WO2021261112A1 - Éjecteur - Google Patents

Éjecteur Download PDF

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Publication number
WO2021261112A1
WO2021261112A1 PCT/JP2021/018569 JP2021018569W WO2021261112A1 WO 2021261112 A1 WO2021261112 A1 WO 2021261112A1 JP 2021018569 W JP2021018569 W JP 2021018569W WO 2021261112 A1 WO2021261112 A1 WO 2021261112A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
drive
ejector
suction
pressure
Prior art date
Application number
PCT/JP2021/018569
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English (en)
Japanese (ja)
Inventor
春幸 西嶋
洋 押谷
正博 伊藤
紘志 前田
Original Assignee
株式会社デンソー
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Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112021003333.6T priority Critical patent/DE112021003333T5/de
Publication of WO2021261112A1 publication Critical patent/WO2021261112A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F04F5/465—Arrangements of nozzles with supersonic flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F04F5/16—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
    • F04F5/18—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids for compressing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0271—Compressor control by controlling pressure the discharge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present disclosure relates to an ejector that injects a fluid in a gas-liquid two-phase state from a nozzle portion on the drive side.
  • an ejector type refrigeration cycle which is a refrigeration cycle device equipped with an ejector, is known.
  • the pressure of the refrigerant sucked into the compressor can be raised higher than the refrigerant evaporation pressure in the evaporator by the pressurizing action of the ejector.
  • the power consumption of the compressor is reduced and the coefficient of performance (COP) of the cycle is improved. Therefore, in order to improve the COP of the ejector type refrigeration cycle, it is effective to improve the boosting capacity of the ejector.
  • Patent Document 1 as an ejector applied to the ejector type refrigeration cycle, the passage shape of the mixing portion for mixing the injection refrigerant and the suction refrigerant is described, and the passage cross-sectional area is described as the direction of the refrigerant flow.
  • An ejector having a truncated cone shape to be enlarged is disclosed.
  • the ejector of Patent Document 1 attempts to suppress the energy loss of the refrigerant in the mixing portion and increase the boosting amount of the refrigerant in the diffuser portion.
  • Patent Document 2 in an industrial ejector (hereinafter, referred to as a steam ejector) applied to a vacuum exhaust device or the like, the gas phase fluid (specifically, air) is boosted by the pressure recovery action of a shock wave. It is stated that it will be done. Further, Patent Document 2 describes that the steam ejector can enhance the pressure recovery action of the shock wave by reducing the Mach number of air in the most upstream portion of the shock wave.
  • an object of the present disclosure to provide an ejector capable of exhibiting a high boosting ability by using a shock wave regardless of the load fluctuation of the applied refrigeration cycle device.
  • the ejector of the first aspect of the present disclosure is an ejector applied to a refrigeration cycle apparatus, and includes a drive side nozzle portion and a body portion.
  • the drive-side nozzle section decompresses the drive-side refrigerant and accelerates it until it reaches supersonic speed, and injects the drive-side injection refrigerant in a gas-liquid two-phase state.
  • the body section has a refrigerant suction port, a suction side nozzle section, a mixing section, and a diffuser section.
  • the refrigerant suction port sucks the suction side refrigerant.
  • the suction side nozzle portion decompresses and injects the suction side refrigerant sucked from the refrigerant suction port.
  • the mixing unit mixes the suction-side injection refrigerant injected from the suction-side nozzle unit and the drive-side injection refrigerant injected from the drive-side nozzle unit.
  • the diffuser section converts the kinetic energy of the mixed refrigerant mixed in the mixing section into pressure energy.
  • the refrigerant pressure of the drive-side injection refrigerant decompressed by the drive-side nozzle portion is higher than the refrigerant pressure of the suction-side injection refrigerant decompressed by the suction-side nozzle portion. Therefore, regardless of the load fluctuation of the refrigeration cycle device, the drive-side refrigerant can be insufficiently expanded in the drive-side nozzle portion, and a shock wave can be reliably generated in the mixing portion. As a result, the mixed refrigerant can be boosted by the pressure recovery action of the shock wave in the mixing section.
  • the flow velocity of the mixed refrigerant flowing out of the mixing section and flowing into the diffuser section is subsonic. Therefore, even if a pseudo-shock wave that may cause energy loss is generated in the mixing portion by the first shock wave generated by the drive-side injection refrigerant, the pseudo-shock wave can be quickly extinguished.
  • the drive side injection refrigerant and the suction side injection refrigerant so that the refrigerant pressure on the central axis side and the refrigerant pressure on the wall surface side of the mixed refrigerant flowing out of the mixing section and flowing into the diffuser section match. And are mixed. Therefore, even if the generation range of the pseudo-shock wave changes due to the load fluctuation of the refrigeration cycle device, the pseudo-shock wave can be surely extinguished in the mixing unit.
  • the first embodiment of the present disclosure will be described with reference to FIGS. 1 to 10.
  • the ejector 13 of the present embodiment is applied to the ejector type refrigeration cycle 10.
  • the ejector type refrigeration cycle 10 is a steam compression type refrigeration cycle apparatus including an ejector.
  • the ejector type refrigeration cycle 10 is applied to an air conditioner for a vehicle, and cools the blown air blown into the vehicle interior, which is a space to be air-conditioned.
  • the drive side inlet 31a side of the drive side nozzle portion 31 of the ejector 13 is connected to the refrigerant outlet of the radiator 12.
  • the ejector 13 is a refrigerant decompression unit that depressurizes the drive-side refrigerant flowing out of the radiator 12.
  • the ejector 13 is also a refrigerant transport unit that sucks and transports the refrigerant flowing out of the evaporator 16 described later. Further, the ejector 13 is also a refrigerant boosting unit that boosts the pressure of the refrigerant flowing into the inside.
  • the detailed configuration of the ejector 13 will be described with reference to FIG. 2 and the like.
  • the ejector 13 has a drive-side nozzle portion 31 and a body portion 32.
  • the drive side nozzle portion 31 has a tip detail 31b, a throat portion 31c, and a divergent portion 31d.
  • the detail 31b is a portion where the passage cross-sectional area of the refrigerant flowing in from the drive side inlet 31a is reduced as the refrigerant flows toward the downstream side.
  • the throat portion 31c is a portion that most reduces the passage cross-sectional area of the refrigerant.
  • the suehiro portion 31d is a portion that expands the passage cross-sectional area of the refrigerant as it goes from the throat portion 31c to the drive side injection port 31e. That is, in the ejector 13, a so-called Laval nozzle is adopted as the drive side nozzle portion 31.
  • the drive-side nozzle portion 31 is formed by subjecting a metal (in this embodiment, stainless steel) cylindrical member to plastic working.
  • the thickness of the portion forming the tip detail 31b and the divergent portion 31d of the drive-side nozzle portion 31 is substantially constant. Therefore, the appearance shapes of the tip detail 31b and the divergent portion 31d are changed in the same manner as the shape of the refrigerant passage formed inside.
  • the drive-side nozzle portion 31 may be formed by cutting a block-shaped metal member.
  • the shape of the refrigerant passage of the drive-side nozzle portion 31 is determined so that the flow velocity of the drive-side injection refrigerant injected from the drive-side injection port 31e is equal to or higher than the sound velocity of the gas-liquid two-phase refrigerant. .. Further, the speed of the gas phase refrigerant in the refrigerant passage of the drive side nozzle portion 31 is determined to be equal to or lower than the gas phase sound velocity which is the sound velocity of the gas phase refrigerant.
  • the relationship between the throat area Anzth and the drive-side injection port area Anzout is determined so as to satisfy the following mathematical formula F1.
  • F1 1.3 ⁇ Anzout / Anzth ⁇ 1.5 ...
  • the throat area Anzth is the passage cross-sectional area of the throat 31c.
  • the drive-side injection port area Anzout is the passage cross-sectional area of the drive-side injection port 31e.
  • the body portion 32 is formed of a tubular member made of metal (made of aluminum in this embodiment).
  • the body portion 32 forms the outer shell of the ejector 13.
  • the drive-side nozzle portion 31 is fixed to the inside of the body portion 32 on one end side in the longitudinal direction by press fitting.
  • the central axis of the drive-side nozzle portion 31 and the central axis of the body portion 32 are arranged coaxially.
  • the body portion 32 may be formed of a resin tubular member.
  • the body portion 32 has a refrigerant suction port 321, a suction side nozzle portion 322, a mixing portion 323, and a diffuser portion 324.
  • the refrigerant suction port 321 is formed on the cylindrical side surface of the body portion 32.
  • the refrigerant suction port 321 is a through hole for sucking the suction-side refrigerant flowing out of the evaporator 16 into the ejector 13 by the suction action of the drive-side injection refrigerant jetted from the drive-side nozzle portion 31.
  • the refrigerant suction port 321 communicates with the suction space 321a formed inside the body portion 32.
  • the suction space 321a is formed by coaxially arranging the tip details 31b and the divergent portion 31d of the drive-side nozzle portion 31 in the columnar space formed inside the body portion 32. Therefore, the suction space 321a is formed in an annular cross section on the outer peripheral side of the tip detail 31b and the divergent portion 31d of the drive side nozzle portion 31.
  • the suction side nozzle unit 322 decompresses the suction side refrigerant sucked into the suction space 321a through the refrigerant suction port 321 and injects it into the mixing unit 323.
  • the suction-side nozzle portion 322 is a downstream portion of the suction space 321a in the body portion 32, and is formed on the outer peripheral side of the tip end portion of the divergent portion 31d of the drive-side nozzle portion 31. Therefore, the refrigerant passage of the suction side nozzle portion 322 is formed in an annular cross section between the outer peripheral surface of the divergent portion 31d and the inner peripheral surface of the body portion 32.
  • the outer peripheral portion of the divergent portion 31d of the drive-side nozzle portion 31 is formed in a shape that increases the outer diameter toward the downstream side of the refrigerant flow, similar to the shape of the internal refrigerant passage. Therefore, the annular refrigerant passage of the suction side nozzle portion 322 has a shape in which the cross-sectional area of the passage decreases toward the downstream side of the refrigerant flow. That is, in the ejector 13, a so-called tapered nozzle is substantially adopted as the suction side nozzle portion 322.
  • the suction side injection port 322a of the suction side nozzle portion 322 is opened in an annular shape around the drive side injection port 31e.
  • the drive side injection port 31e and the suction side injection port 322a are open on the same plane.
  • the outer diameter of the suction side injection port 322a coincides with the mixing portion inlet diameter Dmix, which is the inner diameter of the inlet portion of the mixing portion 323.
  • the drive side injection refrigerant immediately after being injected from the drive side injection port 31e and the suction side injection refrigerant immediately after being injected from the suction side injection port 322a are substantially parallel to each other. It is open to flow. In other words, the drive-side injection port 31e and the suction-side injection port 322a are opened so that the injection direction of the drive-side injection refrigerant immediately after injection and the injection direction of the suction-side injection refrigerant immediately after injection are in the same direction. is doing.
  • the decompression performance of the drive-side nozzle unit 31 and the decompression performance of the suction-side nozzle unit 322 are the suction immediately after the pressure of the drive-side injection refrigerant immediately after being injected from the drive-side injection port 31e is injected from the suction-side injection port 322a. It is determined to be higher than the pressure of the side injection refrigerant.
  • the drive-side injection port area Anzout of the drive-side nozzle unit 31 and the suction-side injection port area Asnout of the suction-side nozzle unit 322 are determined to satisfy the following formula F2. 2 ⁇ Asnout / Anzout ⁇ 4... (F2)
  • the suction side injection port area Asnout is the passage cross-sectional area of the suction side injection port 322a.
  • the drive side injection port area Anzout is smaller than the suction side injection port area Asnout.
  • the drive-side refrigerant is a high-pressure refrigerant flowing out of the radiator 12, and the suction-side refrigerant is a low-pressure refrigerant flowing out of the evaporator 16. Therefore, if the suction side injection port area Asnout and the drive side injection port area Anzout are determined so as to satisfy the equation F2, the pressure of the drive side injection refrigerant can be made higher than the pressure of the suction side injection refrigerant. can.
  • the mixing unit 323 forms a mixing space 323a that mixes the drive-side injection refrigerant and the suction-side injection refrigerant.
  • the mixing unit 323 is arranged on the downstream side of the refrigerant flow of the drive side injection port 31e and the suction side injection port 322a in the body unit 32.
  • the mixed space 323a is formed in a substantially truncated cone shape that expands the cross-sectional area of the passage toward the downstream side of the refrigerant flow.
  • the drive side injection refrigerant and the suction side injection refrigerant are mixed so that the flow velocity of the gas-liquid two-phase mixed refrigerant flowing out of the mixing unit 323 and flowing into the diffuser unit 324 becomes subsonic. Let me.
  • the cross-sectional area of the passage does not decrease as the refrigerant flows toward the downstream side.
  • the passage cross-sectional area does not shrink. Therefore, in the mixing unit 323, the gas-liquid two-phase mixed refrigerant that has become subsonic at a uniform pressure is not accelerated to supersonic speed again on the downstream side of the refrigerant flow from the mixing unit 323.
  • the passage shape of the mixing unit 323 is such that the shock wave generated by the driving-side injection refrigerant injected from the driving-side nozzle unit 31 at supersonic speed is extinguished in the mixing unit 323.
  • the mixing unit distance L is determined so as to satisfy the following mathematical formula F3.
  • the relaxation distance Lv is defined below by the mathematical formula F4.
  • Lv U 0 ⁇ ( ⁇ L ⁇ D L 2 ) / (18 ⁇ ⁇ G )... (F4)
  • the mixing section distance L is an axial length from the inlet to the exit of the mixing section 323.
  • the mixing section distance L needs to be larger than the relaxation distance Lv. That is, it is necessary to satisfy the above formula F3.
  • the initial Mach number M 0, which is the Mach number of the mixed refrigerant in the most upstream part of the first shock wave is a relatively high value
  • an expansion wave may be generated on the downstream side of the first shock wave. ..
  • the refrigerant flow velocity on the central axis side of the mixing unit 323 becomes subsonic, but the refrigerant flow velocity on the turbulent boundary layer side becomes supersonic again. ..
  • FIG. 3 is an explanatory diagram schematically showing the generation mode of the pseudo-shock wave generated in the gas phase fluid flowing in the fluid passage of the circular tube 100 and the fluid pressure on the axial cross-sectional view of the circular tube 100.
  • the non-hatched region in the circular tube 100 of FIG. 3 is a region in which a supersonic fluid is mainly distributed.
  • the point hatch region is a region where subsonic fluids are mainly distributed.
  • the thick line in the circular tube 100 of FIG. 3 indicates a shock wave, and the double broken line indicates an expansion wave.
  • three shock waves and three expansion waves are schematically represented, but the number of shock waves and expansion waves is not limited to this.
  • the pseudo-shock wave is not a phenomenon that always occurs, and does not occur when the initial Mach number M 0 is a relatively low value.
  • the steam ejector is an ejector in which a vapor phase fluid flows inside and the outlet of the diffuser portion is opened to the atmosphere.
  • the steam ejector is used for a vacuum exhaust device, a smoke exhaust suction device, an aircraft air intake, and the like.
  • the present inventors confirmed that a pseudo-shock wave is generated even in the ejector in which the gas-liquid two-phase fluid flows inside. Furthermore, the present inventors have also confirmed that the mode of generation of the pseudo-shock wave generated by the steam ejector is different from the mode of generation of the pseudo-shock wave generated by the ejector through which the gas-liquid two-phase fluid flows.
  • the pseudo-shock wave generated by the steam ejector through which the gas-phase fluid flows is described as the pseudo-shock wave in the gas-phase flow.
  • a pseudo-shock wave generated by an ejector through which a gas-liquid two-phase fluid flows is described as a pseudo-shock wave in a two-phase flow.
  • the reason why the pseudo-shock wave generation mode in the gas-phase flow and the pseudo-shock wave generation mode in the two-phase flow are different is that droplets are present in the gas-liquid two-phase fluid. Specifically, the vapor phase refrigerant in the shock wave rapidly decreases the flow velocity, but the droplet has an inertial force, so that the velocity decrease becomes slower than that of the vapor phase refrigerant. Further, the gas phase refrigerant in the expansion wave rapidly increases the flow velocity, but the droplets accelerate more slowly than the gas phase refrigerant due to the drag force from the gas phase refrigerant.
  • pseudo-shock waves in two-phase flow are less likely to occur as the dryness of the drive-side injection refrigerant decreases.
  • the reason is that the droplet has the effect of attenuating the pressure wave by scattering or absorption. Therefore, the generation mode of the pseudo-shock wave in the two-phase flow changes depending on the size and number density of the droplets.
  • the present inventors have conducted a study for promptly extinguishing the pseudo-shock wave in the two-phase flow when the pseudo-shock wave in the two-phase flow is generated in the mixing unit 323 in the ejector 13.
  • the axial length required to extinguish the pseudo-shock wave in the two-phase flow increases as the initial Mach number M 0 increases. Further, it was found that the axial length required to extinguish the pseudo-shock wave in the two-phase flow increases as the dryness X of the refrigerant flowing through the mixing portion 323 increases.
  • the axial length required to extinguish the pseudo shock wave is represented by the ratio to the relaxation distance Lv.
  • the pseudo shock wave can be extinguished in the mixing section. I found it. 1 ⁇ L / Lv ⁇ 3.5 (however, 1 ⁇ M 0 ⁇ 2.5) ... (F5) Further, when the relationship shown in the formula F5 is converted into the flow path shape, if the relationship between the mixing section distance L and the mixing section inlet diameter Dmix is determined so as to satisfy the following formula F6, the pseudo shock wave is extinguished in the mixing section. I found that I could do it. 1 ⁇ L / Dmix ⁇ 10 (however, 1 ⁇ M 0 ⁇ 2.5)... (F6)
  • the mixing portion inlet diameter Dmix is the diameter of the refrigerant passage at the inlet of the mixing portion 323.
  • the mixing portion inlet diameter Dmix coincides with the outer diameter of the suction side injection port 322a of the suction side nozzle portion 322. Further, the range of the initial Mach number M 0 in the formulas F5 and F6 is a range that can be practically used in an ejector applied to a general ejector type refrigeration cycle.
  • the mixing section distance L of the mixing section 323 of the ejector 13 is determined to satisfy the above equations F3, F5, and F6. Therefore, in the mixing unit 323, not only the pressure of the mixed refrigerant is increased, but also the flow velocity of the mixed refrigerant is greatly reduced. As a result, the refrigerant on the wall surface side of the mixing unit 323 is likely to be separated from the wall surface. The peeling of the refrigerant on the wall surface side of the mixing unit 323 from the wall surface hinders the flow of the mixed refrigerant and causes energy loss.
  • the passage shape of the mixing portion 323 is formed so that the cross-sectional area of the passage increases as the mixed refrigerant moves toward the downstream side in the flow direction.
  • the area change rate dA / dz is determined so that the passage shape of the mixing unit 323 satisfies the following mathematical formulas F7 within the range satisfying the above mathematical formulas F5 and F6. 0 ⁇ dA / dz ⁇ 0.8 (mm) ... (F7)
  • the area change rate dA / dz is the amount of change dA (mm 2 ) in the cross-sectional area of the refrigerant passage per unit length dz (mm) in the axial direction in the mixing unit 323.
  • the area change rate dA / dz is increased toward the downstream side of the refrigerant flow.
  • the diffuser unit 324 forms a step-up passage 324a that converts the kinetic energy of the mixed refrigerant mixed in the mixing unit 323 into pressure energy.
  • the inlet of the boost passage 324a is formed so as to be continuous with the outlet of the mixing portion 323.
  • the booster passage 324a is formed in a substantially truncated cone shape in which the cross-sectional area of the passage is expanded toward the downstream side of the refrigerant flow. Due to this shape, the diffuser unit 324 decelerates the mixed refrigerant and boosts the pressure of the mixed refrigerant.
  • the passage shape of the boost passage 324a is determined so that the flow velocity of the mixed refrigerant flowing out of the mixing section 323 and flowing into the diffuser section 324 is subsonic.
  • the relationship between the mixing portion outlet area Amixout and the diffuser portion outlet area Aout is determined so as to satisfy the following mathematical formula F8.
  • the mixing section outlet area Amixout is the passage cross-sectional area of the exit of the mixing section 323.
  • the mixed-section outlet area Amixout coincides with the passage cross-sectional area of the inlet of the diffuser section 324.
  • the diffuser section outlet area Aout is the passage cross-sectional area of the outlet of the diffuser section 324.
  • the refrigerant flowing out from the diffuser section has a certain flow velocity in order to reduce the power consumption of the compressor.
  • the flow velocity of the refrigerant flowing out from the diffuser portion may be a subsonic speed of about 0.1 to 0.2 times the speed of sound.
  • the passage cross-sectional area of the diffuser section 324 is expanded so as to satisfy the above formula F8, the flow velocity of the mixed refrigerant flowing out of the mixing section 323 and flowing into the diffuser section 324 does not exceed the speed of sound. ..
  • the suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 14.
  • the refrigerant inlet side of the evaporator 16 is connected to the liquid phase refrigerant outlet of the accumulator 14 via a fixed throttle 15 as a depressurizing means.
  • a fixed throttle 15 an orifice, a capillary tube, or the like can be adopted.
  • the internal air temperature sensor is an internal air temperature detection unit that detects the temperature inside the vehicle.
  • the outside air temperature sensor is an outside air temperature detection unit that detects the outside air temperature.
  • the solar radiation sensor is a solar radiation amount detection unit that detects the amount of solar radiation in the vehicle interior.
  • the evaporator temperature sensor is an evaporator temperature detection unit that detects the temperature of the blown air (evaporator temperature) of the evaporator 16.
  • the discharge pressure sensor is a discharge refrigerant pressure detection unit that detects the pressure of the refrigerant discharged from the compressor 11.
  • the control device 20 is integrally configured with a control unit that controls the operation of various controlled devices connected to the output side.
  • a configuration that is, hardware and software that controls the operation of each control target device constitutes a control unit of each control target device.
  • a configuration that controls the operation of the compressor 11 constitutes a discharge capacity control unit.
  • FIG. 1 and the like a power line or a signal line connecting the control device 20 and various controlled devices is shown, but for the sake of clarification of the illustration, the sensor group and the control device 20 and the sensor group are shown. The illustration of the signal line to be connected is omitted.
  • the control device 20 operates the compressor 11, the cooling fan 12a, the indoor blower 16a, and the like. As a result, the compressor 11 sucks in the refrigerant, compresses it, and discharges it.
  • the drive-side refrigerant that has flowed into the drive-side nozzle portion 31 reaches a critical state at the throat portion 31c, and the drive flow rate of the ejector 13 is determined.
  • the drive-side refrigerant is accelerated at the divergent portion 31d until it reaches a supersonic state. Then, it becomes a drive-side injection refrigerant in a gas-liquid two-phase state and is injected from the drive-side injection port 31e into the mixing space 323a of the mixing unit 323.
  • the drive-side injection refrigerant is a supersonic mist flow that exceeds the two-phase sound velocity.
  • the refrigerant flowing out of the evaporator 16 is sucked from the refrigerant suction port 321 into the suction space 321a as the suction side refrigerant by the suction action of the drive side injection refrigerant injected from the drive side injection port 31e to the mixing unit 323. More specifically, since the drive-side injection refrigerant is in a gas-liquid two-phase state, the injected droplets accelerate due to the action of inertial force, thereby reducing the pressure in the vicinity of the suction-side injection port 322a. As a result, the suction side refrigerant is sucked into the suction space 321a.
  • the suction-side refrigerant sucked into the suction space 321a is depressurized by the suction-side nozzle portion 322, becomes a suction-side injection refrigerant, and is injected from the suction-side injection port 322a into the mixing space 323a of the mixing section 323.
  • the refrigerant pressure of the drive-side injection refrigerant injected to the mixing unit 323 is higher than the refrigerant pressure of the suction-side injection refrigerant injected to the mixing unit 323. Therefore, in the drive-side nozzle unit 31, the drive-side refrigerant is insufficiently expanded to generate an expansion wave in the mixing unit 323.
  • the mixed refrigerant flowing out of the mixing section 323 flows into the diffuser section 324.
  • the kinetic energy of the mixed refrigerant is converted into pressure energy by expanding the cross-sectional area of the passage. As a result, the pressure of the mixed refrigerant further increases.
  • the flow velocity of the mixed refrigerant flowing out from the mixing section 323, flowing out, and flowing into the diffuser section 324 is reduced to subsonic speed.
  • the shock wave generated by the drive-side injection refrigerant can be reliably eliminated in the mixing unit 323. Therefore, it is possible to suppress the energy loss caused by the shock wave after exerting the pressure recovery action.
  • the driving side injection refrigerant so as to match the refrigerant pressure on the central axis side and the refrigerant pressure on the wall surface side of the mixed refrigerant flowing out from the mixing section 323 and flowing out into the diffuser section 324. And the suction side injection refrigerant are mixed. Therefore, even if the generation range of the pseudo-shock wave in the two-phase flow changes due to the load fluctuation of the refrigeration cycle device, the pseudo-shock wave can be surely extinguished in the mixing unit 323.
  • the operating condition OP1 is the operating condition in which the refrigerant pressure at the outlet of the diffuser unit 324 is minimized.
  • the operating condition OP2 is an operating condition in which the refrigerant pressure at the outlet of the diffuser unit 324 is higher than that of the operating condition OP1.
  • the operating condition OP3 is an operating condition in which the refrigerant pressure at the outlet of the diffuser unit 324 is higher than that of the operating condition OP2.
  • the operating condition OP4 is an operating condition in which the refrigerant pressure at the outlet of the diffuser unit 324 is higher than that of the operating condition OP3.
  • the refrigerant pressure at the outlet of the diffuser unit 324 increases in the order of operating condition OP1, operating condition OP2, operating condition OP3, and operating condition OP4. Further, in the graph of FIG. 5, the value obtained by subtracting the refrigerant pressure at the inlet of the mixing unit 323 from the refrigerant pressure at the outlet of the diffuser unit 324 is the boosted amount of the refrigerant as the entire ejector 13. In FIG. 5, for the sake of clarification of the illustration, the boost amount ⁇ P is shown only for the operating condition OP3.
  • the boosting amount of the ejector 13 as a whole is increased as compared with other operating conditions. Therefore, in the operating condition OP3, as shown in FIG. 8, the shock wave is rapidly extinguished in the mixing unit 323, and the relaxation distance Lv of the pseudo shock wave is reduced as compared with the other operating conditions, thereby further reducing the energy loss. It is understood that it is decreasing.
  • the pressure of the mixed refrigerant starts to rise sharply immediately after flowing into the mixing unit 323. Therefore, under the operating condition OP4, as shown in FIG. 9, it is understood that the drive-side refrigerant cannot be insufficiently expanded in the drive-side nozzle portion 31, and a shock wave is generated inside the drive-side nozzle portion 31. Will be done.
  • the pressure recovery action of the shock wave cannot be sufficiently utilized to boost the pressure of the mixed refrigerant in the mixing unit 323, and the boosting amount of the ejector 13 as a whole is larger than that of other operating conditions. It has decreased.
  • the refrigerant pressure at the inlet of the mixing unit 323 rises as in the operating condition OP4
  • the pressure of the suction side refrigerant also rises, and the refrigerant evaporation temperature in the evaporator 16 may rise.
  • Asnout / Anzout is set so that the pressure of the drive-side injection refrigerant is higher than the pressure of the suction-side injection refrigerant, as described in the mathematical formula F2.
  • the pressure of the drive side injection refrigerant can be made higher than the pressure of the suction side injection refrigerant without requiring complicated operation control or the like according to the load fluctuation. Then, the drive-side nozzle portion 31 can surely inadequately expand the drive-side refrigerant, and can surely generate an expansion wave in the drive-side injection refrigerant.
  • the flow velocity of the drive-side injection refrigerant injected from the drive-side injection port 31e becomes equal to or higher than the two-phase sound velocity, which is the sound velocity of the gas-liquid two-phase refrigerant.
  • Anzout / Anzth is set so that the speed of the gas phase refrigerant in the refrigerant passage of the drive side nozzle portion 31 is equal to or lower than the gas phase sound velocity which is the sound velocity of the gas phase refrigerant.
  • the drive-side injection refrigerant in the gas-liquid two-phase state can be surely set to the two-phase sound velocity or higher without requiring complicated operation control or the like according to the load fluctuation. Further, the speed of the gas phase refrigerant in the refrigerant passage of the drive side nozzle portion 31 can be set to be equal to or lower than the gas phase sound velocity.
  • the distance L1 from the inlet of the mixing section 323 to the generation of the first shock wave is 0.1 times or less of the mixing section inlet diameter Dmix. It has been confirmed that it will be. Therefore, as described in the operating condition OP3 of FIG. 5, the boosting amount of the ejector 13 as a whole can be increased.
  • the wall friction in the refrigerant passage of the drive-side nozzle portion 31 can be alleviated, so that the initial Mach number M 0 can be increased. Therefore, the boost amount of the mixed refrigerant can be further increased by the shock wave having high energy.
  • the mixing portion distance L is set to be longer than the relaxation distance Lv. According to this, the first shock wave generated in the mixing section 323 by the driving side injection refrigerant can be surely extinguished in the mixing section 323. Therefore, the flow velocity of the mixed refrigerant in the gas-liquid two-phase state flowing out of the mixing section 323 and flowing into the diffuser section 324 can be easily brought close to the subsonic speed.
  • the range of L / Lv or L / Dmix is set as shown in the formulas F5 and F6. According to this, even if a pseudo-shock wave in the two-phase flow is generated due to the load fluctuation of the ejector type refrigeration cycle 10, the pseudo-shock wave in the two-phase flow can be surely extinguished in the mixing unit 323.
  • the passage shape of the mixing portion 323 has a shape in which the passage cross-sectional area increases as the mixed refrigerant moves toward the downstream side in the flow direction. There is. According to this, it is possible to suppress the separation of the refrigerant on the wall surface side of the mixing unit 323 from the wall surface and suppress the energy loss.
  • the flow velocity of the mixed refrigerant suddenly decreases in the mixing unit 323. Therefore, being able to suppress the separation of the refrigerant on the wall surface side of the mixing unit 323 from the wall surface is effective in suppressing energy loss.
  • the present inventors make a shock wave in the ejector 13 under the following conditions. It has been confirmed that it exerts a high boosting ability by using.
  • the ejector 13 exhibits a boosting capacity four times or more that of the conventional technique, at least within the range in which the inlet pressure Pin and the outlet pressure Pout of the ejector 13 satisfy both of the following formulas F9 and F10. is doing. 0.4 ⁇ Pin ⁇ 1.7 (MPa) ... (F9) 0.3 ⁇ Pout ⁇ 0.65 (MPa) ... (F10)
  • the inlet pressure Pin is the pressure of the drive-side refrigerant flowing into the drive-side nozzle portion 31 of the ejector 13.
  • the outlet pressure Pout is the pressure of the refrigerant flowing out from the diffuser unit 324.
  • the ejector 13 exhibits a boosting capacity four times or more that of the conventional technique, at least in the range where the inlet pressure Pin and the drive side injection pressure Pnzout of the ejector 13 are in the following mathematical formula F11. 0.2 ⁇ Pnzout / Pin ⁇ 0.65 ... (F11)
  • the drive-side injection pressure Pnzout is the pressure of the drive-side injection refrigerant immediately after being injected from the drive-side injection port 31e.
  • the HFO-based refrigerant includes R1234zd and the like in addition to R1234yf.
  • the HFC-based refrigerant includes R134a, R410A, R32, R404A, R407C and the like.
  • An ejector-type refrigeration cycle that employs these refrigerants constitutes a subcritical refrigeration cycle.
  • the ejector 113 of the present embodiment is applied to the ejector type refrigeration cycle 10 having the same configuration as that of the first embodiment.
  • the ejector type refrigerating cycle 10 of the present embodiment is applied to a stationary heating / hot water supply device, and heats the blown air or hot water supplied to the room.
  • the ejector type refrigeration cycle 10 of the present embodiment uses carbon dioxide as a refrigerant, and constitutes a supercritical refrigeration cycle in which the refrigerant pressure on the high pressure side exceeds the critical pressure of the refrigerant.
  • the radiator 12 of the ejector type refrigeration cycle 10 of the present embodiment heat-exchanges the high-pressure refrigerant with the blown air blown to the air-conditioned space or the hot water supplied to the kitchen, bath, or the like to exchange heat with the high-pressure refrigerant.
  • It is a heat exchanger for heat dissipation that dissipates heat in a supercritical state.
  • the evaporator 16 of the present embodiment is an endothermic heat exchanger that exchanges heat between the low pressure refrigerant and the outside air blown by the outside air fan to evaporate the low pressure refrigerant and exert a heat absorbing action.
  • the ejector 113 of the present embodiment has a drive side nozzle portion 131, a body portion 132, a needle valve 133, and a drive mechanism 134.
  • the dimensional specifications of each portion are set so that the drive-side nozzle unit 31 described in the first embodiment has the same function.
  • a needle valve 133 is arranged in the refrigerant passage of the drive-side nozzle portion 131.
  • the needle valve 133 changes the passage cross-sectional area of the throat portion of the drive side nozzle portion 131 and the drive side injection port by being displaced in the axial direction of the drive side nozzle portion 131.
  • the needle valve 133 is made of a metal (stainless steel in this embodiment) needle-shaped member.
  • the central axis of the needle valve 133 is arranged coaxially with the central axis of the drive-side nozzle portion 131.
  • the opposite end of the drive-side injection port of the needle valve 133 is connected to the drive mechanism 134.
  • the drive mechanism 134 is a drive unit that displaces the needle valve 133 in the central axis direction.
  • a stepping motor is adopted as the drive mechanism 134.
  • the operation of the drive mechanism 134 is controlled by a control signal (that is, a control pulse) output from the control device 20.
  • the body portion 132 is formed by combining a plurality of metal (in this embodiment, aluminum) block members.
  • the dimensional specifications of each part of the body part 132 are set so as to exhibit the same function as the body part 32 described in the first embodiment.
  • the body portion 132 has the same refrigerant suction port 321 as in the first embodiment, a suction side nozzle portion 322, a mixing portion 323, and a diffuser portion 324.
  • the configuration of the other ejectors 113 is the same as that of the ejector 13 described in the first embodiment.
  • the control device 20 controls the operation of the drive mechanism 134 so that the superheat degree of the refrigerant on the outlet side of the evaporator 16 approaches a predetermined reference superheat degree KSH.
  • Other operations are the same as in the first embodiment. Therefore, the same effect as that of the first embodiment can be obtained in the ejector type refrigeration cycle 10 of the present embodiment.
  • the present inventors exhibit a high boosting ability by using a shock wave under the following conditions. I have confirmed that.
  • the ejector 13 exhibits a high boosting ability at least within a range in which the inlet pressure Pin and the outlet pressure Pout of the ejector 13 satisfy both of the following formulas F12 and F13. 6 ⁇ Pin ⁇ 14 (MPa) ... (F12) 1.5 ⁇ Pout ⁇ 7 (MPa) ... (F13) Further, it has been confirmed that the ejector 13 exhibits a high boosting ability at least within a range in which the inlet pressure Pin and the drive side injection pressure Pnzout of the ejector 13 satisfy the following formula F14. 0.3 ⁇ Pnzout / Pin ⁇ 0.7 ... (F14) In the ejector type refrigeration cycle that employs carbon dioxide or a mixed refrigerant containing carbon dioxide, a supercritical refrigeration cycle is configured.
  • the ejector type refrigeration cycle 10a is applied to an air conditioner for vehicles.
  • the ejector type refrigeration cycle 10a includes a branch portion 17, a first evaporator 161 and a second evaporator 162. Further, in the ejector type refrigeration cycle 10a, the accumulator 14 is abolished.
  • the branch portion 17 is a three-way joint that branches the flow of the refrigerant flowing out of the radiator 12.
  • the drive-side inlet 31a side of the drive-side nozzle portion 31 of the ejector 13 is connected to one of the outlets of the branch portion 17.
  • the inlet side of the fixed throttle 15 is connected to the other outlet of the branch portion 17.
  • the refrigerant inlet side of the first evaporator 161 is connected to the outlet of the diffuser portion 324 of the ejector 13.
  • the first evaporator 161 is an endothermic heat exchanger that cools the blown air by exchanging heat between the low-pressure refrigerant flowing out of the diffuser portion 324 of the ejector 13 and the blown air blown from the indoor blower 16a.
  • the suction port side of the compressor 11 is connected to the refrigerant outlet of the first evaporator 161.
  • the refrigerant inlet side of the second evaporator 162 is connected to the outlet of the fixed throttle 15.
  • the second evaporator 162 is an endothermic heat exchanger that cools the blown air by exchanging heat between the low-pressure refrigerant decompressed by the fixed throttle 15 and the blown air after passing through the first evaporator 161.
  • the refrigerant suction port 321 side of the ejector 13 is connected to the refrigerant outlet of the second evaporator 162.
  • the first evaporator 161 and the second evaporator 162 of this embodiment are integrally configured.
  • the first evaporator 161 and the second evaporator 162 are composed of a so-called tank-and-tube type heat exchanger.
  • a tank-and-tube heat exchanger is a heat exchanger having a plurality of tubes for circulating a refrigerant and a pair of collecting and distributing tanks connected to both ends of the plurality of tubes to collect or distribute the refrigerant. be.
  • the first evaporator 161 and the second evaporator 162 are integrally configured by forming the collective distribution tank with the same member.
  • the first evaporator 161 and the second evaporator 162 are arranged in series with respect to the blown air flow so that the first evaporator 161 is arranged on the upstream side of the blown air flow with respect to the second evaporator 162. It is placed in. Therefore, the blown air flows as shown by the dashed arrow in FIG. 12.
  • the operation of the ejector type refrigeration cycle 10a of the present embodiment in the above configuration will be described.
  • the control device 20 operates the compressor 11
  • the high-temperature high-pressure refrigerant discharged from the compressor 11 is condensed by the radiator 12 as in the first embodiment.
  • the refrigerant flowing out of the radiator 12 flows into the branch portion 17.
  • the flow of the refrigerant flowing out of the radiator 12 is branched.
  • One of the refrigerants branched at the branch portion 17 flows into the drive side nozzle portion 31 of the ejector 13 as the drive side refrigerant.
  • the drive-side refrigerant is issentropically depressurized as in the first embodiment. Then, the drive-side injection refrigerant in the gas-liquid two-phase state exceeding the two-phase sound velocity is injected from the drive-side injection port 31e of the drive-side nozzle unit 31 into the mixing space 323a of the mixing unit 323.
  • the suction side injection refrigerant is injected from the suction side injection port 322a of the suction side nozzle unit 322 into the mixing space 323a of the mixing unit 323, as in the first embodiment.
  • the pressure of the mixed refrigerant of the driving side injection refrigerant and the suction side injection refrigerant increases due to the pressure recovery action of the shock wave generated by the drive side injection refrigerant.
  • the mixed refrigerant flowing out of the mixing section 323 flows into the diffuser section 324.
  • the pressure of the mixed refrigerant further increases, as in the first embodiment.
  • the refrigerant flowing out of the diffuser unit 324 flows into the first evaporator 161.
  • the refrigerant flowing out from the diffuser unit 324 absorbs heat from the blown air blown by the indoor blower 16a and evaporates. As a result, the blown air is cooled.
  • the vapor phase refrigerant flowing out of the first evaporator 161 is sucked into the compressor 11 and compressed again.
  • the other refrigerant branched at the branch portion 17 flows into the fixed throttle 15 and is enthalpy depressurized.
  • the low-pressure refrigerant decompressed by the fixed throttle 15 flows into the second evaporator 162.
  • the refrigerant flowing into the second evaporator 162 absorbs heat from the blown air after passing through the first evaporator 161 and evaporates. As a result, the blown air is further cooled and blown into the vehicle interior.
  • the refrigerant flowing out of the second evaporator 162 is sucked from the refrigerant suction port 321 of the ejector 13.
  • the ejector type refrigerating cycle 10a of the present embodiment operates as described above and can cool the blown air blown into the vehicle interior.
  • the refrigerant evaporation temperature of the first evaporator 161 can be raised higher than the refrigerant evaporation temperature of the second evaporator 162 by the pressurizing action of the ejector 13. Therefore, in the ejector type refrigeration cycle 10a, the temperature difference between the refrigerant evaporation temperature of the first evaporator 161 and the blown air and the temperature difference between the refrigerant evaporation temperature of the second evaporator 162 and the blown air are ensured efficiently. Blower air can be cooled.
  • the intermediate pressure expansion valve decompresses the refrigerant flowing out of the radiator 12 in the ejector type refrigeration cycle 10 and causes the refrigerant to flow out to the drive side inlet 31a side of the drive side nozzle portion 31 of the ejector 13.
  • a variable expansion mechanism that changes the throttle opening so that the pressure of the high pressure refrigerant flowing into the intermediate pressure expansion valve becomes the target high pressure determined according to the temperature of the high pressure refrigerant can be adopted. can.
  • the intermediate pressure expansion valve decompresses the refrigerant flowing out of the radiator 12 in the ejector type refrigeration cycle 10a and causes it to flow out to the inflow port side of the branch portion 17.
  • a variable throttle mechanism that changes the throttle opening so that the superheat degree of the refrigerant flowing out of the first evaporator 161 approaches a predetermined reference superheat degree can be adopted.
  • first evaporator 161 and the second evaporator 162 of the ejector type refrigeration cycle 10a are integrally configured
  • first evaporator 161 and the second evaporator 162 have been described. May be formed separately.
  • the first evaporator 161 and the second evaporator 162 may cool the different refrigerant target fluids in different temperature zones.
  • the first evaporator 161 whose refrigerant evaporation temperature is higher than that of the second evaporator 162 is used for air conditioning to be blown to the air conditioning target space. It may be used to blow air. Then, the second evaporator 162, in which the refrigerant evaporation temperature is lower than that of the first evaporator 161 may be used to cool the blown air for the freezer that is circulated and blown into the freezer.
  • the configurations of the ejector type refrigeration cycles 10 and 10a are not limited to those disclosed in the above-described embodiment.
  • the compressor 11 is not limited to the electric compressor.
  • an engine drive type compressor driven by a rotational driving force transmitted from the engine may be adopted.
  • a variable capacity type compressor or the like whose refrigerant discharge capacity can be adjusted by changing the discharge capacity can be adopted.
  • radiator 12 of the ejector type refrigeration cycle constituting the subcritical refrigeration cycle.
  • the subcool type condenser has a condensing part, a receiver part, and a supercooling part.
  • the condensing unit exchanges heat between the refrigerant and the outside air to condense the refrigerant.
  • the receiver unit separates the gas and liquid of the refrigerant flowing out from the condensing unit, and stores a part of the separated liquid phase refrigerant as a surplus refrigerant in the cycle.
  • the supercooling unit supercools the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant flowing out from the receiver unit and the outside air.
  • each of the above embodiments may be appropriately combined to the extent practicable.
  • the ejector 113 described in the second embodiment may be applied to the ejector type refrigeration cycle 10a described in the third embodiment.

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  • Physics & Mathematics (AREA)
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  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
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Abstract

L'invention concerne un éjecteur qui comporte : une partie de buse de côté d'entraînement (31, 131); et une partie de corps (32, 132). La partie de corps (32, 132) a un orifice d'aspiration de réfrigérant (321), une partie de buse de côté d'aspiration (322), une partie de mélange (323) et une partie de diffuseur (324). Un orifice d'éjection de côté d'entraînement (31e) de la partie de buse de côté d'entraînement (31, 131) et un orifice d'éjection de côté d'aspiration (322a) de la partie de buse de côté d'aspiration (322) sont ouverts de telle sorte que la direction d'éjection d'un réfrigérant éjecté du côté d'entraînement et la direction d'éjection d'un réfrigérant éjecté du côté d'aspiration doivent être équivalentes. La pression du réfrigérant éjecté du côté d'entraînement est supérieure à la pression du réfrigérant éjecté du côté d'aspiration. Le réfrigérant mélangé s'écoulant de la partie de mélange (323) à la partie de diffuseur (324) a une vitesse subsonique, et la pression de réfrigérant de celui-ci sur le côté d'axe central coïncide avec la pression de réfrigérant sur le côté de surface de paroi.
PCT/JP2021/018569 2020-06-22 2021-05-17 Éjecteur WO2021261112A1 (fr)

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Citations (4)

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Publication number Priority date Publication date Assignee Title
JP2012017946A (ja) * 2010-07-09 2012-01-26 Denso Corp 冷凍サイクル装置およびその制御方法
JP2014115069A (ja) * 2012-11-16 2014-06-26 Denso Corp エジェクタ
JP2015521703A (ja) * 2012-06-12 2015-07-30 エンドレス ソーラー コーポレイション リミテッド エジェクタおよびその操作方法
WO2017135092A1 (fr) * 2016-02-02 2017-08-10 株式会社デンソー Éjecteur

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Publication number Priority date Publication date Assignee Title
JPS59151000A (ja) 1983-02-16 1984-08-29 Mitsubishi Heavy Ind Ltd エゼクタ
CN103620323B (zh) 2011-06-27 2016-09-07 开利公司 喷射器混合器
JP7088000B2 (ja) 2018-12-27 2022-06-21 トヨタ自動車株式会社 交通情報処理装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012017946A (ja) * 2010-07-09 2012-01-26 Denso Corp 冷凍サイクル装置およびその制御方法
JP2015521703A (ja) * 2012-06-12 2015-07-30 エンドレス ソーラー コーポレイション リミテッド エジェクタおよびその操作方法
JP2014115069A (ja) * 2012-11-16 2014-06-26 Denso Corp エジェクタ
WO2017135092A1 (fr) * 2016-02-02 2017-08-10 株式会社デンソー Éjecteur

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