される。操作パネルに設けられた各種操作スイッチとしては、車室内空調を行うことを要求する空調作動スイッチ、車室内温度を設定する車室内温度設定スイッチ等が設けられている。 Furthermore, 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. The As 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.
 なお、本実施形態の制御装置は、その出力側に接続された各種の制御対象機器の作動を制御する制御部が一体に構成されたものであるが、制御装置のうち、各制御対象機器の作動を制御する構成(ハードウェアおよびソフトウェア)が各制御対象機器の制御部を構成している。 Note that the control device of the present embodiment is configured integrally with a control unit that controls the operation of various control target devices connected to the output side of the control device. A configuration (hardware and software) for controlling the operation constitutes a control unit of each control target device.
 例えば、本実施形態では、圧縮機11の吐出容量制御弁の作動を制御することによって、圧縮機11の冷媒吐出能力を制御する構成が吐出能力制御部を構成している。もちろん、吐出能力制御部を、制御装置に対して別体の制御装置で構成してもよい。 For example, in the present embodiment, the configuration for controlling the refrigerant discharge capacity of the compressor 11 by controlling the operation of the discharge capacity control valve of the compressor 11 constitutes the discharge capacity control unit. Of course, you may comprise a discharge capability control part with a separate control apparatus with respect to a control apparatus.
 次に、上記構成における本実施形態の作動を図5のモリエル線図を用いて説明する。まず、操作パネルの作動スイッチが投入(ON)されると、制御装置が圧縮機11の吐出容量制御弁、冷却ファン12d、送風ファン14a等を作動させる。これにより、圧縮機11が冷媒を吸入し、圧縮して吐出する。 Next, the operation of the present embodiment in the above configuration will be described using the Mollier diagram of FIG. First, when the operation switch of the operation panel is turned on (ON), the control device operates the discharge capacity control valve of the compressor 11, the cooling fan 12d, the blower fan 14a, and the like. Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it.
 圧縮機11から吐出された高温高圧冷媒(図5のa点)は、放熱器12の凝縮部12aへ流入し、冷却ファン12dから送風された外気と熱交換し、放熱して凝縮する。凝縮部12aにて凝縮した冷媒は、レシーバ部12bにて気液分離される。レシーバ部12bにて気液分離された液相冷媒は、過冷却部12cにて冷却ファン12dから送風された外気と熱交換し、さらに放熱して過冷却液相冷媒となる(図5のa点→b点)。 The high-temperature and high-pressure refrigerant discharged from the compressor 11 (point a in FIG. 5) flows into the condenser 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, and dissipates heat to condense. The refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid phase refrigerant separated from the gas and liquid by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d by the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a in FIG. 5). Point → b).
 放熱器12の過冷却部12cから流出した過冷却液相冷媒は、エジェクタ13の減圧用空間30bの内周面と通路形成部材35の外周面との間に形成されるノズル通路13aにて等エントロピ的に減圧されて噴射される(図5のb点→c点)。この際、減圧用空間30bの最小通路面積部30mにおける通路断面積は、蒸発器14出口側冷媒(図5のh点)の過熱度が基準過熱度KSHに近づくように調整される。 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 (point b → point c in FIG. 5). At this time, the passage cross-sectional area in the minimum passage area 30m of the decompression space 30b is adjusted so that the superheat degree of the evaporator 14 outlet side refrigerant (point h in FIG. 5) approaches the reference superheat degree KSH.
 さらに、ノズル通路13aから噴射された噴射冷媒の吸引作用によって、蒸発器14から流出した冷媒(図5のh点)が、冷媒吸引口31bおよび吸引用通路13bを介して吸引される。ノズル通路13aから噴射された噴射冷媒および吸引用通路13bを介して吸引された吸引冷媒は、ディフューザ通路13cへ流入して合流する(図5のc点→d点、h1点→d点)。 Furthermore, the refrigerant flowing out of the evaporator 14 (point h in FIG. 5) is sucked through the refrigerant suction port 31b and the suction passage 13b by the suction action of the injection refrigerant injected from the nozzle passage 13a. The injection refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b flow into the diffuser passage 13c and join (point c → d point, h1 point → d point in FIG. 5).
 ここで、本実施形態の吸引用通路13bの最下流部は、冷媒流れ方向に向かって通路断面積が徐々に縮小する形状に形成されている。このため、吸引用通路13bを通過する吸引冷媒は、その圧力を低下させながら(図5のh点→h1点)、流速を増加させる。 Here, the most downstream portion of the suction passage 13b of the present embodiment is formed in a shape in which the passage cross-sectional area gradually decreases in the refrigerant flow direction. For this reason, the suction refrigerant passing through the suction passage 13b increases the flow velocity while decreasing the pressure (point h → point h1 in FIG. 5).
 ディフューザ通路13cでは冷媒通路断面積の拡大により、冷媒の運動エネルギが圧力エネルギに変換される。これにより、噴射冷媒と吸引冷媒が混合されながら混合冷媒の圧力が上昇する(図5のd点→e点)。ディフューザ通路13cから流出した冷媒は気液分離空間30fにて気液分離される(図5のe点→f点、e点→g点)。 In the diffuser passage 13c, the kinetic energy of the refrigerant is converted into pressure energy by expanding the sectional area of the refrigerant passage. As a result, the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d → point e in FIG. 5). The refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (e point → f point, e point → g point in FIG. 5).
 気液分離空間30fにて分離された液相冷媒は、エジェクタ13から蒸発器14へ至る冷媒流路を流通する際に圧力損失を伴って蒸発器14へ流入する(図5のg点→g1点)。蒸発器14へ流入した冷媒は、送風ファン14aによって送風された送風空気から吸熱して蒸発する(図5のg1点→h点)。これにより、送風空気が冷却される。 The liquid-phase refrigerant separated in the gas-liquid separation space 30f flows into the evaporator 14 with pressure loss when flowing through the refrigerant flow path from the ejector 13 to the evaporator 14 (g point → g1 in FIG. 5). point). The refrigerant flowing into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates (g1 point → h point in FIG. 5). Thereby, blowing air is cooled.
 一方、気液分離空間30fにて分離された気相冷媒は気相冷媒流出口31dから流出して、圧縮機11へ吸入され再び圧縮される(図5のf点→a点)。 On the other hand, 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 f → a in FIG. 5).
 本実施形態のエジェクタ式冷凍サイクル10は、以上の如く作動して、車室内へ送風される送風空気を冷却することができる。 The ejector refrigeration cycle 10 of the present embodiment operates as described above, and can cool the blown air blown into the vehicle interior.
 本実施形態のエジェクタ式冷凍サイクル10では、ディフューザ通路13cにて昇圧された冷媒を圧縮機11へ吸入させている。従って、エジェクタ式冷凍サイクル10によれば、蒸発器における冷媒蒸発圧力と圧縮機吸入冷媒の圧力が略同等となる通常の冷凍サイクル装置よりも、圧縮機11の消費動力を低減させて、サイクルの成績係数(COP)を向上させることができる。 In the ejector refrigeration cycle 10 of the present embodiment, the refrigerant whose pressure has been increased in the diffuser passage 13c is sucked into the compressor 11. Therefore, according to the ejector-type refrigeration cycle 10, the power consumption of the compressor 11 can be reduced compared with the normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the refrigerant sucked by the compressor are substantially equal. Coefficient of performance (COP) can be improved.
 さらに、本実施形態のエジェクタ13では、駆動機構37を備えているので、エジェクタ式冷凍サイクル10の負荷変動に応じて通路形成部材35を変位させて、ノズル通路13aの通路断面積、およびディフューザ通路13cの通路断面積を調整することができる。 Furthermore, since the ejector 13 of the present embodiment includes the drive mechanism 37, the passage forming member 35 is displaced according to the load fluctuation of the ejector refrigeration cycle 10, and the passage sectional area of the nozzle passage 13a and the diffuser passage The passage cross-sectional area of 13c can be adjusted.
 従って、エジェクタ式冷凍サイクル10の負荷変動に応じて、内部に形成された冷媒通路(具体的には、ノズル通路13a、およびディフューザ通路13c)の通路断面積を変化させて、エジェクタ13を適切に作動させることができる。 Therefore, according to the load fluctuation of the ejector type refrigeration cycle 10, the passage cross-sectional areas of the refrigerant passages (specifically, the nozzle passage 13a and the diffuser passage 13c) formed inside are changed to appropriately adjust the ejector 13. Can be operated.
 ここで、本実施形態のエジェクタ13のように、エジェクタ式冷凍サイクル10の負荷変動に応じて通路形成部材35を変位させる構成では、通路形成部材35の中心軸CLが、流入空間30a、減圧用空間30b、昇圧用空間30e等の中心軸に対して傾いてしまうおそれがある。 Here, in the configuration in which the passage forming member 35 is displaced according to the load fluctuation of the ejector refrigeration cycle 10 as in the ejector 13 of the present embodiment, the central axis CL of the passage forming member 35 has the inflow space 30a and the pressure reducing portion. There is a risk of tilting with respect to the central axis of the space 30b, the boosting space 30e, and the like.
 そして、通路形成部材35の中心軸CLが傾いてしまうと、断面円環状の冷媒通路の通路断面積が周方向に変化してしまうため、高いエジェクタ効率を安定的に発揮できなくなってしまうおそれがある。 And if the central axis CL of the passage forming member 35 is inclined, the passage cross-sectional area of the refrigerant passage having an annular cross section changes in the circumferential direction, and thus there is a possibility that high ejector efficiency cannot be stably exhibited. is there.
 これに対して、本実施形態のエジェクタ13では、通路形成部材35とシャフト351の上流側作動棒351aが一体化されて、通路形成部材35の中心軸CLと上流側作動棒351aの中心軸が同軸上に配置されている。これにより、駆動機構37がシャフト351とともに通路形成部材35を変位させても、通路形成部材35の中心軸CLが傾いてしまうことを抑制することができる。 On the other hand, in the ejector 13 of the present embodiment, the passage forming member 35 and the upstream operating rod 351a of the shaft 351 are integrated, and the central axis CL of the passage forming member 35 and the central axis of the upstream operating rod 351a are It is arranged on the same axis. Thereby, even if the drive mechanism 37 displaces the channel | path formation member 35 with the shaft 351, it can suppress that the central axis CL of the channel | path formation member 35 inclines.
 さらに、本実施形態のエジェクタ13では、下流側作動棒351bを備えているので、通路形成部材35を中心軸CLの両端側で支持することができる。従って、より一層確実に、通路形成部材35の中心軸CLが傾いてしまうことを抑制することができる。その結果、エジェクタ効率が不安定となってしまうことを抑制することができる。 Furthermore, since the ejector 13 of the present embodiment includes the downstream operation rod 351b, the passage forming member 35 can be supported on both ends of the central axis CL. Therefore, it is possible to suppress the inclination of the central axis CL of the passage forming member 35 more reliably. As a result, it is possible to suppress the ejector efficiency from becoming unstable.
 また、本実施形態のエジェクタ13では、上流側作動棒351aが流入空間30aを貫通して、上流側作動棒351aの中心軸と流入空間30aの中心軸が同軸上に配置されている。これによれば、流入空間30a内の冷媒が中心軸周りに旋回しにくいだけでなく、仮に旋回してしまったとしても、流入空間30aの中心部に気柱が発生してしまうことを抑制することができる。 In the ejector 13 of the present embodiment, the upstream operating rod 351a passes through the inflow space 30a, and the central axis of the upstream operating rod 351a and the central axis of the inflow space 30a are arranged coaxially. This not only makes it difficult for the refrigerant in the inflow space 30a to turn around the central axis, but also suppresses the occurrence of an air column at the center of the inflow space 30a even if it turns. be able to.
 従って、通路形成部材35の中心軸CLが傾いて気柱の形態が不安定になってしまうこともない。その結果、エジェクタ効率が不安定となってしまうことを抑制することができる。さらに、流入空間30a内の冷媒に中心軸周りの旋回流れが生じにくいので、混合通路13dにて噴射冷媒と吸引冷媒とを混合させる際に、噴射冷媒と吸引冷媒との流れ方向の相違によって生じる混合損失の増加を抑制することができる。 Therefore, the central axis CL of the passage forming member 35 is not inclined and the form of the air column does not become unstable. As a result, it is possible to suppress the ejector efficiency from becoming unstable. Further, since the swirl flow around the central axis is unlikely to occur in the refrigerant in the inflow space 30a, it occurs due to the difference in the flow direction between the injected refrigerant and the sucked refrigerant when the injected refrigerant and the sucked refrigerant are mixed in the mixing passage 13d. An increase in mixing loss can be suppressed.
 また、本実施形態のエジェクタ13では、図4に示すように、混合通路13dの通路断面積が、冷媒流れ下流側へ向かって縮小している。これによれば、混合通路13d、およびディフューザ通路13cにて生じる損失を抑制することができる。 Further, in the ejector 13 of the present embodiment, as shown in FIG. 4, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow. According to this, the loss generated in the mixing passage 13d and the diffuser passage 13c can be suppressed.
 このことをより詳細に説明する。エジェクタ13では、ノズル通路13aから混合通路13dへ噴射される噴射冷媒は、液滴の慣性力の為、壁近傍の液体積割合が小さくなり、流速が流路中央より大きい傾向がある。つまり、ノズル通路13aから噴射された直後の噴射冷媒のうち液滴の流速は二相音速よりも大きく、ガス(すなわち、噴射冷媒のうち気相冷媒)の流速はガス音速より大きくなる場合がある。一方、吸引用通路13bから混合通路13dへ吸引される吸引冷媒の流速は音速よりも小さい。つまり、混合通路13dへ吸引された直後の吸引冷媒は亜音速状態となっている。 This will be explained in more detail. In the ejector 13, the jet refrigerant injected from the nozzle passage 13a to the mixing passage 13d has a liquid volume ratio in the vicinity of the wall due to the inertial force of the liquid droplets, and the flow velocity tends to be larger than the center of the flow path. That is, the flow velocity of the droplets of the injected refrigerant immediately after being injected from the nozzle passage 13a is larger than the two-phase sonic velocity, and the flow velocity of the gas (that is, the gas phase refrigerant of the injected refrigerant) may be larger than the sonic velocity of the gas. . On the other hand, the flow rate of the suction refrigerant sucked from the suction passage 13b to the mixing passage 13d is smaller than the speed of sound. That is, the suction refrigerant immediately after being sucked into the mixing passage 13d is in a subsonic speed state.
 この場合、混合通路13d内の冷媒には、図6の太破線に示すように、超音速状態の冷媒と亜音速状態の冷媒との間に速度境界層が形成され、混合通路13d内で流路断面積が流れ方向に減少する流れ(すなわち、先細流れ)になり、超音速のガス冷媒のマッハ数は低下する為、図6の二重細線に示すような斜め衝撃波が生じる。この衝撃波の後流のマッハ数が1を超える場合には、さらに図6の細線に示すような膨張波が発生し、そのさらに後流で衝撃波が発生するが、先細流れとすることで、その衝撃波の間隔を短くすることができ、発生回数も抑制できる(図6では2回発生)。 In this case, the refrigerant in the mixing passage 13d is formed with a velocity boundary layer between the supersonic state refrigerant and the subsonic state refrigerant as shown by a thick broken line in FIG. The road cross-sectional area becomes a flow that decreases in the flow direction (that is, a tapered flow), and the Mach number of the supersonic gas refrigerant decreases, so that an oblique shock wave as shown by a double thin line in FIG. 6 is generated. When the Mach number of the wake of the shock wave exceeds 1, an expansion wave as shown by a thin line in FIG. 6 is further generated, and a shock wave is further generated in the wake. The interval between shock waves can be shortened, and the number of occurrences can be suppressed (occurrence twice in FIG. 6).
 一方、図7のように、混合通路13d内の冷媒流れが先細流れとならない比較例のエジェクタであって、通路形成部材35が細破線で示すノズル通路13aの出口側の稜線と交わらないような形状においては、上記衝撃波の発生回数が増加しやすく(図7では、3回発生)、面積拡大区間(すなわち、ディフューザ通路13c)で衝撃波が発生する場合には、この衝撃波上流のマッハ数は1以上の為、面積拡大により減圧膨張し、エジェクタの圧力上昇量が低下する。 On the other hand, as shown in FIG. 7, it is an ejector of a comparative example in which the refrigerant flow in the mixing passage 13d is not a tapered flow, and the passage forming member 35 does not intersect the ridge line on the outlet side of the nozzle passage 13a indicated by the thin broken line. In the shape, the number of occurrences of the shock wave is likely to increase (in FIG. 7, it is generated three times). When a shock wave is generated in the area expansion section (that is, the diffuser passage 13c), the Mach number upstream of the shock wave is 1. For this reason, the expansion of the area is reduced and the pressure increase of the ejector is reduced.
 一般的な衝撃波のエントロピー生成量の式(F1)を用いて、衝撃波の損失(エントロピー生成量)を説明する。 The loss of the shock wave (entropy generation amount) will be described using the general formula (F1) of the shock wave entropy generation amount.
Figure JPOXMLDOC01-appb-M000001
 式(F1)において、s:エントロピ、γ:比熱比、R:気体定数、β:衝撃波角、M:マッハ数であり、添え字の1は衝撃波前、2は衝撃波後の物理量を表す。
Figure JPOXMLDOC01-appb-M000001
In the formula (F1), s: entropy, γ: specific heat ratio, R: gas constant, β: shock wave angle, M: Mach number, the subscript 1 represents the physical quantity before the shock wave, and 2 represents the physical quantity after the shock wave.
 このように、圧力上昇に対し損失となるエントロピー生成量は衝撃波角度とマッハ数が大きくなると増加する傾向にある。また、このエントロピー生成量は衝撃波の発生回数分大きくなる。 Thus, the amount of entropy generated that becomes a loss with respect to the pressure rise tends to increase as the shock wave angle and Mach number increase. In addition, the amount of entropy generation increases by the number of shock waves generated.
 そして、本実施形態の混合通路18dでは、噴射冷媒が図8の上段の実線矢印で示すように、N1→N2の順に2回衝撃波を発生させながら亜音速状態へ移行する。一方、比較例では、噴射冷媒が図8の上段の破線矢印に示すように、n1→n2→n3の順で、本実施形態よりも高いマッハ数で3回衝撃波を発生させながら亜音速状態へ移行する。 Then, in the mixing passage 18d of the present embodiment, the injected refrigerant shifts to the subsonic state while generating shock waves twice in the order of N1 → N2, as indicated by the solid arrow in the upper part of FIG. On the other hand, in the comparative example, as shown by the broken arrow in the upper part of FIG. 8, the injected refrigerant enters the subsonic state while generating shock waves three times at a Mach number higher than that of the present embodiment in the order of n 1 → n 2 → n 3. Transition.
 したがって、本実施形態のように混合通路13d内の冷媒流れを先細流れとし、流れのマッハ数を減少させることで、図8の下段に示すように、衝撃波によるエントロピー生成量(衝突を繰り返すことによって積算されるエネルギ損失)を低減させることができ、エネルギ変換効率を向上できる。 Therefore, as shown in the lower part of FIG. 8, the entropy generation amount by shock waves (by repeating the collision) is obtained by reducing the Mach number of the flow by reducing the flow of refrigerant in the mixing passage 13d as in the present embodiment. Energy loss) can be reduced, and energy conversion efficiency can be improved.
 その結果、本実施形態のエジェクタ13によれば、適用されたエジェクタ式冷凍サイクル10の負荷変動によらず、安定的に高いエネルギ変換効率を発揮させることができる。また、上記の如く、混合損失の増加を抑制できることは、吸引用通路13bの吸引冷媒出口13fがノズル通路13aの冷媒噴射口13eの外周側に環状に開口しているエジェクタ13において極めて有効である。 As a result, according to the ejector 13 of the present embodiment, high energy conversion efficiency can be stably exhibited regardless of the load fluctuation of the applied ejector refrigeration cycle 10. Further, as described above, the suppression of the increase in mixing loss is extremely effective in the ejector 13 in which the suction refrigerant outlet 13f of the suction passage 13b is annularly opened on the outer peripheral side of the refrigerant injection port 13e of the nozzle passage 13a. .
 また、本実施形態のエジェクタ13では、上流側作動棒351aの中心軸および下流側作動棒351bの中心軸が、互いに同軸上に配置されているので、通路形成部材35およびシャフト351をエジェクタ13の内部に組み付ける際の組み付け性を向上させることができる。 Further, in the ejector 13 of the present embodiment, since the central axis of the upstream operating rod 351a and the central axis of the downstream operating rod 351b are arranged coaxially with each other, the passage forming member 35 and the shaft 351 are connected to the ejector 13. The assembling property when assembling inside can be improved.
 さらに、上流側作動棒351aの先端部が駆動機構37のプレート部材374に連結されているので、通路形成部材35と駆動機構37とを複数の作動棒を介して連結する場合に対して容易に連結することができる。 Furthermore, since the tip of the upstream operating rod 351a is connected to the plate member 374 of the drive mechanism 37, it is easier to connect the passage forming member 35 and the drive mechanism 37 via a plurality of operating rods. Can be linked.
 また、本実施形態のエジェクタ13では、流入空間30aの中心軸方向から見たときに、冷媒流入通路31eが、流入空間30aへ流入する冷媒を流入空間30aの中心軸に向かって流入させるように形成されている。これによれば、より一層、流入空間30a内の冷媒に中心軸周りの旋回流れが発生してしまうことを抑制することができる。 In the ejector 13 of the present embodiment, the refrigerant inflow passage 31e causes the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a when viewed from the central axis direction of the inflow space 30a. Is formed. According to this, it is possible to further suppress the swirling flow around the central axis from occurring in the refrigerant in the inflow space 30a.
 さらに、本実施形態では、流入空間30a、減圧用空間30b、昇圧用空間30eの中心部に、上流側作動棒351a、通路形成部材35といった剛体が配置されている。従って、流入空間30a、減圧用空間30b、昇圧用空間30eによって形成される全ての冷媒通路の軸方向垂直断面形状が円環状となる。 Furthermore, in the present embodiment, rigid bodies such as the upstream operation rod 351a and the passage forming member 35 are arranged at the center of the inflow space 30a, the pressure reducing space 30b, and the pressure increasing space 30e. Accordingly, the axial vertical cross-sectional shapes of all the refrigerant passages formed by the inflow space 30a, the decompression space 30b, and the pressurization space 30e are annular.
 このため、これらの冷媒通路を流通する冷媒には、外周側壁面の壁面との摩擦および内周側の壁面との摩擦の双方の摩擦が生じるので、旋回流れが促進されてしまうことがない。 Therefore, in the refrigerant flowing through these refrigerant passages, both the friction with the wall surface of the outer peripheral side wall surface and the friction with the wall surface of the inner peripheral side are generated, so that the swirl flow is not promoted.
 また、本実施形態のエジェクタ13では、混合通路13dの最小通路断面積は、冷媒噴射口13eの通路断面積および吸引冷媒出口13fの通路断面積の合計値よりも小さく形成されている。これによれば、混合通路13dにおける噴射冷媒と混合冷媒との混合性を向上させることができる。 Further, in the ejector 13 of the present embodiment, the minimum passage sectional area of the mixing passage 13d is formed smaller than the total value of the passage sectional area of the refrigerant injection port 13e and the passage sectional area of the suction refrigerant outlet 13f. According to this, the mixing property of the injection refrigerant and the mixed refrigerant in the mixing passage 13d can be improved.
 また、本実施形態のエジェクタ13では、混合冷媒流出口31gの通路断面積がディフューザ通路13cの最下流部の通路断面積よりも小さく形成されており、さらに、ディフューザ通路13cから流出した気液混合状態の冷媒を気液分離空間30fの外周側の壁面に沿って流入させている。これによれば、気液分離空間30fにて生じる冷媒の圧力損失を低減させることができる。 Further, in the ejector 13 of the present embodiment, the passage sectional area of the mixed refrigerant outlet 31g is formed to be smaller than the passage sectional area of the most downstream portion of the diffuser passage 13c, and further the gas-liquid mixture flowing out of the diffuser passage 13c The refrigerant in the state is caused to flow along the outer peripheral wall surface of the gas-liquid separation space 30f. According to this, the pressure loss of the refrigerant generated in the gas-liquid separation space 30f can be reduced.
 このことをより詳細に説明すると、混合冷媒流出口31gでは、通路断面積の縮小によって冷媒の静圧低下が生じるものの、混合冷媒流出口31gから気液分離空間30f内へ流入する冷媒は、気液分離ボデー313の内周壁面(すなわち、気液分離空間30fの外周側の壁面)に沿って流入する。 This will be described in more detail. At the mixed refrigerant outlet 31g, the static pressure of the refrigerant decreases due to the reduction of the passage cross-sectional area, but the refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g It flows along the inner peripheral wall surface of the liquid separation body 313 (that is, the outer peripheral wall surface of the gas-liquid separation space 30f).
 このため、混合冷媒流出口31gから気液分離空間30f内へ流入する気相冷媒は、気液分離空間30f内へ流入した際の体積の急拡大が抑制されるので、体積拡大によるエネルギ損失を抑制できる。一方、混合冷媒流出口31gから気液分離空間30f内へ流入する液相冷媒については、比較的影響の少ない壁面摩擦分しかエネルギ損失が生じない。 For this reason, since the vapor phase refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g is suppressed from rapidly expanding when it flows into the gas-liquid separation space 30f, energy loss due to volume expansion is reduced. Can be suppressed. On the other hand, with respect to the liquid-phase refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g, energy loss occurs only for the wall friction that has relatively little influence.
 従って、混合冷媒流出口31gから比較的体積の大きい気液分離空間30f内へ流入した冷媒の運動エネルギが、大きく損失してしまうことなく圧力エネルギに変換されて、冷媒の静圧が回復する。これにより、気液分離空間30fにて生じる冷媒の圧力損失を低減させることができる。 Therefore, the kinetic energy of the refrigerant that has flowed into the gas-liquid separation space 30f having a relatively large volume from the mixed refrigerant outlet 31g is converted into pressure energy without loss, and the static pressure of the refrigerant is restored. Thereby, the pressure loss of the refrigerant | coolant produced in the gas-liquid separation space 30f can be reduced.
 さらに、この圧力回復によって、気液分離空間30f内の圧力と圧縮機11の吸入口側の圧力との圧力差を確保することができる。これにより、液相冷媒に溶け込んだ冷凍機油を、オイル戻し穴313bを介して、確実に圧縮機11の吸入口側へ戻すことができる。 Furthermore, by this pressure recovery, a pressure difference between the pressure in the gas-liquid separation space 30f and the pressure on the suction port side of the compressor 11 can be secured. Thereby, the refrigerating machine oil dissolved in the liquid-phase refrigerant can be reliably returned to the suction port side of the compressor 11 through the oil return hole 313b.
 (第2実施形態)
 本実施形態では、第1実施形態のエジェクタ13に対して、図9の拡大断面図に示すように、通路形成部材35の頂部側にノズル通路13aの通路断面積を拡大させる側に凹んだ凹み部を形成した例を説明する。なお、図9は、第1実施形態で説明した図4に対応する図面である。また、図9では、第1実施形態と同一もしくは均等部分には同一の符号を付している。このことは、以下の図面でも同様である。
(Second Embodiment)
In the present embodiment, with respect to the ejector 13 of the first embodiment, as shown in the enlarged sectional view of FIG. The example which formed the part is demonstrated. FIG. 9 is a drawing corresponding to FIG. 4 described in the first embodiment. Moreover, in FIG. 9, the same code | symbol is attached | subjected to the same or equivalent part as 1st Embodiment. The same applies to the following drawings.
 具体的には、本実施形態の凹み部は、通路形成部材35の頂部側に形成されて、通路形成部材35の円錐状側面を中心軸CLに垂直な方向に貫通する貫通穴35aで構成されている。貫通穴35aは、ノズル通路13aの最小通路面積部30mよりも冷媒流れ上流側に位置付けられるように形成されている。 Specifically, the recessed portion of the present embodiment is formed by a through hole 35a that is formed on the top side of the passage forming member 35 and penetrates the conical side surface of the passage forming member 35 in a direction perpendicular to the central axis CL. ing. The through hole 35a is formed so as to be positioned upstream of the refrigerant flow with respect to the minimum passage area 30m of the nozzle passage 13a.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成および作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第1実施形態と同様の効果を得ることができる。 Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment.
 さらに、本実施形態のエジェクタ13の通路形成部材35には、貫通穴35aが設けられているので、ノズル通路13aの冷媒通路断面積を急拡大させて沸騰核を生成することができる。従って、ノズル通路13aにおける冷媒の沸騰を促進して、ノズル通路13aにおけるエネルギ変換効率を向上させることができる。 Furthermore, since the passage forming member 35 of the ejector 13 of the present embodiment is provided with a through hole 35a, the boiling passage nuclei can be generated by rapidly expanding the refrigerant passage cross-sectional area of the nozzle passage 13a. Therefore, the boiling of the refrigerant in the nozzle passage 13a can be promoted, and the energy conversion efficiency in the nozzle passage 13a can be improved.
 また、本実施形態のエジェクタ13では、貫通穴35aが設けられているので、断面円環状に形成されるノズル通路13aの周方向の圧力分布を抑制することができる。従って、仮に、通路形成部材35の中心軸CLが傾いてしまったとしても、エジェクタ効率が大きく低下してしまうことを抑制することができる。また、貫通穴35aの数は1つに限定されることなく、周方向に複数設けられて、等角度間隔に配置されていてもよい。 Further, in the ejector 13 of the present embodiment, since the through hole 35a is provided, the pressure distribution in the circumferential direction of the nozzle passage 13a formed in an annular cross section can be suppressed. Therefore, even if the central axis CL of the passage forming member 35 is inclined, it is possible to prevent the ejector efficiency from being greatly reduced. The number of through holes 35a is not limited to one, and a plurality of through holes 35a may be provided in the circumferential direction and arranged at equal angular intervals.
 (第3実施形態)
 本実施形態では、第1実施形態のエジェクタ13に対して、図10の拡大断面図に示すように、通路形成部材35の頂部側にノズル通路13aの通路断面積を拡大させる側に凹んだ凹み部を形成した例を説明する。なお、図10は、第1実施形態で説明した図4に対応する図面である。
(Third embodiment)
In the present embodiment, as shown in the enlarged sectional view of FIG. 10 with respect to the ejector 13 of the first embodiment, a dent recessed on the top side of the passage forming member 35 on the side where the passage sectional area of the nozzle passage 13a is enlarged The example which formed the part is demonstrated. FIG. 10 is a drawing corresponding to FIG. 4 described in the first embodiment.
 具体的には、本実施形態の凹み部は、通路形成部材35の頂部側に形成されて、通路形成部材35の中心軸CL周りの全周に亘って形成された溝部35bで構成されている。溝部35bは、ノズル通路13aの最小通路面積部30mよりも冷媒流れ上流側に位置付けられるように形成されている。 Specifically, the recess portion of the present embodiment is formed by a groove portion 35 b formed on the top side of the passage forming member 35 and formed over the entire circumference around the central axis CL of the passage forming member 35. . The groove 35b is formed to be positioned upstream of the refrigerant flow with respect to the minimum passage area 30m of the nozzle passage 13a.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成および作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第1実施形態と同様の効果を得ることができる。 Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment.
 さらに、本実施形態のエジェクタ13の通路形成部材35には、溝部35bが設けられているので、ノズル通路13aの冷媒通路断面積を急拡大させて沸騰核を生成することができる。従って、ノズル通路13aにおける冷媒の沸騰を促進して、ノズル通路13aにおけるエネルギ変換効率を向上させることができる。 Furthermore, since the channel forming member 35 of the ejector 13 of the present embodiment is provided with the groove 35b, it is possible to generate a boiling nucleus by rapidly expanding the refrigerant channel cross-sectional area of the nozzle channel 13a. Therefore, the boiling of the refrigerant in the nozzle passage 13a can be promoted, and the energy conversion efficiency in the nozzle passage 13a can be improved.
 また、本実施形態のエジェクタ13では、溝部35bが設けられているので、仮に、通路形成部材35の中心軸CLが傾いてしまったとしても、傾きに応じて沸騰核の生成量が調整される。これにより、第2実施形態と同様に、断面円環状に形成されるノズル通路13aの周方向の圧力分布を抑制することができる。 In the ejector 13 of the present embodiment, since the groove portion 35b is provided, even if the central axis CL of the passage forming member 35 is inclined, the amount of boiling nuclei generated is adjusted according to the inclination. . Thereby, similarly to 2nd Embodiment, the pressure distribution of the circumferential direction of the nozzle channel | path 13a formed in an annular | circular shaped cross section can be suppressed.
 なお、本実施形態のエジェクタ13では、溝部35bを通路形成部材35の中心軸周りの全周に亘って形成した例を説明したが、溝部35bの形状はこれに限定されない。複数の円環状の溝部を中心軸周りの全周に亘って形成してもよいし、複数の溝部を通路形成部材35の中心軸周りに不連続的に円環状に形成してもよい。 In addition, in the ejector 13 of this embodiment, although the example which formed the groove part 35b over the perimeter around the central axis of the channel | path formation member 35 was demonstrated, the shape of the groove part 35b is not limited to this. A plurality of annular groove portions may be formed over the entire circumference around the central axis, or a plurality of groove portions may be formed in an annular shape discontinuously around the central axis of the passage forming member 35.
 (第4実施形態)
 本実施形態では、第1実施形態のエジェクタ13に対して、図11に示すように、混合通路13dの形状を変更した例を説明する。
(Fourth embodiment)
This embodiment demonstrates the example which changed the shape of the mixing channel | path 13d as shown in FIG. 11 with respect to the ejector 13 of 1st Embodiment.
 具体的には、本実施形態の通路形成部材35のうち混合通路13dを形成する壁面が中心軸CLを含む断面に描く線は、冷媒流れ下流側へ向かってディフューザボデー33側に近づくように傾斜している。これにより、混合通路13dの通路断面積は、冷媒流れ下流側へ向かって縮小している。 Specifically, a line drawn on a cross section including the central axis CL of the wall surface forming the mixing passage 13d in the passage forming member 35 of the present embodiment is inclined so as to approach the diffuser body 33 side toward the downstream side of the refrigerant flow. is doing. Thereby, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow.
 なお、図11は、第1実施形態で説明した図6に対応する模式的な拡大断面図である。また、図11では、説明の明確化のために、第1実施形態の通路形成部材35の円錐状側面に対応する断面形状を細破線で示している。 FIG. 11 is a schematic enlarged cross-sectional view corresponding to FIG. 6 described in the first embodiment. Moreover, in FIG. 11, the cross-sectional shape corresponding to the conical side surface of the channel | path formation member 35 of 1st Embodiment is shown with the thin broken line for clarification of description.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成および作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第1実施形態と同様の効果を得ることができる。 Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment.
 つまり、本実施形態では、通路形成部材35の円錐状側面を傾斜させることによって、混合通路13dの通路断面積を冷媒流れ下流側へ向かって縮小させている。このように混合通路13dを形成しても、第1実施形態と同様に、ディフューザ通路13cの昇圧性能を安定化させて、エジェクタ効率が不安定となってしまうことを抑制することができるとともに、噴射冷媒と吸引冷媒とを混合させる際に生じる混合損失を抑制することができる。 That is, in this embodiment, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow by inclining the conical side surface of the passage forming member 35. Even if the mixing passage 13d is formed in this way, the boosting performance of the diffuser passage 13c can be stabilized and the ejector efficiency can be prevented from becoming unstable, as in the first embodiment. Mixing loss that occurs when the injection refrigerant and the suction refrigerant are mixed can be suppressed.
 (第5実施形態)
 本実施形態では、第1実施形態のエジェクタ13に対して、図12に示すように、通路形成部材35等の形状を変更した例を説明する。なお、図12は、本実施形態のエジェクタ13の拡大断面図であって、第1実施形態で説明した図4のXII部に対応する部位の模式的な拡大断面図である。
(Fifth embodiment)
In the present embodiment, an example will be described in which the shape of the passage forming member 35 and the like is changed as shown in FIG. 12 with respect to the ejector 13 of the first embodiment. FIG. 12 is an enlarged cross-sectional view of the ejector 13 of the present embodiment, and is a schematic enlarged cross-sectional view of a portion corresponding to the XII portion of FIG. 4 described in the first embodiment.
 具体的には、本実施形態のエジェクタ13では、通路形成部材35のうちノズル通路13aを形成する壁面が中心軸CLを含む断面に描く線(以下、内側線という。)350は、ノズル通路13a側に尖った形状を含んでいる。より詳細には、この内側線350は、複数の直線あるいは曲線を組み合わせた形状となっており、ノズル通路13a側に凸となる角部350a、350bを形成している。 Specifically, in the ejector 13 of the present embodiment, a line (hereinafter referred to as an inner line) 350 drawn on a cross section including a central axis CL of the wall surface forming the nozzle passage 13a in the passage forming member 35 is the nozzle passage 13a. Includes a pointed shape on the side. More specifically, the inner line 350 is formed by combining a plurality of straight lines or curves, and forms corners 350a and 350b that protrude toward the nozzle passage 13a.
 また、本実施形態のエジェクタ13では、ノズル32のうちノズル通路13aを形成する壁面が中心軸CLを含む断面に描く線(以下、外側線という。)320は、ノズル通路13a側に尖った形状を含んでいる。より詳細には、この外側線320は、複数の直線あるいは曲線を組み合わせた形状となっており、ノズル通路13a側に凸となる角部320a、320bを形成している。 In the ejector 13 of the present embodiment, a line (hereinafter, referred to as an outer line) 320 drawn on a cross section including the central axis CL of the wall surface forming the nozzle passage 13a of the nozzle 32 has a sharp shape toward the nozzle passage 13a. Is included. More specifically, the outer line 320 has a shape formed by combining a plurality of straight lines or curves, and forms corners 320a and 320b that protrude toward the nozzle passage 13a.
 さらに、内側線350および外側線320は、中心軸CLを含む断面に仮想的に定めた仮想基準線に対して線対称となるように形成されている。 Furthermore, the inner line 350 and the outer line 320 are formed so as to be line-symmetric with respect to a virtual reference line that is virtually determined in a cross section including the central axis CL.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成および作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第1実施形態と同様の効果を得ることができる。 Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment.
 さらに、本実施形態のエジェクタ13の通路形成部材35には、角部350a、350bが形成されているので、ノズル通路13aを流通する冷媒の流れ方向を転向させてノズル通路13aの中心軸側に沸騰核を生成することができる。つまり、角部350a、350bを沸騰起点として、ノズル通路13aにおける冷媒の沸騰を促進することができる。 Furthermore, since the corner portions 350a and 350b are formed in the passage forming member 35 of the ejector 13 of the present embodiment, the flow direction of the refrigerant flowing through the nozzle passage 13a is turned to the central axis side of the nozzle passage 13a. Boiling nuclei can be generated. That is, the boiling of the refrigerant in the nozzle passage 13a can be promoted with the corner portions 350a and 350b as the boiling start points.
 同様に、ノズル32には、角部320a、320bが形成されているので、ノズル通路13aを流通する冷媒の流れ方向を転向させてノズル通路13aの外周側に沸騰核を生成することができる。つまり、角部320a、320bを沸騰起点として、ノズル通路13aにおける冷媒の沸騰を促進することができる。 Similarly, since the corners 320a and 320b are formed in the nozzle 32, the flow direction of the refrigerant flowing through the nozzle passage 13a can be turned to generate boiling nuclei on the outer peripheral side of the nozzle passage 13a. That is, the boiling of the refrigerant in the nozzle passage 13a can be promoted with the corner portions 320a and 320b as the boiling start points.
 また、本実施形態では内側線と外側線が、基準線に対して線対称となるように形成されているので、ノズル通路13aを流通する冷媒に対して、内周側および外周側の双方から同時に沸騰核を供給することができる。従って、ノズル通路13aを流通する冷媒に均等に沸騰核を供給しやすい。 Further, in the present embodiment, the inner line and the outer line are formed so as to be line symmetric with respect to the reference line, so that the refrigerant flowing through the nozzle passage 13a is viewed from both the inner and outer peripheral sides. At the same time, boiling nuclei can be supplied. Therefore, it is easy to supply the boiling nuclei equally to the refrigerant flowing through the nozzle passage 13a.
 その結果、ノズル通路13aにおける冷媒の沸騰を効果的に促進させて、より一層、ノズル通路13aにおけるエネルギ変換効率を向上させることができる。 As a result, the boiling of the refrigerant in the nozzle passage 13a can be effectively promoted, and the energy conversion efficiency in the nozzle passage 13a can be further improved.
 (第6実施形態)
 本実施形態では、第1実施形態のエジェクタ13に対して、図13に示すように、通路形成部材35の頂部側に環状部材352を配置した例を説明する。なお、図13は、第1実施形態で説明した図4に対応する模式的な拡大断面図である。また、本実施形態では、ノズル32のノズル通路13aを形成する部位のうち、最も内径の小さい部位を最小内径部30qとする。
(Sixth embodiment)
In the present embodiment, an example will be described in which an annular member 352 is arranged on the top side of the passage forming member 35 as shown in FIG. 13 with respect to the ejector 13 of the first embodiment. FIG. 13 is a schematic enlarged cross-sectional view corresponding to FIG. 4 described in the first embodiment. Moreover, in this embodiment, the site | part with the smallest internal diameter among the site | parts which form the nozzle channel | path 13a of the nozzle 32 is made into the minimum internal diameter part 30q.
 具体的には、環状部材352は、通路形成部材35と同じ材質で形成された円環状部材である。環状部材352の外形は、2つの円錐台の底面側同士を結合させた回転体形状に形成されている。 Specifically, the annular member 352 is an annular member formed of the same material as the passage forming member 35. The outer shape of the annular member 352 is formed in a rotating body shape in which the bottom sides of the two truncated cones are coupled to each other.
 環状部材352は、中心軸方向の略中央部に最大外径部30nを有し、冷媒流れ最下流部に最小外径部30pを有する形状に形成されている。なお、本実施形態では、環状部材352と通路形成部材35とを別部材で形成しているが、通路形成部材35等をボデー30の内部に組付可能であれば、環状部材352と通路形成部材35とを一体的に形成してもよい。 The annular member 352 is formed in a shape having a maximum outer diameter portion 30n at a substantially central portion in the central axis direction and a minimum outer diameter portion 30p at the most downstream portion of the refrigerant flow. In this embodiment, the annular member 352 and the passage forming member 35 are formed as separate members. However, if the passage forming member 35 or the like can be assembled inside the body 30, the annular member 352 and the passage forming are formed. The member 35 may be integrally formed.
 次に、本実施形態のノズル通路13aについて説明する。通路形成部材35の頂部側には、環状部材352が配置されている。このため、ノズル通路13aの中心軸CL側(すなわち、通路形成部材35および環状部材352側)の壁面が軸方向断面に描く形状は、図13に示すように、環状部材352の上流側から最大外径部30nへ至る範囲では冷媒流れ下流側に向かって、中心軸CLから離れる形状となっている。 Next, the nozzle passage 13a of this embodiment will be described. An annular member 352 is disposed on the top side of the passage forming member 35. For this reason, the shape that the wall surface of the nozzle passage 13a on the center axis CL side (that is, the passage forming member 35 and the annular member 352 side) draws in the axial cross section is the largest from the upstream side of the annular member 352 as shown in FIG. In the range reaching the outer diameter portion 30n, the shape is separated from the central axis CL toward the downstream side of the refrigerant flow.
 さらに、最大外径部30nから最小外径部30pへ至る範囲では冷媒流れ下流側に向かって、中心軸CLへ近づく形状となっている。最小外径部30pから冷媒流れ下流側に向かって、中心軸CLから離れる形状となっている。 Further, in the range from the maximum outer diameter portion 30n to the minimum outer diameter portion 30p, the shape approaches the central axis CL toward the refrigerant flow downstream side. The shape is separated from the central axis CL toward the downstream side of the refrigerant flow from the minimum outer diameter portion 30p.
 一方、ノズル通路13aの中心軸CLの反対側(すなわち、ノズル32の減圧用空間30bを形成する部位側)の壁面が軸方向断面に描く形状は、図13に示すように、流入空間30a側から最小内径部30qへ至る範囲では冷媒流れ下流側に向かって、中心軸CLへ近づく形状となっている。さらに、最小内径部30qから冷媒流れ下流側に向かって、中心軸CLから離れる形状となっている。 On the other hand, the shape of the wall surface on the opposite side of the central axis CL of the nozzle passage 13a (that is, the side of the nozzle 32 forming the decompression space 30b) in the axial cross section is as shown in FIG. In the range from to the minimum inner diameter portion 30q, the shape approaches the central axis CL toward the refrigerant flow downstream side. Further, the shape is separated from the central axis CL from the minimum inner diameter portion 30q toward the downstream side of the refrigerant flow.
 このため、本実施形態のノズル通路13aの先細部131は、図13に示すように、第1先細部131a、第2先細部131bに大別される。 For this reason, the tapered portion 131 of the nozzle passage 13a of the present embodiment is roughly divided into a first tapered portion 131a and a second tapered portion 131b as shown in FIG.
 第1先細部131aは、環状部材352の冷媒流れ上流部側から最大外径部30nへ至る範囲に形成されて、通路断面積が徐々に縮小する冷媒通路である。第2先細部131bは、環状部材352の最大外径部30nからノズル32の最小内径部30qへ至る範囲に形成されて、第1先細部131aの直後の通路断面積を拡大させた後に縮小させる冷媒通路である。 The first tapered portion 131a is a refrigerant passage that is formed in a range from the refrigerant flow upstream side of the annular member 352 to the maximum outer diameter portion 30n, and the passage cross-sectional area gradually decreases. The second tapered portion 131b is formed in a range from the maximum outer diameter portion 30n of the annular member 352 to the minimum inner diameter portion 30q of the nozzle 32, and is enlarged after the passage sectional area immediately after the first tapered portion 131a is reduced. It is a refrigerant passage.
 つまり、本実施形態では、環状部材352の最大外径部30n、およびノズル32の最小内径部30qによって、ノズル通路13aの通路断面積を冷媒流れ下流側に向かって徐々に縮小させた後に、少なくとも一部の冷媒の流れ方向を急転向させるスロート部が形成されている。 That is, in the present embodiment, after the passage cross-sectional area of the nozzle passage 13a is gradually reduced toward the downstream side of the refrigerant flow by the maximum outer diameter portion 30n of the annular member 352 and the minimum inner diameter portion 30q of the nozzle 32, at least A throat portion that rapidly changes the flow direction of some of the refrigerant is formed.
 さらに、環状部材352の最大外径部30nは、冷媒流れ最上流側に配置された最上流側スロート部である。そして、最大外径部30nが形成されていることによって、ノズル通路13aは中心軸CL側へ通路断面積を拡大させる形状になっている。また、最大外径部30nは、ノズル通路13aのうち亜音速状態の冷媒が流通する領域に配置されている。 Furthermore, the maximum outer diameter portion 30n of the annular member 352 is the most upstream throat portion arranged on the most upstream side of the refrigerant flow. Further, since the maximum outer diameter portion 30n is formed, the nozzle passage 13a has a shape that enlarges the passage sectional area toward the central axis CL. Further, the maximum outer diameter portion 30n is disposed in a region where the subsonic refrigerant flows in the nozzle passage 13a.
 一方、ノズル32の最小内径部30qは、最上流側スロート部よりも冷媒流れ下流側に配置された下流側スロート部である。最小内径部30qは、ノズル通路13aの通路断面積を通路形成部材35の中心軸CLから離れる側に拡大させる形状に形成されている。 On the other hand, the minimum inner diameter portion 30q of the nozzle 32 is a downstream throat portion arranged downstream of the refrigerant flow with respect to the most upstream throat portion. The minimum inner diameter portion 30q is formed in a shape that enlarges the passage cross-sectional area of the nozzle passage 13a to the side away from the central axis CL of the passage forming member 35.
 つまり、本実施形態のノズル通路13aは、複数(本実施形態では、2つ)のスロート部(喉部)を有する二段絞り型のラバールノズルとして機能するように通路断面積が変化する。これにより、ノズル通路13aでは、冷媒を減圧させるとともに、冷媒の流速を超音速となるように増速させて噴射している。 That is, the passage cross-sectional area of the nozzle passage 13a of the present embodiment changes so as to function as a two-stage throttle type Laval nozzle having a plurality of (two in the present embodiment) throat portions (throat portions). Thus, in the nozzle passage 13a, the pressure of the refrigerant is reduced and the flow rate of the refrigerant is increased to be supersonic and injected.
 さらに、本実施形態のノズル通路13aでは、最上流側スロート部(すなわち、環状部材352の最大外径部30n)によって形成される冷媒通路の最小通路断面積が、下流側スロート部(すなわち、ノズル32の最小内径部30q)によって形成される冷媒通路の最小通路断面積よりも小さくなるように、環状部材352およびノズル32の寸法が設定されている。 Furthermore, in the nozzle passage 13a of the present embodiment, the minimum passage cross-sectional area of the refrigerant passage formed by the most upstream throat portion (that is, the maximum outer diameter portion 30n of the annular member 352) is the downstream throat portion (that is, the nozzle The dimensions of the annular member 352 and the nozzle 32 are set to be smaller than the minimum passage cross-sectional area of the refrigerant passage formed by the 32 minimum inner diameter portion 30q).
 このため、駆動機構37が通路形成部材35を変位させて、ノズル通路13aを閉塞させる際には、環状部材352の最大外径部30nがノズル32に接触する。 Therefore, when the drive mechanism 37 displaces the passage forming member 35 to close the nozzle passage 13a, the maximum outer diameter portion 30n of the annular member 352 contacts the nozzle 32.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成および作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第1実施形態と同様の効果を得ることができる。 Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment.
 つまり、本実施形態のエジェクタ13では、最上流側スロート部を構成する環状部材352の最大外径部30nが、ノズル通路13aのうち亜音速状態の冷媒が流通する領域に形成されており、最大外径部30nがノズル通路13aの通路断面積を急拡大させて剥離渦を発生させるエッジとして機能する。従って、ノズル通路13aを流通する液相冷媒中に沸騰核を生成することができる。 That is, in the ejector 13 of the present embodiment, the maximum outer diameter portion 30n of the annular member 352 constituting the most upstream throat portion is formed in a region where the subsonic refrigerant flows in the nozzle passage 13a. The outer diameter portion 30n functions as an edge that rapidly expands the cross-sectional area of the nozzle passage 13a to generate a separation vortex. Therefore, boiling nuclei can be generated in the liquid-phase refrigerant flowing through the nozzle passage 13a.
 さらに、最上流側スロート部を構成する環状部材352の最大外径部30nが、通路形成部材35側(すなわち、中心軸CL側)に形成されている。そして、ノズル通路13aの少なくとも一部の形状が、冷媒の流れ方向を通路形成部材35の中心軸CL側へ転向させる形状に形成されている。 Furthermore, the maximum outer diameter portion 30n of the annular member 352 constituting the most upstream throat portion is formed on the passage forming member 35 side (that is, the central axis CL side). The shape of at least a part of the nozzle passage 13 a is formed to turn the refrigerant flow direction toward the central axis CL of the passage forming member 35.
 これによれば、ノズル通路13aを流通する液相冷媒に中心軸CL側から沸騰核を供給することができる。従って、流入空間30a内の冷媒に気柱等が生成されていなくても、ノズル通路13aを流通する冷媒の沸騰を促進することができ、エジェクタ効率を向上させることができる。 According to this, the boiling nuclei can be supplied from the central axis CL side to the liquid refrigerant flowing through the nozzle passage 13a. Therefore, even if an air column or the like is not generated in the refrigerant in the inflow space 30a, the boiling of the refrigerant flowing through the nozzle passage 13a can be promoted, and the ejector efficiency can be improved.
 これに加えて、本実施形態のエジェクタ13では、下流側スロート部を構成するノズル32の最小内径部30qが、ノズル32の減圧用空間30bを形成する部位に形成されている。そして、ノズル通路13aの少なくとも一部の形状が、冷媒の流れ方向を通路形成部材35の中心軸CLから離れる側へ転向させる形状に形成されている。 In addition to this, in the ejector 13 of the present embodiment, the minimum inner diameter portion 30q of the nozzle 32 constituting the downstream throat portion is formed in a portion where the pressure reducing space 30b of the nozzle 32 is formed. The shape of at least a part of the nozzle passage 13 a is formed to turn the refrigerant flow direction away from the central axis CL of the passage forming member 35.
 これによれば、ノズル通路13aを流通する液相冷媒に外周側からも沸騰核を供給することができる。従って、より一層、ノズル通路13aを流通する冷媒の沸騰を促進することができる。 According to this, boiling nuclei can be supplied from the outer peripheral side to the liquid-phase refrigerant flowing through the nozzle passage 13a. Therefore, the boiling of the refrigerant flowing through the nozzle passage 13a can be further promoted.
 また、本実施形態のエジェクタ13では、環状部材352の最大外径部30nによって形成される冷媒通路の最小通路断面積が、ノズル32の最小内径部30qによって形成される冷媒通路の最小通路断面積よりも小さくなっている。 Further, in the ejector 13 of the present embodiment, the minimum passage sectional area of the refrigerant passage formed by the maximum outer diameter portion 30n of the annular member 352 is the minimum passage sectional area of the refrigerant passage formed by the minimum inner diameter portion 30q of the nozzle 32. Is smaller than
 従って、最大外径部30nによって形成される冷媒通路の通路断面積を変化させることで、ノズル通路13aを流通する冷媒の流量を調整することができる。さらに、最大外径部30nによって形成される冷媒通路には亜音速の冷媒が流通し、冷媒は最大外径部30nの下流側で超音速の臨界状態となるので、最大外径部30nによって形成される冷媒通路おいて冷媒流量を精度良く調整することができる。 Therefore, the flow rate of the refrigerant flowing through the nozzle passage 13a can be adjusted by changing the passage sectional area of the refrigerant passage formed by the maximum outer diameter portion 30n. Further, the subsonic refrigerant flows through the refrigerant passage formed by the maximum outer diameter portion 30n, and the refrigerant enters a supersonic critical state downstream of the maximum outer diameter portion 30n. Therefore, the refrigerant is formed by the maximum outer diameter portion 30n. The refrigerant flow rate can be accurately adjusted in the refrigerant passage.
 (第7実施形態)
 本実施形態では、第6実施形態のエジェクタ13に対して、図14の拡大断面図に示すように、通路形成部材35の頂部側の環状部材353の形状、並びに、ノズル32の減圧用空間30bを形成する部位の形状を変更した例を説明する。なお、図14は、第6実施形態で説明した図13に対応する図面である。
(Seventh embodiment)
In the present embodiment, the shape of the annular member 353 on the top side of the passage forming member 35 and the pressure reducing space 30b of the nozzle 32 are compared with the ejector 13 of the sixth embodiment as shown in the enlarged sectional view of FIG. An example will be described in which the shape of the part that forms the shape is changed. FIG. 14 is a drawing corresponding to FIG. 13 described in the sixth embodiment.
 より具体的には、本実施形態の環状部材353の外形は、2つの円錐台の頂部側同士を結合させた回転体形状に形成されている。従って、本実施形態の環状部材353は、冷媒流れ最上流側に最大外径部30nを有し、中心軸方向の略中央部に最小外径部30pを有する形状に形成されている。さらに、本実施形態のシャフト351の上流側作動棒351aの外径は、最大外径部30nと同等の太さになっている。 More specifically, the outer shape of the annular member 353 of the present embodiment is formed in a rotating body shape in which the top sides of the two truncated cones are coupled to each other. Therefore, the annular member 353 of the present embodiment is formed in a shape having the maximum outer diameter portion 30n on the most upstream side of the refrigerant flow and the minimum outer diameter portion 30p in the substantially central portion in the central axis direction. Furthermore, the outer diameter of the upstream operating rod 351a of the shaft 351 of the present embodiment is the same thickness as the maximum outer diameter portion 30n.
 従って、ノズル通路13aの中心軸CL側(通路形成部材35および環状部材353側)の軸方向断面形状は、図6に示すように、環状部材353の最上流側の最大外径部30nから最小外径部30pへ至る範囲では冷媒流れ下流側に向かって、中心軸CLへ近づく形状となる。最小内径部30oから冷媒流れ下流側に向かって、中心軸CLから離れる形状となっている。 Therefore, the axial sectional shape of the nozzle passage 13a on the center axis CL side (passage forming member 35 and annular member 353 side) is minimum from the maximum outer diameter portion 30n on the most upstream side of the annular member 353 as shown in FIG. In the range reaching the outer diameter portion 30p, the shape approaches the center axis CL toward the downstream side of the refrigerant flow. The shape is away from the central axis CL from the smallest inner diameter portion 30o toward the downstream side of the refrigerant flow.
 一方、本実施形態のノズル32の減圧用空間30bを形成する部位は、上流側最小内径部30qと下流側最小内径部30rの2つの縮径部を有している。上流側最小内径部30qの内径は、下流側最小内径部30rの内径よりも小さい。 On the other hand, the part forming the decompression space 30b of the nozzle 32 of the present embodiment has two reduced diameter portions, that is, an upstream minimum inner diameter portion 30q and a downstream minimum inner diameter portion 30r. The inner diameter of the upstream minimum inner diameter portion 30q is smaller than the inner diameter of the downstream minimum inner diameter portion 30r.
 従って、ノズル通路13aの中心軸CLの反対側(ノズル32の減圧用空間30bを形成する部位側)の軸方向断面形状は、図14に示すように、流入空間30a側から上流側最小内径部30qへ至る範囲では、冷媒流れ下流側に向かって、中心軸CLへ近づく形状となる。上流側最小内径部30qから下流側最小内径部30rへ至る範囲では、冷媒流れ下流側に向かって、中心軸CLから離れた後に近づく形状となる。下流側最小内径部30rから冷媒流れ下流側に向かって、中心軸CLから離れる形状となっている。 Therefore, as shown in FIG. 14, the axial cross-sectional shape of the nozzle passage 13a on the opposite side of the central axis CL (on the side of the nozzle 32 where the pressure reducing space 30b is formed) is the upstream minimum inner diameter portion from the inflow space 30a side. In the range up to 30q, the shape approaches the central axis CL toward the downstream side of the refrigerant flow. In the range from the upstream minimum inner diameter portion 30q to the downstream minimum inner diameter portion 30r, the refrigerant flows toward the downstream side and becomes a shape that approaches after leaving the central axis CL. The shape is separated from the central axis CL from the downstream-side minimum inner diameter portion 30r toward the downstream side of the refrigerant flow.
 また、本実施形態では、第2先細部131bは、冷媒流れ下流側に向かって通路断面積が徐々に縮小する形状に形成されている。さらに、本実施形態の末広部132には、上流側最小内径部30q、および下流側最小内径部30rの2つのスロート部が形成されている。つまり、本実施形態では、最上流側スロート部よりも冷媒流れ下流側に配置された下流側スロート部が2つ形成されている。 In the present embodiment, the second tapered portion 131b is formed in a shape in which the passage sectional area gradually decreases toward the downstream side of the refrigerant flow. Furthermore, the throat portion 132 of the present embodiment is formed with two throat portions, an upstream minimum inner diameter portion 30q and a downstream minimum inner diameter portion 30r. That is, in the present embodiment, two downstream throat portions are formed which are arranged on the downstream side of the refrigerant flow with respect to the most upstream throat portion.
 つまり、本実施形態のノズル通路13aは、複数のスロート部(喉部)を有する多段絞り型のノズルとして機能するように通路断面積が変化する。その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成は、第1実施形態と同様である。 In other words, the passage cross-sectional area of the nozzle passage 13a of the present embodiment changes so as to function as a multistage throttle nozzle having a plurality of throat portions (throat portions). Other configurations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.
 また、本実施形態のエジェクタ13のノズル通路13aでは、冷媒を多段階に減圧させる。すなわち、本実施形態の第1先細部131aでは、亜音速状態の液相冷媒が減圧される。本実施形態の第2先細部131bは、冷媒流れ下流側に向かって通路断面積が徐々に縮小する先細形状となっている。このため、第2先細部131bでは、冷媒は亜音速のまま減圧されて加速される。 In the nozzle passage 13a of the ejector 13 of this embodiment, the refrigerant is depressurized in multiple stages. That is, in the first taper 131a of the present embodiment, the subsonic liquid phase refrigerant is decompressed. The second tapered portion 131b of the present embodiment has a tapered shape in which the passage sectional area gradually decreases toward the downstream side of the refrigerant flow. For this reason, in the 2nd taper 131b, a refrigerant | coolant is decompressed and accelerated with subsonic speed.
 第2先細部131bへ流入した冷媒には、第2先細部131bの最上流部を形成する環状部材353の最大外径部30nがエッジとなって剥離渦が生じ、中心軸CL側の冷媒に沸騰核が生成される。末広部132へ流入した冷媒には、末広部132の最上流部を形成するノズル32の上流側最小内径部30qがエッジとなって剥離渦が生じ、外周側の冷媒に沸騰核が生成される。 In the refrigerant flowing into the second tapered portion 131b, a separation vortex is generated with the maximum outer diameter portion 30n of the annular member 353 forming the most upstream portion of the second tapered portion 131b as an edge, and the refrigerant on the central axis CL side Boiling nuclei are generated. In the refrigerant flowing into the divergent part 132, an upstream minimum inner diameter part 30q of the nozzle 32 forming the uppermost stream part of the divergent part 132 becomes an edge to generate a separation vortex, and boiling nuclei are generated in the outer refrigerant. .
 上流側最小内径部30qの近傍では、沸騰促進された冷媒に閉塞(チョーキング)が生じる。このチョーキングによって冷媒が音速に到達する。さらに、下流側最小内径部30rがエッジとなって、沸騰核が生成されることで、より一層、冷媒の沸騰促進がなされて、冷媒噴射口13eから噴射される。 In the vicinity of the upstream minimum inner diameter portion 30q, the refrigerant whose boiling has been promoted is blocked (choked). This choking causes the refrigerant to reach the speed of sound. Further, the downstream minimum inner diameter portion 30r becomes an edge to generate boiling nuclei, whereby the boiling of the refrigerant is further promoted and the refrigerant is injected from the refrigerant injection port 13e.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の基本的な作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第6実施形態と同様の効果を得ることができる。つまり、複数のスロート部は、第6実施形態のように2つ限定されることなく、本実施形態のように、3つ以上設けられていてもよい。 Other basic operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, also in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment, the same effect as in the sixth embodiment can be obtained. That is, the plurality of throat portions are not limited to two as in the sixth embodiment, but may be provided as three or more as in the present embodiment.
 (第8実施形態)
 本実施形態では、第1実施形態のエジェクタ13に対して、図15に示すように、エジェクタ13の構成を簡素化させた例を説明する。なお、図15は、第1実施形態で説明した図2に対応する軸方向断面図である。
(Eighth embodiment)
In the present embodiment, an example in which the configuration of the ejector 13 is simplified as shown in FIG. 15 with respect to the ejector 13 of the first embodiment will be described. FIG. 15 is an axial sectional view corresponding to FIG. 2 described in the first embodiment.
 本実施形態のエジェクタ13では、第1実施形態に対して、通路形成部材35の形状を変更している。本実施形態の通路形成部材35は、冷媒流れ上流側から下流側へ向かって中心軸に垂直な断面積が拡大した後に縮小する形状に形成されている。より具体的には、本実施形態の通路形成部材35の外形は、円錐台状部材と円錐状部材の底面同士を結合させた回転体形状に形成されている。 In the ejector 13 of the present embodiment, the shape of the passage forming member 35 is changed with respect to the first embodiment. The passage forming member 35 of the present embodiment is formed in a shape that decreases after the cross-sectional area perpendicular to the central axis increases from the refrigerant flow upstream side to the downstream side. More specifically, the outer shape of the passage forming member 35 of the present embodiment is formed in a rotating body shape in which the truncated cone-shaped member and the bottom surfaces of the conical members are combined.
 このため、通路形成部材35の中心軸方向の略中央部には、最大外径部30nが形成されている。最大外径部30nは、第6実施形態で説明した最上流側スロート部としての機能を果たす。通路形成部材35の少なくとも一部は、ノズル32内に形成された減圧用空間30bの内部に配置されている。 Therefore, a maximum outer diameter portion 30n is formed at a substantially central portion in the central axis direction of the passage forming member 35. The maximum outer diameter portion 30n functions as the most upstream throat portion described in the sixth embodiment. At least a part of the passage forming member 35 is disposed in the decompression space 30 b formed in the nozzle 32.
 本実施形態のノズル32は、アッパーボデー311に一体的に形成されている。ノズル32には、ノズル通路13aの通路断面積を最も縮小させる最小通路面積部30mが形成されている。最小通路面積部30mは、第6実施形態で説明した下流側スロート部としての機能を果たす。 The nozzle 32 of this embodiment is formed integrally with the upper body 311. The nozzle 32 is formed with a minimum passage area portion 30m that reduces the passage sectional area of the nozzle passage 13a the most. The minimum passage area portion 30m fulfills the function as the downstream throat portion described in the sixth embodiment.
 通路形成部材35の最大外径部30nは、最小通路面積部30mよりも冷媒流れ上流側に位置付けられる。そして、通路形成部材35の外周面とノズル32の減圧用空間30bを形成する部位の内周面との間に形成されるノズル通路13aは、第1実施形態と同様に、ラバールノズルと同様に通路断面積が変化する。 The maximum outer diameter portion 30n of the passage forming member 35 is positioned upstream of the refrigerant flow with respect to the minimum passage area portion 30m. The nozzle passage 13a formed between the outer peripheral surface of the passage forming member 35 and the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle 32 is the same as the Laval nozzle, as in the first embodiment. The cross-sectional area changes.
 つまり、ノズル通路13aのうち通路断面積が最も縮小した最小通路面積部30mよりも冷媒流れ上流側に形成される部位が、冷媒流れ下流側へ向かって通路断面積が徐々に縮小する先細部となる。そして、最小通路面積部30mから冷媒流れ下流側に形成される部位が、冷媒流れ下流側へ向かって通路断面積が徐々に拡大する末広部となる。 In other words, a portion of the nozzle passage 13a formed on the upstream side of the refrigerant flow with respect to the smallest passage area portion 30m having the smallest passage cross-sectional area has a tapered portion in which the cross-sectional area of the passage gradually decreases toward the downstream side of the refrigerant flow. Become. And the site | part formed in the refrigerant | coolant flow downstream from the minimum channel | path area part 30m becomes a divergent part where a channel | path cross-sectional area expands gradually toward a refrigerant | coolant flow downstream.
 最大外径部30nよりも冷媒流れ上流側に配置される円錐台状部の頂部側には、シャフト351の上流側作動棒351aが一体的、かつ、同軸上に連結されている。上流側作動棒351aには、ステッピングモータ370に連結されている。ステッピングモータ370は、通路形成部材35を変位させる駆動機構である。ステッピングモータ370は、制御装置から出力される制御信号(制御パルス)によって、その作動が制御される。 The upstream side operating rod 351a of the shaft 351 is integrally and coaxially connected to the top side of the truncated cone-shaped part disposed on the upstream side of the refrigerant flow from the maximum outer diameter part 30n. A stepping motor 370 is connected to the upstream operating rod 351a. The stepping motor 370 is a drive mechanism that displaces the passage forming member 35. The operation of the stepping motor 370 is controlled by a control signal (control pulse) output from the control device.
 また、通路形成部材35の最大外径部30nの外径は、ノズル32の最小通路面積部30mの内径よりも大きく形成されている。このため、ステッピングモータ370が通路形成部材35を変位させてノズル通路13aを閉塞させる際には、通路形成部材35の最大外径部30nがノズル32に接触する。 Further, the outer diameter of the maximum outer diameter portion 30n of the passage forming member 35 is formed larger than the inner diameter of the minimum passage area portion 30m of the nozzle 32. For this reason, when the stepping motor 370 displaces the passage forming member 35 and closes the nozzle passage 13a, the maximum outer diameter portion 30n of the passage forming member 35 contacts the nozzle 32.
 また、ノズル通路13aの冷媒流れ下流側に配置される混合通路13dの通路断面積は、冷媒流れ下流側へ向かって縮小している。さらに、混合通路13dの最小通路断面積は、冷媒噴射口13eの通路断面積および吸引冷媒出口13fの通路断面積の合計値よりも小さく形成されている。 Further, the passage cross-sectional area of the mixing passage 13d arranged on the downstream side of the refrigerant flow in the nozzle passage 13a is reduced toward the downstream side of the refrigerant flow. Furthermore, the minimum passage sectional area of the mixing passage 13d is formed smaller than the total value of the passage sectional area of the refrigerant injection port 13e and the passage sectional area of the suction refrigerant outlet 13f.
 また、本実施形態の通路形成部材35は、少なくとも一部が減圧用空間30b内に配置されているものの、昇圧用空間30e内には配置されていない。従って、本実施形態のエジェクタ13では、図15に示すように、昇圧用空間30eの形状が、冷媒流れ下流側へ向かって通路断面積が徐々に縮小する形状に形成されている。そして、昇圧用空間30eが、ディフューザ通路13cとしての機能を果たす。 Further, at least a part of the passage forming member 35 of the present embodiment is disposed in the decompression space 30b, but is not disposed in the boosting space 30e. Therefore, in the ejector 13 of this embodiment, as shown in FIG. 15, the shape of the pressurizing space 30e is formed such that the passage sectional area gradually decreases toward the downstream side of the refrigerant flow. The pressure increasing space 30e functions as the diffuser passage 13c.
 その他のエジェクタ13およびエジェクタ式冷凍サイクル10の構成および作動は、第1実施形態と同様である。従って、本実施形態のエジェクタ13およびエジェクタ式冷凍サイクル10においても第1実施形態と同様の効果を得ることができる。 Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained in the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment.
 さらに、本実施形態では、通路形成部材35を昇圧用空間30e内に配置することなく減圧用空間30b内に配置している。従って、減圧用空間30bおよび昇圧用空間30e内の双方に配置する場合に対して、通路形成部材35の小型化を図ることできる。これにより、エジェクタ13全体としての小型化、および構成の簡素化を図ることができる。 Furthermore, in this embodiment, the passage forming member 35 is disposed in the decompression space 30b without being disposed in the pressurization space 30e. Therefore, the passage forming member 35 can be downsized as compared with the case where the passage forming member 35 is disposed in both the pressure reducing space 30b and the pressure increasing space 30e. Thereby, size reduction and simplification of the configuration of the ejector 13 as a whole can be achieved.
 また、本実施形態のエジェクタ13では、下流側作動棒351bが廃止されているものの、通路形成部材35に上流側作動棒351aが一体的、かつ、同軸上に連結されている。従って、第1実施形態と同様に、通路形成部材35の中心軸CLが減圧用空間30b、昇圧用空間30e等の中心軸に対して傾いてしまうことを抑制することができる。 Further, in the ejector 13 of the present embodiment, although the downstream operation rod 351b is eliminated, the upstream operation rod 351a is integrally and coaxially connected to the passage forming member 35. Therefore, as in the first embodiment, the central axis CL of the passage forming member 35 can be prevented from being inclined with respect to the central axes of the decompression space 30b, the boosting space 30e, and the like.
 さらに、本実施形態のエジェクタ13では、通路形成部材35の小型化を図ることできる。これにより、通路形成部材35が冷媒から受ける荷重(すなわち、動圧の作用)が小さくなるので、より一層、通路形成部材35の中心軸CLが傾いてしまうことを抑制することができる。 Furthermore, in the ejector 13 of the present embodiment, the passage forming member 35 can be downsized. Thereby, since the load (that is, the action of dynamic pressure) received by the passage forming member 35 from the refrigerant is reduced, the center axis CL of the passage forming member 35 can be further prevented from being inclined.
 また、本実施形態のエジェクタでは、混合通路13dの通路断面積が、冷媒流れ下流側へ向かって縮小している。従って、第1実施形態と同様に、ディフューザ通路13cの昇圧性能を安定化させて、エジェクタ効率が不安定となってしまうことを抑制することができるとともに、噴射冷媒と吸引冷媒とを混合させる際に生じる混合損失を抑制することができる。 Further, in the ejector of the present embodiment, the passage cross-sectional area of the mixing passage 13d is reduced toward the downstream side of the refrigerant flow. Therefore, as in the first embodiment, the pressure rising performance of the diffuser passage 13c can be stabilized to prevent the ejector efficiency from becoming unstable, and the injection refrigerant and the suction refrigerant are mixed. The mixing loss occurring in
 より詳細には、速度境界層にて反射して中心軸CL側へ進行する圧縮波は、通路形成部材35等が存在していなくても、混合通路13dの中心軸上(いわゆる、すべり面上)にて、反対側から進行してくる圧縮波と衝突して反射して外周側に転向する。従って、混合通路13d内に通路形成部材35が配置されていなくても、第1実施形態と同様の効果を得ることができる。 More specifically, the compression wave reflected on the velocity boundary layer and traveling toward the central axis CL side is on the central axis (so-called slip surface) of the mixing passage 13d even if the passage forming member 35 or the like is not present. ), It collides with the compression wave traveling from the opposite side, reflects, and turns to the outer peripheral side. Therefore, even if the passage forming member 35 is not disposed in the mixing passage 13d, the same effect as in the first embodiment can be obtained.
 また、本実施形態では、通路形成部材35に最上流側スロート部としての機能を果たす最大外径部30nが形成されている。従って、ノズル通路13aを流通する液相冷媒に中心軸CL側から沸騰核を供給することができる。さらに、ノズル32に下流側スロート部としての機能を果たす最小通路面積部30mが形成されている。従って、最小内径部30qが、ノズル通路13aを流通する液相冷媒に外周側からも沸騰核を供給することができる。 In the present embodiment, the passage forming member 35 is formed with a maximum outer diameter portion 30n that functions as the most upstream throat portion. Therefore, the boiling nuclei can be supplied from the central axis CL side to the liquid-phase refrigerant flowing through the nozzle passage 13a. Further, a minimum passage area portion 30m that functions as a downstream throat portion is formed in the nozzle 32. Therefore, the minimum inner diameter portion 30q can supply boiling nuclei from the outer peripheral side to the liquid-phase refrigerant flowing through the nozzle passage 13a.
 その結果、流入空間30a内の冷媒に気柱等が生成されていなくても、ノズル通路13aを流通する冷媒の沸騰を促進することができ、エジェクタ効率を向上させることができる。 As a result, even if no air column or the like is generated in the refrigerant in the inflow space 30a, boiling of the refrigerant flowing through the nozzle passage 13a can be promoted, and the ejector efficiency can be improved.
 (他の実施形態)
 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。
(Other embodiments)
The present disclosure is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present disclosure.
 (1)上述の各実施形態では、エジェクタ13の通路形成部材35の中心軸CLを水平方向に配置した例を説明したが、エジェクタ13の配置はこれに限定されない。例えば、図16の全体構成図に示すように、通路形成部材35の中心軸を鉛直方向に配置してもよい。この場合は、液相冷媒流出口31cが気液分離ボデーの最下方側に配置されていることが望ましい。 (1) In each of the above-described embodiments, the example in which the central axis CL of the passage forming member 35 of the ejector 13 is arranged in the horizontal direction has been described, but the arrangement of the ejector 13 is not limited thereto. For example, as shown in the overall configuration diagram of FIG. 16, the central axis of the passage forming member 35 may be arranged in the vertical direction. In this case, it is desirable that the liquid-phase refrigerant outlet 31c is disposed on the lowermost side of the gas-liquid separation body.
 (2)エジェクタ13は、上述の実施形態に開示されたものに限定されない。 (2) The ejector 13 is not limited to the one disclosed in the above embodiment.
 例えば、上述の実施形態では、上流側作動棒351aおよび下流側作動棒351bを共通する円柱状部材であるシャフト351によって形成した例を説明したが、上流側作動棒351aおよび下流側作動棒351bを別部材で形成してもよい。 For example, in the above-described embodiment, the example in which the upstream operation rod 351a and the downstream operation rod 351b are formed by the shaft 351 that is a common cylindrical member has been described. However, the upstream operation rod 351a and the downstream operation rod 351b You may form with another member.
 さらに、上述の実施形態では、下流側作動棒351bを上流側作動棒351aと同様に一本設けているが、下流側作動棒351bを複数本設けてもよい。上流側作動棒351aの外径および下流側作動棒351bの外径は、同一の値に設定されていてもよいし、異なる値に設定されていてもよい。 Furthermore, in the above-described embodiment, one downstream operation rod 351b is provided in the same manner as the upstream operation rod 351a, but a plurality of downstream operation rods 351b may be provided. The outer diameter of the upstream operating rod 351a and the outer diameter of the downstream operating rod 351b may be set to the same value or may be set to different values.
 また、エジェクタ13のアッパーボデー311の軸受穴およびロワーボデー312の軸受穴の摩耗を抑制するために、それぞれの軸受穴に筒状の金属で形成された軸受部材を配置してもよい。 Further, in order to suppress wear of the bearing hole of the upper body 311 of the ejector 13 and the bearing hole of the lower body 312, a bearing member formed of a cylindrical metal may be disposed in each bearing hole.
 また、上述の実施形態では、上流側作動棒351aに駆動機構37のプレート部材374を連結した例を説明したが、下流側作動棒351bに駆動機構を連結してもよい。 In the above-described embodiment, the example in which the plate member 374 of the drive mechanism 37 is connected to the upstream operation rod 351a has been described, but the drive mechanism may be connected to the downstream operation rod 351b.
 また、上述の実施形態では、駆動機構37が、蒸発器14出口側冷媒の温度および圧力に応じて通路形成部材35を変位させることによって、蒸発器14出口側冷媒の過熱度SHが基準過熱度KSHに近づくように、ノズル通路13aの通路断面積を調整した例を説明したが、駆動機構37による通路断面積の調整はこれに限定されない。 In the above-described embodiment, the drive mechanism 37 displaces the passage forming member 35 in accordance with the temperature and pressure of the evaporator 14 outlet-side refrigerant, so that the superheat degree SH of the evaporator 14 outlet-side refrigerant becomes the reference superheat degree. Although the example in which the passage sectional area of the nozzle passage 13a is adjusted so as to approach KSH has been described, the adjustment of the passage sectional area by the drive mechanism 37 is not limited to this.
 例えば、放熱器12出口側冷媒の温度および圧力に応じて通路形成部材35を変位させることによって、放熱器12出口側冷媒の過冷却度が予め定めた基準過冷却度に近づくように、ノズル通路13aの通路断面積を調整してもよい。 For example, the nozzle passage is arranged so that the degree of supercooling of the refrigerant on the outlet side of the radiator 12 approaches a predetermined reference subcooling degree by displacing the passage forming member 35 according to the temperature and pressure of the refrigerant on the outlet side of the radiator 12. The passage cross-sectional area of 13a may be adjusted.
 また、駆動機構37は上述の実施形態で説明したものに限定されない。例えば、第1~第7実施形態の駆動機構で採用した感温媒体として温度によって体積変化するサーモワックスを採用してもよい。さらに、駆動機構として、形状記憶合金性の弾性部材を有して構成されたものを採用してもよい。 Further, the drive mechanism 37 is not limited to the one described in the above embodiment. For example, a thermo wax that changes in volume depending on temperature may be employed as the temperature-sensitive medium employed in the drive mechanisms of the first to seventh embodiments. Further, as the drive mechanism, a mechanism having a shape memory alloy elastic member may be adopted.
 また、第8実施形態では、駆動機構として、電気的に作動するステッピングモータ370採用した例を説明したが、もちろん、第8実施形態で説明したエジェクタ13の駆動機構として、第1~第7実施形態で説明した機械的機構で構成される駆動機構37を採用してもよい。 In the eighth embodiment, the example in which the electrically operated stepping motor 370 is employed as the driving mechanism has been described. Of course, the first to seventh embodiments are used as the driving mechanism of the ejector 13 described in the eighth embodiment. You may employ | adopt the drive mechanism 37 comprised with the mechanical mechanism demonstrated by the form.
 (3)エジェクタ式冷凍サイクル10を構成する各構成機器は、上述の実施形態に開示されたものに限定されない。 (3) Each component device constituting the ejector refrigeration cycle 10 is not limited to that disclosed in the above-described embodiment.
 例えば、上述の実施形態では、圧縮機11として、エンジン駆動式の可変容量型圧縮機を採用した例を説明したが、圧縮機11として、電磁クラッチの断続により圧縮機の稼働率を変化させて冷媒吐出能力を調整する固定容量型圧縮機を採用してもよい。さらに、固定容量型圧縮機構と電動モータとを備え、電力を供給されることによって作動する電動圧縮機を採用してもよい。電動圧縮機では、電動モータの回転数を調整することによって、冷媒吐出能力を制御することができる。 For example, in the above-described embodiment, an example in which an engine-driven variable displacement compressor is employed as the compressor 11 has been described. However, as the compressor 11, the operating rate of the compressor is changed by the on / off of an electromagnetic clutch. You may employ | adopt the fixed capacity type compressor which adjusts a refrigerant | coolant discharge capability. Furthermore, you may employ | adopt an electric compressor provided with a fixed displacement type compression mechanism and an electric motor, and act | operating by supplying electric power. In the electric compressor, the refrigerant discharge capacity can be controlled by adjusting the rotation speed of the electric motor.
 また、上述の実施形態では、放熱器12として、サブクール型の熱交換器を採用した例を説明したが、凝縮部12aのみからなる通常の放熱器を採用してもよい。さらに、通常の放熱器とともに、この放熱器にて放熱した冷媒の気液を分離して余剰液相冷媒を蓄える受液器(レシーバ)を一体化させたレシーバ一体型の凝縮器を採用してもよい。 In the above-described embodiment, an example in which a subcool type heat exchanger is employed as the radiator 12 has been described, but a normal radiator including only the condensing unit 12a may be employed. In addition to a normal radiator, a receiver-integrated condenser that integrates a receiver (receiver) that separates the gas-liquid of the refrigerant radiated by this radiator and stores excess liquid phase refrigerant is adopted. Also good.
 また、上述の実施形態では、冷媒としてR1234yfを採用した例を説明したが、冷媒はこれに限定されない。例えば、R134a、R600a、R410A、R404A、R32、R407C、等を採用することができる。または、これらの冷媒のうち複数種を混合させた混合冷媒等を採用してもよい。さらに、冷媒として二酸化炭素を採用して、高圧側冷媒圧力が冷媒の臨界圧力以上となる超臨界冷凍サイクルを構成してもよい。 In the above-described embodiment, the example in which R1234yf is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. can be employed. Or you may employ | adopt the mixed refrigerant | coolant etc. which mixed multiple types among these refrigerant | coolants. Furthermore, a supercritical refrigeration cycle in which carbon dioxide is employed as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.
 (4)上述の実施形態では、本開示に係るエジェクタ式冷凍サイクル10を、車両用空調装置に適用した例を説明したが、エジェクタ式冷凍サイクル10の適用はこれに限定されない。例えば、据置型空調装置、冷温保存庫、自動販売機用冷却加熱装置等に適用してもよい。 (4) In the above-described embodiment, the example in which the ejector refrigeration cycle 10 according to the present disclosure is applied to a vehicle air conditioner has been described, but the application of the ejector refrigeration cycle 10 is not limited thereto. For example, 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.
 また、上述の実施形態では、本開示に係るエジェクタ13を備えるエジェクタ式冷凍サイクル10の放熱器12を冷媒と外気とを熱交換させる室外側熱交換器とし、蒸発器14を送風空気を冷却する利用側熱交換器としている。これに対して、蒸発器14を外気等の熱源から吸熱する室外側熱交換器として用い、放熱器12を空気あるいは水等の被加熱流体を加熱する利用側熱交換器として用いてもよい。 In the above-described embodiment, the radiator 12 of the ejector refrigeration cycle 10 including the ejector 13 according to the present disclosure is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 14 cools the blown air. Use side heat exchanger. On the other hand, the evaporator 14 may be used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 may be used as a use side heat exchanger that heats a heated fluid such as air or water.
 (5)また、上記各実施形態に開示された要素は、実施可能な範囲で適宜組み合わせてもよい。例えば、第4実施形態の通路形成部材35を、第2、第3、第5~第7実施形態に適用してもよい。また、第5~第8実施形態の通路形成部材35に、第2実施形態で説明した凹み部(貫通穴35a)を形成してもよい。 (5) The elements disclosed in each of the above embodiments may be appropriately combined within a practicable range. For example, the passage forming member 35 of the fourth embodiment may be applied to the second, third, and fifth to seventh embodiments. Further, the recess (through hole 35a) described in the second embodiment may be formed in the passage forming member 35 of the fifth to eighth embodiments.
 本開示は、実施例に準拠して記述されたが、本開示は当該実施例や構造に限定されるものではないと理解される。本開示は、様々な変形例や均等範囲内の変形をも包含する。加えて、様々な組み合わせや形態、さらには、それらに一要素のみ、それ以上、あるいはそれ以下、を含む他の組み合わせや形態をも、本開示の範疇や思想範囲に入るものである。 Although the present disclosure has been described based on the embodiments, it is understood that the present disclosure is not limited to the embodiments and structures. The present disclosure includes various modifications and modifications within the equivalent range. In addition, various combinations and forms, as well as other combinations and forms including only one element, more or less, are within the scope and spirit of the present disclosure.

Claims (16)

  1.  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、
     液相冷媒を流入させる流入空間(30a)、前記流入空間から流出した冷媒を減圧させる減圧用空間(30b)、前記減圧用空間の冷媒流れ下流側に連通して冷媒吸引口(31b)から吸引した冷媒を流通させる吸引用通路(13b)、および前記減圧用空間から噴射された噴射冷媒と前記吸引用通路を介して吸引された吸引冷媒とを流入させる昇圧用空間(30e)を有するボデー(30)と、
     少なくとも一部が前記減圧用空間の内部に配置されて、前記ボデーとの間に冷媒通路を形成する通路形成部材(35)と、
     前記通路形成部材を変位させる駆動機構(37)と、を備え、
     前記ボデーのうち前記減圧用空間を形成する部位の内周面と前記通路形成部材の外周面との間に形成される冷媒通路は、冷媒を減圧させて噴射するノズルとして機能するノズル通路(13a)であり、
     前記通路形成部材には、前記流入空間側へ延びて前記ボデーに摺動可能に支持された上流側作動棒(351a)が連結されており、
     前記流入空間の中心軸、前記上流側作動棒の中心軸、および前記通路形成部材の中心軸(CL)は、同軸上に配置されているエジェクタ。
    An ejector applied to a vapor compression refrigeration cycle apparatus (10),
    An inflow space (30a) through which liquid phase refrigerant flows, a decompression space (30b) that decompresses the refrigerant that has flowed out of the inflow space, and a refrigerant suction downstream (31b) that communicates with the downstream side of the refrigerant flow in the decompression space. A body having a suction passage (13b) through which the refrigerant is circulated, and a pressurization space (30e) through which the refrigerant injected from the decompression space and the suction refrigerant sucked through the suction passage flow in. 30),
    A passage forming member (35) that is at least partially disposed within the space for decompression and forms a refrigerant passage with the body;
    A drive mechanism (37) for displacing the passage forming member,
    A refrigerant passage formed between an inner peripheral surface of a portion of the body that forms the decompression space and an outer peripheral surface of the passage forming member is a nozzle passage (13a) that functions as a nozzle that decompresses and injects the refrigerant. ) And
    The passage forming member is connected to an upstream operating rod (351a) that extends toward the inflow space and is slidably supported by the body.
    The central axis of the inflow space, the central axis of the upstream operating rod, and the central axis (CL) of the passage forming member are arranged on the same axis.
  2.  前記通路形成部材は、少なくとも一部が前記昇圧用空間の内部に配置されており、
     前記ボデーのうち前記昇圧用空間を形成する部位の内周面と前記通路形成部材の外周面との間に形成される冷媒通路は、前記噴射冷媒および前記吸引冷媒を混合させて昇圧させる昇圧部として機能するディフューザ通路(13c)である請求項1に記載のエジェクタ。
    The passage forming member is at least partially disposed inside the pressurizing space,
    A refrigerant passage formed between an inner peripheral surface of a portion of the body that forms the pressurizing space and an outer peripheral surface of the passage forming member is a pressure increasing unit that increases the pressure by mixing the injected refrigerant and the suction refrigerant. The ejector according to claim 1, which is a diffuser passage (13 c) functioning as
  3.  前記通路形成部材には、前記ディフューザ通路の下流側へ向かって延びて前記ボデーに摺動可能に支持された下流側作動棒(351b)が連結されている請求項2に記載のエジェクタ。 The ejector according to claim 2, wherein a downstream operation rod (351b) extending toward the downstream side of the diffuser passage and slidably supported by the body is connected to the passage forming member.
  4.  前記上流側作動棒の中心軸と前記下流側作動棒の中心軸は、同軸上に配置されている請求項3に記載のエジェクタ。 The ejector according to claim 3, wherein a central axis of the upstream operating rod and a central axis of the downstream operating rod are arranged coaxially.
  5.  前記駆動機構は、前記上流側作動棒および前記下流側作動棒の少なくとも一方に連結されている請求項3または4に記載のエジェクタ。 The ejector according to claim 3 or 4, wherein the drive mechanism is connected to at least one of the upstream operating rod and the downstream operating rod.
  6.  前記流入空間の中心軸方向から見たときに、前記吸引用通路の吸引冷媒出口(13f)は前記ノズル通路の冷媒噴射口(13e)の外周側に環状に開口している請求項2ないし5のいずれか1つに記載のエジェクタ。 The suction refrigerant outlet (13f) of the suction passage is annularly opened on the outer peripheral side of the refrigerant injection port (13e) of the nozzle passage when viewed from the central axis direction of the inflow space. The ejector as described in any one of these.
  7.  前記ボデーのうち前記昇圧用空間を形成する部位の内周面と前記通路形成部材の外周面との間に形成される冷媒通路であって、前記ディフューザ通路の冷媒流れ上流側には、前記噴射冷媒と前記吸引冷媒とを混合させる混合通路(13d)が形成されており、
     前記混合通路の最小通路断面積は、前記冷媒噴射口の通路断面積および前記吸引冷媒出口の通路断面積の合計値よりも小さく形成されている請求項6に記載のエジェクタ。
    A refrigerant passage formed between an inner peripheral surface of a portion of the body that forms the pressurizing space and an outer peripheral surface of the passage forming member, wherein the injection is provided upstream of the refrigerant flow in the diffuser passage. A mixing passage (13d) for mixing the refrigerant and the suction refrigerant is formed,
    The ejector according to claim 6, wherein a minimum passage sectional area of the mixing passage is formed smaller than a total value of a passage sectional area of the refrigerant injection port and a passage sectional area of the suction refrigerant outlet.
  8.  前記ボデーのうち前記混合通路を形成する壁面が前記中心軸を含む断面に描く線は、冷媒流れ下流側に向かって前記通路形成部材側に近づくように傾斜している請求項7に記載のエジェクタ。 The ejector according to claim 7, wherein a line drawn on a cross section including the central axis of a wall surface forming the mixing passage in the body is inclined so as to approach the passage forming member side toward a refrigerant flow downstream side. .
  9.  前記通路形成部材のうち前記混合通路を形成する壁面が前記中心軸を含む断面に描く線は、冷媒流れ下流側に向かって前記ボデー側に近づくように傾斜している請求項7または8に記載のエジェクタ。 The line which the wall surface which forms the said mixing channel among the said channel | path formation members draws in the cross section containing the said central axis inclines so that it may approach the said body side toward a refrigerant | coolant flow downstream. Ejector.
  10.  前記通路形成部材は、冷媒流れ上流側から下流側へ向かって中心軸に垂直な断面積が拡大した後に縮小する形状に形成されており、
     前記ボデーのうち前記減圧用空間を形成する部位には、前記ノズル通路に通路断面積を最も縮小させる最小通路面積部(30m)が形成されており、
     前記通路形成部材の最大外径部(30n)は、前記最小通路面積部よりも冷媒流れ上流側に配置されている請求項1に記載のエジェクタ。
    The passage forming member is formed in a shape that decreases after the cross-sectional area perpendicular to the central axis increases from the refrigerant flow upstream side to the downstream side,
    A portion of the body that forms the pressure-reducing space is formed with a minimum passage area (30 m) that reduces the passage cross-sectional area to the nozzle passage.
    The ejector according to claim 1, wherein the maximum outer diameter portion (30n) of the passage forming member is disposed upstream of the refrigerant flow with respect to the minimum passage area portion.
  11.  前記ノズル通路の下流側には、前記噴射冷媒と前記吸引冷媒とを混合させる混合通路(13d)が形成されており、
     前記混合通路の最小通路断面積は、前記ノズル通路の冷媒噴射口の通路断面積および前記吸引用通路の吸引冷媒出口の通路断面積の合計値よりも小さく形成されている請求項10に記載のエジェクタ。
    A mixing passage (13d) for mixing the jet refrigerant and the suction refrigerant is formed on the downstream side of the nozzle passage,
    The minimum passage cross-sectional area of the mixing passage is smaller than a total value of a passage cross-sectional area of a refrigerant injection port of the nozzle passage and a passage cross-sectional area of a suction refrigerant outlet of the suction passage. Ejector.
  12.  前記通路形成部材には、前記ノズル通路の通路断面積を拡大させる側に凹んだ凹み部(35a、35b)が形成されている請求項1ないし11のいずれか1つに記載のエジェクタ。 The ejector according to any one of claims 1 to 11, wherein the passage forming member is formed with a recessed portion (35a, 35b) that is recessed toward the side where the passage sectional area of the nozzle passage is enlarged.
  13.  前記凹み部は、前記通路形成部材の円錐状側面を貫通する貫通穴(35a)である請求項12に記載のエジェクタ。 The ejector according to claim 12, wherein the recessed portion is a through hole (35a) penetrating the conical side surface of the passage forming member.
  14.  前記凹み部は、前記通路形成部材の中心軸周りの全周に亘って形成された溝部(35b)である請求項12に記載のエジェクタ。 The ejector according to claim 12, wherein the recess is a groove (35b) formed over the entire circumference around the central axis of the passage forming member.
  15.  前記通路形成部材のうち前記ノズル通路を形成する壁面が前記中心軸を含む断面に描く線は、前記ノズル通路側に尖った形状を含んでいる請求項1ないし14のいずれか1つに記載のエジェクタ。 The line which the wall surface which forms the said nozzle channel among the said channel | path formation members draws in the cross section containing the said central axis contains the shape pointed to the said nozzle channel side as described in any one of Claim 1 thru | or 14. Ejector.
  16.  前記ボデーには、冷媒流入口(31a)から流入した冷媒を前記流入空間へ導く冷媒流入通路(31e)が形成されており、
     前記流入空間の中心軸方向から見たときに、前記冷媒流入通路は前記流入空間へ流入する冷媒を前記中心軸に向かって流入させる形状に形成されている請求項1ないし15のいずれか1つに記載のエジェクタ。
    The body is formed with a refrigerant inflow passage (31e) that guides the refrigerant flowing in from the refrigerant inlet (31a) to the inflow space,
    The refrigerant inflow passage is formed in a shape for allowing the refrigerant flowing into the inflow space to flow toward the central axis when viewed from the direction of the central axis of the inflow space. Ejector as described in.
PCT/JP2017/002204 2016-02-02 2017-01-24 Ejector WO2017135093A1 (en)

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US10767905B2 (en) 2016-02-02 2020-09-08 Denso Corporation Ejector
US11053956B2 (en) 2016-02-02 2021-07-06 Denso Corporation Ejector

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WO2002001970A2 (en) * 2000-06-30 2002-01-10 Fmc Corporation Steam injection heater and method
JP2013177879A (en) * 2012-02-02 2013-09-09 Denso Corp Ejector
JP2014126225A (en) * 2012-12-25 2014-07-07 Calsonic Kansei Corp Vehicle air conditioning system and gas-liquid mixer

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JP2014126225A (en) * 2012-12-25 2014-07-07 Calsonic Kansei Corp Vehicle air conditioning system and gas-liquid mixer

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US10767905B2 (en) 2016-02-02 2020-09-08 Denso Corporation Ejector
US11053956B2 (en) 2016-02-02 2021-07-06 Denso Corporation Ejector

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