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WO2018047563A1 - Éjecteur - Google Patents

Éjecteur Download PDF

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Publication number
WO2018047563A1
WO2018047563A1 PCT/JP2017/028665 JP2017028665W WO2018047563A1 WO 2018047563 A1 WO2018047563 A1 WO 2018047563A1 JP 2017028665 W JP2017028665 W JP 2017028665W WO 2018047563 A1 WO2018047563 A1 WO 2018047563A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
forming member
passage
passage forming
space
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2017/028665
Other languages
English (en)
Japanese (ja)
Inventor
大介 中島
陽一郎 河本
照之 堀田
山田　悦久
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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
Application filed by Denso Corp filed Critical Denso Corp
Publication of WO2018047563A1 publication Critical patent/WO2018047563A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/48—Control

Definitions

  • 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 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.
  • 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 ejector of Patent Document 1 includes a drive mechanism that outputs a drive force for displacing the passage forming member.
  • a drive mechanism that outputs a drive force for displacing the passage forming member.
  • a gas-liquid separation space for separating the gas-liquid of the refrigerant flowing out from the diffuser passage is arranged on the downstream side of the diffuser passage. Further, a support member for supporting the passage forming member is disposed in the gas-liquid separation space. For this reason, when the refrigerant whose pressure has been increased in the diffuser passage flows through a gap such as a support member in the gas-liquid separation space, pressure loss may easily occur in the refrigerant.
  • the ejector of Patent Document 1 has a coil spring that is an elastic member that applies a load to the passage forming member as one of the members disposed in the gas-liquid separation space.
  • the coil spring has a function of suppressing vibration of the passage forming member and a function of adjusting a driving force that acts on the passage forming member from the drive mechanism. For this reason, the coil spring also fulfills the function of suppressing the performance variation of the ejector.
  • the present disclosure has a first object of suppressing a decrease in the pressure increase performance of an ejector configured to change the passage cross-sectional area of the refrigerant passage.
  • a second object of the present disclosure is to suppress an increase in performance variation of an ejector configured to be able to change the passage cross-sectional area of the refrigerant passage.
  • the ejector according to the first aspect of the present disclosure is applied to the vapor compression refrigeration cycle apparatus (10).
  • the ejector includes a body (30), a passage forming member (35), a drive mechanism (37), a guide member (39), an elastic member (40), and a load adjusting unit (41).
  • the body (30) communicates with an inflow space (30a) for allowing refrigerant to flow in, a decompression space (30b) for decompressing refrigerant flowing out of the inflow space, and a refrigerant suction port (31b) in communication with the downstream side of the refrigerant flow in the decompression space.
  • the passage forming member (35) is at least partially disposed in the decompression space and in the pressurization space.
  • the drive mechanism (37) outputs a drive force that displaces the passage forming member.
  • the guide member (39) is fixed to the body and slidably supports the passage forming member.
  • the elastic member (40) applies a load to the passage forming member.
  • the load adjusting unit (41) adjusts the load.
  • 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 (13a) that functions as a nozzle that decompresses and injects the refrigerant.
  • the refrigerant passage formed between the inner peripheral surface of the part of the body that forms the pressurization space and the outer peripheral surface of the passage forming member is a diffuser passage that functions as a booster for mixing and increasing the pressure of the injected refrigerant and the suction refrigerant. (13c).
  • the guide member is formed in a shape extending in the displacement direction of the passage forming member, and one end side is fixed to a portion of the body on the upstream side of the refrigerant flow with respect to the passage forming member.
  • the passage forming member is formed with an insertion hole (35b) into which the guide member is slidably fitted and an accommodation space (35a) for accommodating a part of the guide member.
  • the elastic member is disposed in the accommodation space.
  • the load adjusting unit is attached to the guide member.
  • the drive mechanism since the drive mechanism is provided, it is possible to change the passage sectional areas of the nozzle passage and the diffuser passage by displacing the passage forming member in accordance with the load fluctuation of the refrigeration cycle apparatus.
  • the guide member is disposed so as to extend from a portion of the body upstream of the coolant flow to the passage forming member with respect to the passage forming member, and the elastic member is disposed in the accommodating space.
  • a load adjusting portion is attached to the guide member.
  • the first aspect it is possible to suppress a decrease in the boosting performance of the ejector configured to be able to change the passage cross-sectional area of the refrigerant passage such as the nozzle passage and the diffuser passage.
  • the ejector according to the second aspect of the present disclosure is applied to a vapor compression refrigeration cycle apparatus.
  • the ejector includes a body, a passage forming member, a drive mechanism, a shaft, a guide member, and a position adjusting unit.
  • the body includes an inflow space into which the refrigerant flows, a decompression space that decompresses the refrigerant that has flowed out of the inflow space, a suction passage that communicates with the downstream side of the refrigerant flow in the decompression space and distributes the refrigerant sucked from the refrigerant suction port, and There is a pressure increasing space through which the injected refrigerant injected from the depressurizing space and the suction refrigerant sucked through the suction passage flow. At least a part of the passage forming member is disposed in the decompression space and in the pressurization space.
  • the drive mechanism outputs a driving force that displaces the passage forming member.
  • the shaft transmits a driving force to the passage forming member.
  • the guide member is fixed to the body and slidably supports the passage forming member.
  • the position adjusting unit adjusts the position of the tip of the shaft on the passage forming member side with respect to 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.
  • the refrigerant passage formed between the inner peripheral surface of the part of the body that forms the pressurization space and the outer peripheral surface of the passage forming member is a diffuser passage that functions as a booster for mixing and increasing the pressure of the injected refrigerant and the suction refrigerant. It is.
  • the guide member is formed in a cylindrical shape extending in the displacement direction of the passage forming member, and one end is fixed to a part of the body on the upstream side of the refrigerant flow with respect to the passage forming member.
  • the passage forming member is formed with an insertion hole into which the guide member is slidably fitted.
  • the shaft is disposed so as to penetrate the guide member.
  • the position adjusting unit is attached to the passage forming member.
  • the position adjusting portion is provided, the position of the tip portion of the shaft relative to the passage forming member can be adjusted. Therefore, it is possible to suppress a change in driving force transmitted from the driving mechanism to the passage forming member due to variations in the axial length of the shaft. As a result, it is possible to suppress an increase in performance variation of the ejector 13 as a whole.
  • the second aspect it is possible to suppress an increase in the performance variation of the ejector configured to be able to change the passage cross-sectional area of the refrigerant passage such as the nozzle passage and the diffuser passage.
  • FIG. 1 is an overall configuration diagram of an ejector refrigeration cycle according to a first embodiment of the present disclosure. It is an axial sectional view of the ejector of the first embodiment.
  • FIG. 3 is a cross-sectional view taken along the line III-III in FIG. It is a typical expanded sectional view of the IV section of FIG.
  • FIG. 5 is a partially enlarged sectional view of the VV section of FIG. 4.
  • It is a Mollier diagram which shows the change of the state of the refrigerant
  • FIG. 3 is a cross-sectional view taken along the line III-III in FIG. It is a typical expanded sectional view of the IV section of FIG.
  • FIG. 5 is a partially enlarged sectional view of the VV section of FIG. 4.
  • It is a Mollier diagram which
  • FIG. 8 is a sectional view taken along line VIII-VIII in FIG. It is a typical expanded sectional view of a position adjustment part and a load adjustment screw of a 3rd embodiment of this indication.
  • FIG. 10 is a sectional view taken along line XX in FIG. 9.
  • FIG. 1 A first embodiment of the present disclosure will be described with reference to FIGS. 1 to 6.
  • the ejector 13 of the present embodiment is applied to a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression apparatus, that is, an ejector refrigeration cycle 10.
  • This ejector-type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior that is a space to be air-conditioned. Therefore, the cooling target fluid of the ejector refrigeration cycle 10 of the present embodiment is blown air.
  • R134a is adopted as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured.
  • 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 liquid-phase 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 of 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.
  • 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. Also, the up and down arrows in FIG. 3 indicate the up and down directions when the ejector 13 is mounted on the vehicle.
  • 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.
  • the upper body 311, the lower body 312, and the gas-liquid separation body 313 form an outer shell of the ejector 13 and function as a housing that accommodates other components inside.
  • the upper body 311, the lower body 312, and the gas-liquid separation body 313 are formed of hollow members made of metal (in this embodiment, made of an aluminum alloy).
  • the upper body 311, the lower body 312 and the gas-liquid separation body 313 may be formed of resin.
  • constituent members of the body 30 such as a nozzle body 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 31 a is a refrigerant inlet through which the high-pressure refrigerant that has flowed out of the radiator 12 flows.
  • the refrigerant suction port 31b is a refrigerant inflow port that sucks the low-pressure refrigerant that has flowed out of the evaporator 14.
  • the gas-liquid separation body 313 is formed with a plurality of refrigerant outlets such as a liquid-phase refrigerant outlet 31c and a gas-phase refrigerant outlet 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 inside 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 body 32 is formed of a cylindrical member made of metal (in this embodiment, stainless steel). As shown in FIGS. 2 and 3, the nozzle body 32 is disposed on the bottom surface of the upper body 311 on the lower body 312 side. The nozzle body 32 is fixed by press fitting into a fixing hole formed in the upper body 311. Therefore, the refrigerant does not leak from the gap between the upper body 311 and the nozzle body 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. Further, as is apparent from FIG. 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.
  • the upper body 311 is formed with a refrigerant inflow passage 31e that guides the high-pressure refrigerant that has flowed from the refrigerant inlet 31a into the inflow space 30a.
  • the refrigerant inflow passage 31e is formed in a shape extending in the radial direction when viewed from the axial direction of the inflow space 30a, and is formed so as to allow the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a. Has been.
  • 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 30 b is arranged coaxially with the central axis CL of the passage forming member 35.
  • the nozzle body 32 is formed with a throat portion 30m that most reduces the refrigerant passage cross-sectional area of the decompression space 30b (specifically, a nozzle passage 13a described later).
  • the top side of the passage forming member 35 formed in a conical shape is disposed in the decompression space 30b.
  • the passage forming member 35 is a valve body portion that changes the passage cross-sectional area of the refrigerant passage formed inside the ejector 13 by being displaced in the direction of the central axis CL.
  • the passage forming member 35 is formed in a conical shape whose outer diameter increases with increasing distance from the decompression space 30b (that is, toward the downstream side of the refrigerant flow).
  • a refrigerant passage in which the shape of the vertical cross section in the axial direction is annular between the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle body 32 and the outer peripheral surface of the portion on the top side of the passage forming member 35. Is formed.
  • the refrigerant passage is a nozzle passage 13a that functions as a nozzle that decompresses and injects the refrigerant.
  • the detailed configuration of the passage forming member 35 will be described later.
  • the passage sectional area decreases from the inflow space 30a side toward the throat 30m, and the passage sectional area increases again from the throat portion 30m toward the refrigerant flow downstream side. That is, in the nozzle passage 13a of the present embodiment, the passage cross-sectional area changes in the refrigerant flow direction in the same manner as a so-called Laval nozzle.
  • the pressure of the refrigerant can be reduced, and the flow rate of the refrigerant can be increased to a supersonic speed for injection.
  • the diffuser body 33 is disposed inside the upper body 311 and on the downstream side of the refrigerant flow with respect to the nozzle body 32.
  • the diffuser body 33 is formed of a cylindrical member made of metal (in this embodiment, aluminum alloy).
  • the outer periphery of the diffuser body 33 is press-fitted into the inner peripheral side surface of the upper body 311 and is fixed to the upper body 311.
  • An O-ring as a seal member (not shown) is disposed between the outer peripheral surface of the diffuser body 33 and the inner peripheral surface of the upper body 311. Therefore, the refrigerant does not leak from the gap between the diffuser body 33 and the upper body 311.
  • a through hole 33a penetrating in the axial direction is formed at the center of the diffuser body 33.
  • the central axis of the through hole 33 a is arranged coaxially with the central axis CL of the passage forming member 35.
  • the through-hole 33a is formed in a substantially truncated cone shape whose cross-sectional area increases toward the downstream side of the refrigerant flow.
  • the tip of the nozzle body 32 on the refrigerant injection port side extends to the inside of the through hole 33 a of the diffuser body 33. Then, the refrigerant sucked from the refrigerant suction port 31b is circulated between the inner peripheral surface of the through hole 33a of the diffuser body 33 and the outer peripheral surface of the cylindrical tip portion of the nozzle body 32, thereby reducing the pressure reducing space 30b ( That is, the downstream side of the suction passage 13b that leads the refrigerant flow downstream of the nozzle passage 13a) is formed.
  • the suction refrigerant outlet that 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.
  • 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 refrigerant flow downstream side of the top of the passage forming member 35 is disposed.
  • the refrigerant whose axial cross section is annular between the inner peripheral surface of the portion of the diffuser body 33 forming the pressurizing space 30e and the outer peripheral surface of the passage forming member 35 on the downstream side of the refrigerant flow.
  • a passage is formed.
  • This refrigerant passage is a diffuser passage 13c that functions as a boosting unit that boosts the pressure by mixing the injected refrigerant and the suction refrigerant.
  • the passage cross-sectional area is gradually enlarged toward the downstream side of the refrigerant flow.
  • the passage forming member 35 is formed of a conical member made of metal (in this embodiment, stainless steel).
  • a substantially frustoconical storage space 35 a 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).
  • an insertion hole 35b is formed at the top of the passage forming member 35 so as to communicate with the accommodation space 35a.
  • the internal space of the insertion hole 35b is formed in a columnar shape.
  • the accommodation space 35 a and the insertion hole 35 b are both formed so that the central axis is arranged coaxially with the central axis CL of the passage forming member 35.
  • the small diameter portion 39a of the guide member 39 is slidably fitted in the insertion hole 35b.
  • the guide member 39 is fixed to the body 30 (specifically, the upper body 311) and slidably supports the passage forming member 35.
  • the guide member 39 is formed in a cylindrical shape with the same material as the passage forming member 35.
  • the guide member 39 has a small diameter portion 39a and a large diameter portion 39b.
  • the small diameter portion 39a is formed in a cylindrical shape.
  • the central axis of the small diameter portion 39 a is arranged coaxially with the central axis CL of the passage forming member 35.
  • the passage forming member 35 is slidably supported by the guide member 39 by the small diameter portion 39a being slidably fitted into the insertion hole 35b of the passage forming member 35.
  • the outer diameter dimension of the small-diameter portion 39a and the inner diameter dimension of the insertion hole 35b are in a dimensional relationship with a clearance fit.
  • An O-ring as a seal member is disposed between the outer peripheral surface of the small diameter portion 39a and the inner peripheral surface of the insertion hole 35b. Therefore, the refrigerant does not leak from the gap between the outer peripheral surface of the small diameter portion 39a and the inner peripheral surface of the insertion hole 35b.
  • cylindrical small-diameter portion 39a is slidably supported in the insertion hole 35b that forms the columnar inner space, so that the displacement direction of the passage forming member 35 is in the direction of the central axis of the decompression space 30b. It is suppressed that it inclines with respect to it.
  • the large diameter portion 39b is formed at one end portion of the guide member 39 (specifically, the end portion on the opposite side of the passage forming member 35 side).
  • the large diameter portion 39b is formed in a cylindrical shape having a larger outer diameter than the small diameter portion 39a.
  • the large-diameter portion 39b is fixed by press-fitting into a fixing hole formed in the upper body 311. Therefore, the large-diameter portion 39b is fixed to a portion of the body 30 on the upstream side of the refrigerant flow with respect to the passage forming member 35.
  • the other end of the guide member 39 (specifically, the end of the narrow diameter portion 39a on the side of the passage forming member 35) is positioned in the accommodation space 35a of the passage forming member 35. Further, a coil spring 40 is disposed in the accommodation space 35 a on the outer peripheral side of the small diameter portion 39 a of the guide member 39.
  • the coil spring 40 is an elastic member that applies a load in a direction to reduce the passage cross-sectional area of the throat portion 30 m to the passage forming member 35.
  • a threaded portion is formed on the outer peripheral side of the other end of the small diameter portion 39a.
  • a load adjusting screw 41 is screwed onto the threaded portion (that is, attached by screw fastening). Therefore, the load adjustment screw 41 is disposed in the accommodation space 35a.
  • the load adjusting screw 41 is a load adjusting unit that adjusts the load that the coil spring 40 acts on the passage forming member 35.
  • the load adjusting screw 41 is formed of a disk-shaped metal (stainless steel in the present embodiment).
  • a through hole penetrating the front and back is formed at the center of the load adjusting screw 41, and a thread portion is formed on the inner peripheral side of the through hole.
  • a shaft 38 is disposed inside the guide member 39 formed in a cylindrical shape so as to be displaceable in the axial direction.
  • the shaft 38 transmits a driving force output from a driving mechanism 37 described later to the passage forming member 35.
  • the shaft 38 is a rod-shaped member (columnar member) formed of the same material as the guide member 39.
  • the outer diameter of the shaft 38 is formed smaller than the inner diameter of the guide member 39. Further, an O-ring as a seal member is disposed between the outer peripheral surface of the shaft 38 and the inner peripheral surface of the large diameter portion 39 b of the guide member 39. The refrigerant does not leak from the gap with the peripheral surface.
  • Both end portions of the shaft 38 protrude from both end portions of the guide member 39.
  • One tip portion of the shaft 38 (specifically, the tip portion on the side opposite to the passage forming member 35 side) is connected to the drive mechanism 37.
  • the other tip portion of the shaft 38 (specifically, the end portion on the passage forming member 35 side) is positioned in the accommodation space 35a.
  • the other tip end portion of the shaft 38 is in contact with the position adjusting portion 42 as shown in FIG.
  • the position of the other tip portion of the shaft 38 relative to the passage forming member 35 in the direction of the central axis CL is restricted.
  • the relative position of the shaft 38 with respect to the passage forming member 35 is determined by the other tip portion of the shaft 38 being in contact with the position adjusting portion 42.
  • the position adjusting part 42 has a contact part 42a and a position adjusting screw part 42b.
  • the contact part 42a and the position adjusting screw part 42b are formed of separate members. Both the contact part 42a and the position adjusting screw part 42b are formed of metal (in this embodiment, stainless steel).
  • the abutting portion 42a has a bottom surface extending perpendicularly to the central axis CL, and the tip portion of the shaft 38 abuts on the bottom surface. Further, the abutting portion 42a has a side surface extending from the bottom surface side to the top portion side of the passage forming member 35 and extending in the direction of the central axis CL, and on the inner peripheral side of this side surface, the outer periphery of the load adjusting screw 41 is provided. The sides are in contact. That is, the contact portion 42 a is in contact with both the load adjusting screw 41 and the shaft 38.
  • two planes 411 are arranged parallel to each other and parallel to the central axis CL. Two planes are formed. Further, on the inner peripheral side of the cylindrical portion of the abutting portion 42a, two planes 421 that are arranged in parallel to the two planes 411 of the load adjusting screw 41 and abut against the respective planes are formed.
  • the position adjusting screw portion 42b is formed of a disk-shaped member made of metal (in this embodiment, stainless steel). A screw portion is formed on the outer peripheral side of the position adjusting screw portion 42b.
  • the position adjusting screw part 42b is attached to the accommodation space 35a side of the passage forming member 35 by screw fastening in a state in contact with the bottom surface of the contact part 42a.
  • the position adjusting screw portion 42b and the contact portion 42a are formed as separate members. For this reason, when the position adjustment screw part 42b is rotated around the center axis CL using a hexagon wrench or the like, the contact part 42a is displaced in the direction of the center axis CL without rotating together with the position adjustment screw part 42b. Thereby, the position of the other front-end
  • a through hole penetrating the front and back is formed at the center of the position adjusting screw portion 42b.
  • the through hole is provided to rotate the contact portion 42a around the central axis CL using a hexagon wrench or the like.
  • the drive mechanism 37 is disposed outside the upper body 311 and on an extension line on one side of the shaft 38 in the axial direction.
  • the driving mechanism 37 outputs a driving force for displacing the passage forming member 35.
  • 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 37 a 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 R134a (for example, a mixed medium of R134a 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) formed in the upper body 311.
  • 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 portion 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. Therefore, in this embodiment, a metal thin plate made of stainless steel (SUS304) is adopted as the diaphragm 371.
  • 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 so as to come into contact with the diaphragm 371. Further, one end of the shaft 38 is connected to the plate member 374.
  • the shaft 38 and the passage forming member 35 are displaced so that the load received from the drive mechanism 37 (specifically, the diaphragm 371) and the load received from the coil spring 40 are balanced.
  • the drive mechanism 37 of the present 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. Then, the passage cross-sectional area in the throat portion 30m is adjusted so that the superheat degree SH of the evaporator 14 outlet-side refrigerant approaches the predetermined reference superheat degree KSH.
  • the reference superheating degree KSH can be changed by adjusting the load that the passage forming member 35 receives from the coil spring 40 with the load adjusting screw 41. Furthermore, the coil spring 40 of the present embodiment also functions as a vibration suppressing member that suppresses the passage forming member 35 from vibrating due to vibrations transmitted from the outside.
  • a cover member 375 covering 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.
  • a mixed refrigerant outlet 31g is formed at the downstream side of the refrigerant flow of the lower body 312.
  • 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 central axis of the gas-liquid separation body 313 and the central axis of the gas-liquid separation space 30f are orthogonal to the central axis CL.
  • 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 disposed coaxially with the gas-liquid separation space 30f and extends in the vertical direction is disposed.
  • 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 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 hole for returning the refrigeration oil dissolved in the liquid phase refrigerant into the compressor 11 through the gas phase refrigerant passage together with a small amount of the liquid phase 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 refrigerant 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) arranged near the instrument panel in the front part of the passenger compartment is connected to the input side of the control device. Then, operation signals from various operation switches provided on the operation panel are input to the control device. 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.
  • 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.
  • the configuration (hardware and software) for controlling the operation constitutes a dedicated control unit for 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 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. At this time, the control device increases the refrigerant discharge capacity of the compressor 11 as the heat load of the ejector refrigeration cycle 10 increases.
  • 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 in the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a in FIG. 6).
  • Point ⁇ b
  • 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. 6).
  • the passage cross-sectional area in the throat 30m of the decompression space 30b is adjusted so that the superheat degree of the evaporator 14 outlet side refrigerant (point h in FIG. 6) approaches the reference superheat degree KSH.
  • the refrigerant flowing out of the evaporator 14 (point h in FIG. 6) 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 refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b flow into the diffuser passage 13c and merge (point c ⁇ d, point h1 ⁇ d in FIG. 6).
  • 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 its pressure (point h ⁇ point h1 in FIG. 6). Thereby, the speed difference between the suction refrigerant and the injection refrigerant is reduced, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser passage 13c is reduced.
  • the kinetic energy of the refrigerant is converted into pressure energy by expanding the passage cross-sectional area.
  • the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d ⁇ point e in FIG. 6).
  • the refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (point e ⁇ point f, point e ⁇ point g in FIG. 6).
  • the liquid-phase refrigerant separated in the gas-liquid separation space 30f flows into the evaporator 14 with a pressure loss when flowing through the refrigerant flow path from the ejector 13 to the evaporator 14 (g point ⁇ g1 in FIG. 6). 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. 6). 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. 6).
  • 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 (throat portion 30m) of the nozzle passage 13a is displaced. And the passage cross-sectional area of the diffuser passage 13c can be adjusted.
  • the passage sectional area of the refrigerant passage (specifically, the nozzle passage 13a and the diffuser passage 13c) formed inside is changed according to the load fluctuation of the ejector refrigeration cycle 10, and the ejector refrigeration cycle 10 is changed.
  • the ejector 13 can be actuated appropriately according to the flow rate of the circulating refrigerant circulating.
  • the guide member 39 is disposed so as to extend from the part of the body 30 upstream of the passage formation member 35 toward the passage formation member from the coolant flow upstream side, and the coil spring 40 is accommodated. It is arranged on the outer peripheral side of the guide member 39 in the space 35a. In addition to this, a load adjusting screw 41 is attached to the guide member 39 in the accommodation space 35a.
  • the coil spring 40 and the load adjusting screw 41 for supporting the passage forming member 35 are not arranged on the downstream side of the refrigerant flow with respect to the passage forming member 35, that is, on the downstream side of the diffuser passage 13c. As a result, it is possible to suppress an increase in pressure loss that occurs when the refrigerant flows downstream from the diffuser passage 13c.
  • the ejector 13 of the present embodiment it is possible to suppress a decrease in the boosting performance of an ejector configured to be able to change the passage cross-sectional area of the refrigerant passage such as the nozzle passage 13a and the diffuser passage 13c.
  • the position adjusting portion 42 since the position adjusting portion 42 is provided, the position of the tip portion of the shaft 38 with respect to the passage forming member 35 can be adjusted. Therefore, it is possible to suppress a change in the driving force transmitted from the driving mechanism 37 to the passage forming member 35 due to variations in the length of the shaft 38 in the central axis CL direction. As a result, it is possible to suppress an increase in performance variation of the ejector 13 as a whole.
  • the ejector 13 of the present embodiment it is possible to suppress an increase in performance variation of the ejector configured to be able to change the passage cross-sectional area of the refrigerant passage such as the nozzle passage 13a and the diffuser passage 13c.
  • the position adjusting portion 42 of the present embodiment is fixed to the passage forming member 35 and adjusts the position of the tip portion of the shaft 38 by contacting the tip portion of the shaft 38 in the accommodation space 35a. Therefore, it is possible to reliably realize a configuration in which the position adjusting unit 42 is not disposed on the downstream side of the diffuser passage 13c.
  • the performance variation of the ejector 13 can be reduced without causing a decrease in the boosting performance of the ejector configured to be able to change the passage sectional area of the refrigerant passage such as the nozzle passage 13a and the diffuser passage 13c. Increase can be suppressed.
  • the load adjusting screw 41 is attached to the guide member 39 by screw fastening. Therefore, the load that the passage forming member 35 receives from the coil spring 40 can be easily adjusted. Further, the position adjusting screw portion 42b of the position adjusting portion 42 is attached to the passage forming member 35 by screw fastening. Therefore, the relative position of the shaft 38 with respect to the passage forming member 35 can be easily adjusted.
  • the position adjustment unit 42 of the present embodiment has a contact portion 42a that is arranged to be rotatable around the central axis CL with respect to the position adjustment screw portion 42b, and adjusts the load as the contact portion 42a rotates.
  • the screw 41 is rotated. Thereby, the attachment position of the load adjustment screw 41 can be changed irrespective of the attachment position of the position adjustment screw part 42b.
  • the position adjustment unit 42 can adjust the position of the shaft 38 without being affected by the load adjustment by the load adjustment screw 41.
  • the load adjustment screw 41 can adjust the load of the coil spring 40 without being affected by the position adjustment by the position adjustment unit 42.
  • the load adjustment screw 41 and the position adjustment unit 42 of this embodiment can perform load adjustment and position adjustment independently of each other.
  • the ejector 13 since the ejector 13 according to the present embodiment includes the coil spring 40 that functions as a vibration suppressing member, vibration transmitted from the outside and vibration of the passage forming member 35 caused by pressure pulsation when the refrigerant is decompressed are suppressed. Can be attenuated. Thereby, the anti-vibration performance as the whole ejector 13 can be improved.
  • FIGS. 7 and 8 are drawings corresponding to FIGS. 4 and 5 described in the first embodiment, respectively.
  • the contact portion 42a of the position adjusting portion 42 of the present embodiment has a plurality of (four in this embodiment) columnar shapes extending in the central axis CL direction from the bottom surface toward the load adjusting screw 41 side.
  • the pin 422 is provided.
  • the load adjusting screw 41 has a pin hole 412 into which the pin 422 is slidably fitted.
  • the load adjusting screw 41 is rotated together with the contact portion 42a and displaced in the direction of the central axis CL. Therefore, the load by the coil spring 40 can be adjusted by rotating the contact portion 42a.
  • the structure of the other ejector 13 is the same as that of 1st Embodiment. Therefore, also in the ejector 13 of this embodiment, the effect similar to 1st Embodiment can be acquired.
  • the contact portion 42a of the position adjusting unit 42 of the present embodiment is a plurality of (two in the present embodiment) cylindrical shapes extending from the bottom surface in the direction of the central axis CL, as in the second embodiment.
  • a pin 422 is provided.
  • the load adjusting screw 41 is formed with a groove 413 that is recessed from the outer peripheral side to the inner peripheral side and that the pin 422 is slidably supported.
  • the load adjusting screw 41 is rotated together with the contact portion 42a and displaced in the direction of the central axis CL. Therefore, the load by the coil spring 40 can be adjusted by rotating the contact portion 42a.
  • the structure of the other ejector 13 is the same as that of 1st Embodiment. Therefore, also in the ejector 13 of this embodiment, the effect similar to 1st Embodiment can be acquired.
  • the position adjusting unit has the position adjusting screw part 42b attached to the passage forming member 35 by screw fastening
  • the position adjusting unit is not limited to this.
  • the position adjusting portion may be fixed to the passage forming member 35 by means such as press fitting, caulking, welding, and adhesion.
  • the configuration of the ejector 13 is not limited to that disclosed in the above embodiment.
  • a metal member is employed as the passage forming member 35
  • a resin member may be employed to reduce the weight of the entire ejector 13.
  • a resin-made material is used as the passage forming member 35, it is desirable to use a material that does not change the slidability with the guide member 39 or the mounting property of the position adjusting screw portion 42b due to a temperature change or the like. .
  • a metal thin plate is used as the pressure responsive member of the drive mechanism 37
  • a rubber member may be used as the pressure responsive member.
  • the rubber diaphragm one made of HNBR (hydrogenated nitrile rubber) may be employed.
  • the driving mechanism an electric mechanism such as an electric motor or a solenoid that outputs a driving force for displacing the passage forming member 35 and transmits the driving force to the passage forming member 35 via the shaft 38 is adopted. May be.
  • 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 arrangement of the ejector 13 is not limited to this.
  • 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.
  • Each component device constituting the ejector refrigeration cycle 10 is not limited to that disclosed in the above-described embodiment.
  • a subcool type heat exchanger is employed as the radiator 12
  • 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.
  • R134a is adopted as the refrigerant
  • the refrigerant is not limited to this.
  • R1234yf, 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 is applied to a vehicle air conditioner.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

Éjecteur appliqué à un dispositif à cycle de réfrigération de type à compression de vapeur (10). L'éjecteur est pourvu d'un corps (30), d'un élément de formation de chemin (35), d'un mécanisme d'entraînement (37), d'un élément de guidage (39), d'un élément élastique (40) et d'une section de régulation de charge (41). Le corps comporte un espace d'écoulement entrant (30a), un espace de réduction de pression (30b), un chemin d'aspiration (13b) et un espace d'augmentation de pression (30e). Le mécanisme d'entraînement déplace l'élément de formation de chemin. L'élément de guidage est fixé au corps et supporte l'élément de formation de chemin de manière coulissante. L'élément élastique applique une charge à l'élément de formation de chemin. L'élément de guidage s'étend dans la direction dans laquelle l'élément de formation de chemin est déplacé, et un premier côté d'extrémité de l'élément de guidage est fixé à la partie du corps, qui se situe en amont de l'élément de formation de chemin. Dans l'élément de formation de chemin sont formés : un trou d'introduction (35b) dans lequel l'élément de guidage est installé de manière coulissante; et un espace de réception (35a) pour recevoir une partie de l'élément de guidage. La section de régulation de charge est montée sur l'élément de guidage.
PCT/JP2017/028665 2016-09-12 2017-08-08 Éjecteur Ceased WO2018047563A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-177389 2016-09-12
JP2016177389A JP2018044442A (ja) 2016-09-12 2016-09-12 エジェクタ

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WO2018047563A1 true WO2018047563A1 (fr) 2018-03-15

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PCT/JP2017/028665 Ceased WO2018047563A1 (fr) 2016-09-12 2017-08-08 Éjecteur

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WO (1) WO2018047563A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108843800B (zh) * 2018-06-20 2020-05-05 江苏大学 一种圆盘卷吸式自吸阀

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1350095A (en) * 1918-03-11 1920-08-17 Surface Comb Co Inc Method of and apparatus for unloading pumps
JP2013177879A (ja) * 2012-02-02 2013-09-09 Denso Corp エジェクタ
JP2017031975A (ja) * 2015-07-28 2017-02-09 株式会社デンソー エジェクタ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1350095A (en) * 1918-03-11 1920-08-17 Surface Comb Co Inc Method of and apparatus for unloading pumps
JP2013177879A (ja) * 2012-02-02 2013-09-09 Denso Corp エジェクタ
JP2017031975A (ja) * 2015-07-28 2017-02-09 株式会社デンソー エジェクタ

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