JP6032122B2 - Ejector - Google Patents

Description

  The present invention relates to an ejector that decompresses a fluid and sucks the fluid by a suction action of a high-speed jet fluid.

  Conventionally, Patent Document 1 discloses a decompression device that is applied to a vapor compression refrigeration cycle device to decompress a refrigerant.

  The decompression device of Patent Document 1 has a main body that forms a swirling space for swirling the refrigerant. By swirling the refrigerant in this swirling space, the refrigerant pressure on the swiveling center side is reduced and the refrigerant is boiled under reduced pressure. The pressure is reduced to the pressure (which causes cavitation). Then, the refrigerant in the gas-liquid mixed state, in which the gas-phase refrigerant and the liquid-phase refrigerant on the turning center side are mixed, is caused to flow into the minimum passage area and decompressed.

  Thereby, in the decompression device of patent document 1, even if the state of the refrigerant flowing into the swirl space changes due to a change in the outside air temperature or the like, the density of the refrigerant flowing into the minimum passage area is suppressed from greatly changing. Thus, fluctuations in the refrigerant flow rate flowing out to the downstream side of the decompression device are suppressed.

  Patent Document 1 also describes an ejector configured using this pressure reducing device as a nozzle. In this type of ejector, the gas-phase refrigerant that has flowed out of the evaporator is sucked by the suction action of the jet refrigerant injected from the nozzle, and the jet refrigerant and the suction refrigerant are mixed and boosted by the booster section (diffuser section). Can do.

  Therefore, in a refrigeration cycle apparatus including an ejector as a refrigerant decompression means (hereinafter referred to as an ejector-type refrigeration cycle), the power consumption of the compressor can be reduced using the refrigerant pressure-increasing action in the pressure-increasing portion of the ejector. The coefficient of performance (COP) of the cycle can be improved as compared with a normal refrigeration cycle apparatus provided with an expansion valve or the like as the refrigerant pressure reducing means.

  Furthermore, in the ejector described in Patent Document 1, as described above, the flow rate variation of the injected refrigerant injected from the nozzle is suppressed, and the refrigerant in the gas-liquid mixed state is decompressed in the minimum passage area portion of the nozzle. The nozzle efficiency is improved by promoting the boiling of the liquid refrigerant flowing into the minimum passage area. The nozzle efficiency is energy conversion efficiency when the pressure energy of the refrigerant is converted into kinetic energy at the nozzle.

JP 2012-202653 A

  By the way, in the ejector described in patent document 1, the refrigerant | coolant pressure by the side of a turning center is reduced to the pressure which a refrigerant | coolant boils under pressure by turning a refrigerant | coolant within turning space. Therefore, even if the refrigerant flowing into the swirl space is a liquid phase refrigerant or a gas-liquid two-phase refrigerant having a relatively low dryness, a gas phase refrigerant is generated in the swirl space, and the gas phase refrigerant and the liquid phase refrigerant are generated. Can be introduced into the minimum passage area of the nozzle.

  However, if the refrigerant flowing into the swirl space is a gas-liquid two-phase refrigerant having a relatively high dryness, the dryness of the refrigerant cannot be reduced in the swirl space. The ratio of the liquid-phase refrigerant in the inflowing gas-liquid mixed state refrigerant will decrease. As a result, the amount of liquid-phase refrigerant that can be boiled in the vicinity of the minimum passage area portion is reduced, and the injection refrigerant injected from the nozzle cannot be sufficiently accelerated. As a result, the nozzle efficiency cannot be sufficiently improved.

  In contrast, in the ejector-type refrigeration cycle of Patent Document 1, as a condenser that condenses the refrigerant discharged from the compressor, the refrigerant and the outside air are heat-exchanged to cool the refrigerant until it reaches a supercooled liquid phase state. By adopting a subcool type condenser, the dryness of the refrigerant flowing into the swirling space is prevented from increasing.

  However, even if a subcool type condenser is adopted, for example, when the outside air temperature is relatively high, the dryness of the refrigerant flowing out of the condenser may be high. Therefore, even if the ejector described in Patent Document 1 is applied to an ejector refrigeration cycle having a subcool condenser, the nozzle efficiency cannot be sufficiently improved.

  In view of the above, an object of the present invention is to sufficiently improve the nozzle efficiency regardless of the state of the refrigerant flowing into the swirling space in an ejector that depressurizes the refrigerant swirling in the swirling space.

The present invention has been devised to achieve the above object, and in the invention described in claim 1, an ejector applied to the vapor compression refrigeration cycle apparatus (10),
A swirling space forming member (33c) that forms a swirling space (30b) for swirling the refrigerant, and nozzle passages (30c, 30d) that function as nozzles that decompress and inject the refrigerant that has flowed out of the swirling space (30b) are formed. From the nozzle passage forming member (33b), the refrigerant suction port (31b) for sucking the refrigerant by the suction action of the high-speed jet refrigerant jetted from the nozzle passages (30c, 30d), the jetted refrigerant and the refrigerant suction port (31b) A pressurized space (30 g) for converting the velocity energy of the mixed refrigerant with the sucked suction refrigerant into pressure energy, and a gas-liquid separation space (30 h) for separating the gas and liquid of the refrigerant flowing out from the pressurized space (30 g) are formed. Body (30)
The refrigerant in the swirl space (30b) and the refrigerant in the gas-liquid separation space (30h) are configured to be able to exchange heat.

  According to this, by turning the refrigerant in the swirling space (30b), the refrigerant pressure on the turning center side of the swirling space (30b) can be reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation). . Then, the refrigerant in the gas-liquid mixed state in which the gas-phase refrigerant and the liquid-phase refrigerant on the turning center side of the turning space (30b) are mixed flows into the nozzle passages (30c, 30d) formed by the nozzle passage forming member (33b). To reduce the pressure.

  Further, since the refrigerant in the swirl space (30b) and the refrigerant in the gas-liquid separation space (30h) are configured to be able to exchange heat, the gas-liquid separation is reduced in pressure by the pressure in the nozzle passages (30c, 30d). The refrigerant in the swirling space (30b) can be cooled by the refrigerant in the space (30h).

  Therefore, even if the refrigerant flowing into the swirl space (30b) is a gas-liquid two-phase refrigerant having a relatively high dryness, the dryness of the refrigerant can be reduced in the swirl space (30b). It can suppress that the ratio of the liquid phase refrigerant | coolant in the refrigerant | coolant of the gas-liquid mixed state flowed into a channel | path (30c, 30d) falls.

  As a result, regardless of the state of the refrigerant flowing into the swirling space (30b), the injection refrigerant injected from the nozzle passage (30c, 30d) can be sufficiently accelerated, and the nozzle passage (30c, 30d) The energy conversion efficiency (equivalent to the nozzle efficiency of the prior art) when converting the pressure energy of the refrigerant into velocity energy can be sufficiently improved.

  Note that the gas-liquid mixed state refrigerant does not mean only a gas-liquid two-phase state refrigerant but also includes a refrigerant in which bubbles are mixed in the supercooled liquid phase state.

  Moreover, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a typical whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is a typical axial sectional view of the ejector of a 1st embodiment. It is III-III sectional drawing of FIG. It is a Mollier diagram which shows the state of the refrigerant | coolant in the ejector-type refrigerating cycle of 1st Embodiment. It is a typical axial sectional view of an ejector of a 2nd embodiment.

(First embodiment)
1st Embodiment of this invention is described using FIGS. 1-4. As shown in the overall configuration diagram of FIG. 1, the ejector 13 of this embodiment is applied to a refrigeration cycle apparatus including an ejector as a refrigerant decompression unit, that is, an ejector refrigeration cycle 10. Furthermore, this ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling the blown air blown into the vehicle interior, which is the air-conditioning target space.

  The ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as a refrigerant, and constitutes a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. doing. Of course, you may employ | adopt HFO type refrigerant | coolants (for example, R1234yf). Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.

  In the ejector-type refrigeration cycle 10, the compressor 11 sucks the refrigerant and discharges it until it becomes high-pressure refrigerant. Specifically, the compressor 11 of the present embodiment is an electric compressor configured by housing a fixed capacity type compression mechanism 11a and an electric motor 11b for driving the compression mechanism 11a in one housing.

  As the compression mechanism 11a, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed. Further, the electric motor 11b is controlled in its operation (number of rotations) by a control signal output from a control device to be described later, and may adopt either an AC motor or a DC motor.

  The compressor 11 may be an engine-driven compressor that is driven by a rotational driving force transmitted from a vehicle travel engine via a pulley, a belt, or the like. This type of engine-driven compressor includes a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, and a fixed type that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch. A capacity type compressor or the like can be employed.

  The refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port side of the compressor 11. The radiator 12 is a heat exchanger for heat radiation that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (outside air) blown by the cooling fan 12d. .

  More specifically, the radiator 12 is a condensing unit 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 to radiate and condense the high-pressure gas-phase refrigerant. 12a, a receiver 12b that separates the gas-liquid refrigerant flowing out of the condensing unit 12a and stores excess liquid-phase refrigerant, and a liquid-phase refrigerant that flows out of the receiver unit 12b and the outside air blown from the cooling fan 12d exchange heat. This is a so-called subcool condenser that includes a supercooling section 12c that supercools the liquid-phase refrigerant.

  The cooling fan 12d is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device. A refrigerant inlet 31 a of the ejector 13 is connected to the refrigerant outlet side of the supercooling portion 12 c of the radiator 12.

  The ejector 13 functions as a refrigerant pressure reducing means for reducing the pressure of the supercooled high-pressure liquid-phase refrigerant that has flowed out of the radiator 12 to flow downstream, and will be described later by the suction action of the refrigerant that is injected at a high speed. It functions as a refrigerant circulating means (refrigerant transporting means) for sucking (transporting) and circulating the refrigerant flowing out of the evaporator 14. Furthermore, the ejector 13 according to the present embodiment also functions as a gas-liquid separation unit that separates the gas-liquid of the decompressed refrigerant.

  A specific configuration of the ejector 13 will be described with reference to FIGS. In addition, the up and down arrows in FIG. 2 indicate the up and down directions in a state where the ejector refrigeration cycle 10 is mounted on the vehicle air conditioner.

  As shown in FIG. 2, the ejector 13 of the present embodiment includes a body 30 configured by combining a plurality of constituent members. The body 30 is made of a prismatic metal or resin or the like, and includes a housing body 31 that forms the outer shell of the ejector 13, and an upper body 32, a middle body 33, a lower body 34, and the like that are fixed inside the housing body 31. It is configured.

  More specifically, a cylindrical space whose axial direction extends in the vertical direction (vertical direction) is formed inside the housing body 31. The columnar space is closed on the upper side and opened to the outside on the lower side. And the outer peripheral side of the upper body 32, the middle body 33, and the lower body 34 is being fixed to the inner peripheral wall surface of this cylindrical space in order from the upper side by press-fitting.

  The housing body 31 includes a refrigerant inlet 31 a for allowing the refrigerant flowing out of the radiator 12 to flow into the interior, a refrigerant suction port 31 b for sucking the refrigerant flowing out of the evaporator 14, and a gas-liquid formed inside the body 30. The liquid-phase refrigerant outlet 31c that causes the liquid-phase refrigerant separated in the separation space 30h to flow out to the refrigerant inlet side of the evaporator 14 and the gas-phase refrigerant separated in the gas-liquid separation space 30h are taken into the suction side of the compressor 11. A gas-phase refrigerant outlet 31d and the like are formed.

  Further, as shown in FIG. 2, the refrigerant inlet 31a is disposed on the lower side in the vertical direction of the gas-phase refrigerant outlet 31d, and the liquid-phase refrigerant outlet 31c is disposed on the lower side in the vertical direction of the refrigerant suction port 31b. ing. Further, as shown in FIG. 3, the refrigerant inlet 31 a and the liquid phase refrigerant outlet 31 c are opened at positions that are symmetric with respect to the central axis of a cylindrical space formed inside the housing body 31. . Similarly, the gas-phase refrigerant outlet 31d and the refrigerant suction port 31b are also opened at positions symmetrical with respect to the central axis.

  First, among the inlets 31 a to 31 d formed in the housing body 31, the refrigerant inlet 31 a communicates with a space formed between the lower side of the middle body 33 and the upper side of the lower body 34. This space constitutes a refrigerant inflow passage 30 a that guides the refrigerant that has flowed out of the radiator 12 to the swirling space 30 b formed inside the body 30.

  The middle body 33 is formed in a circular shape when viewed from the central axis direction indicated by a one-dot chain line in FIG. 2, and a lower disk-shaped member 33a and an upper disk in which a through hole penetrating the front and back is formed in the center portion And a cylindrical member 33c that is disposed between the lower disk-shaped member 33a and the upper disk-shaped member 33b and connects the lower disk-shaped member 33a and the upper disk-shaped member 33b. It is comprised.

  The lower disk-shaped member 33 a is formed in a flat plate shape, and the outer peripheral portion is fixed to the inner peripheral wall surface of the housing body 31. The cylindrical member 33c protrudes from the lower disk-shaped member 33a to the opposite side (that is, the upper side) of the lower body 34, and forms a columnar space inside. This space constitutes a swirling space 30b that swirls the refrigerant flowing into the inside around the central axis.

  The central axis of the columnar space (swirl space 30 b) formed inside the cylindrical member 33 c is arranged coaxially with the central axis of the columnar space formed inside the housing body 31. Furthermore, the outer diameter of the swirling space 30b is formed to be equal to the diameter of the through hole of the lower disk-shaped member 33a.

  On the other hand, the diameter of the through hole of the upper disk-shaped member 33b is formed smaller than the outer diameter of the swirling space 30b. Further, the through hole of the upper disk-shaped member 33b is also arranged coaxially with the central axis of the swirling space 30b. Furthermore, the outer diameter of the upper disk-shaped member 33b is smaller than the outer diameter of the lower disk-shaped member 33a and larger than the outer diameter of the cylindrical member 33c.

  In addition, a refrigerant passage forming member 35 formed in a shape (an abacus ball shape) in which the bottom surfaces of two conical members are bonded to each other is disposed above the upper disk-shaped member 33b. This refrigerant passage forming member 35 changes the passage cross-sectional area in the minimum passage area portion 33d formed in the through hole of the upper disk-shaped member 33b, and the flow of the refrigerant flowing out of the through hole of the upper disk-shaped member 33b. It fulfills the function of forming a refrigerant passage whose direction is directed radially outward.

  More specifically, the refrigerant passage forming member 35 has a central axis coaxially disposed with the central axis of the swirling space 30b, and a tapered tip 35a disposed at the top on the lower side has an upper disk-shaped member. It is inserted into the through hole 33b. Thus, a minimum passage area portion 33 d having the smallest refrigerant passage area is formed between the through hole of the upper disk-shaped member 33 b and the lower end portion of the refrigerant passage forming member 35.

  Further, the refrigerant passage area from the through hole of the upper disk-shaped member 33b to the tapered tip portion 35a is formed on the upstream side of the refrigerant flow from the minimum passage area portion 33d and reaches the minimum passage area portion 33d. A tapered space 30c that gradually decreases is formed. Further, a divergent space 30 d for gradually increasing the refrigerant passage area is formed between the upper surface of the upper disk-shaped member 33 b and the conical outer peripheral wall surface on the lower side of the refrigerant passage forming member 35.

  In the present embodiment, by forming the tapered space 30c and the divergent space 30d in this manner, the passage sectional area of the refrigerant passage extending from the tapered space 30c to the divergent space 30d is changed in the same manner as the Laval nozzle. Then, in the refrigerant passage from the tapered space 30c to the divergent space 30d, the flow velocity of the refrigerant in the gas-liquid mixed state is accelerated so as to become a value higher than the two-phase sound velocity, and from the divergent space 30d toward the radially outer peripheral side. Spraying.

  Accordingly, the refrigerant passage from the tapered space 30c to the divergent space 30d constitutes a nozzle passage that functions as a nozzle. Further, since this nozzle passage is formed between the upper disk-shaped member 33b and the refrigerant passage forming member 35, the cross section perpendicular to the central axis direction has an annular shape (from a circular shape to a small diameter arranged coaxially). It is formed in a donut shape excluding the circular shape.

  On the other hand, a shaft 36 a of an electric actuator 36 made of a stepping motor, which is disposed on the upper surface of the housing body 31, is connected to the top of the refrigerant passage forming member 35. The electric actuator 36 is a driving means for displacing the refrigerant passage forming member 35 in the vertical direction, and its operation is controlled by a control signal output from the control device.

  Therefore, when the electric actuator 36 displaces the refrigerant passage forming member 35 upward, the tapered tip 35a inserted into the through hole of the upper disk-like member 33b moves upward, and the minimum passage area portion 33d The cross-sectional area of the passage increases. Further, when the electric actuator 36 displaces the refrigerant passage forming member 35 downward, the tapered tip 35a moves downward, and the passage sectional area in the minimum passage area portion 33d decreases.

  The lower body 34 is a flat plate-like member formed in a circular shape when viewed from the central axis direction, and the plate surface of the lower body 34 is arranged in parallel with the plate surface of the lower disc-like member 33a. Further, the outer peripheral portion of the lower body 34 is fixed to the inner peripheral wall surface of the housing body 31. Further, the lower body 34 is formed with a plurality of rectifying plates 34a that protrude toward the middle body 33 (that is, the upper side).

  As shown in FIG. 3, the plurality of rectifying plates 34 a are annularly arranged along the outer periphery of a columnar space formed inside the cylindrical member 33 c. Further, the plate surfaces of these rectifying plates 34a are inclined or curved so as to turn the flow of the refrigerant from the outer peripheral side toward the inner peripheral side around the central axis when viewed from the central axis direction.

  Accordingly, when the refrigerant flows into the refrigerant inflow passage 30a via the refrigerant inflow port 31a, the refrigerant flows from the outer peripheral side to the inner peripheral side of the refrigerant inflow passage 30a. Flowing along. Thereby, swirl | flow can be produced in the refrigerant | coolant which flows into the space of the inner peripheral side of the some baffle plate 34a, ie, the column-shaped swirl | vortex space 30b formed in the inside of the cylindrical member 33c.

  The refrigerant swirling in the swirling space 30b is depressurized when passing through the nozzle passage formed between the upper disk-shaped member 33b of the middle body 33 and the refrigerant passage forming member 35, and moves toward the radially outer peripheral side. Is injected. In addition, the refrigerant | coolant injected from the divergent space 30d has the speed component of the direction swirled in the same direction as the refrigerant swirling in the swirl space 30b.

  Further, in the present embodiment, as shown in FIG. 3, when the refrigerant flows into the refrigerant inflow passage 30a from the refrigerant inflow port 31a, the refrigerant is caused to flow in the tangential direction of the outer periphery of the refrigerant inflow passage 30a. The swirling flow of the refrigerant flowing into 30b is promoted.

  As is clear from the above description, the lower body 34 constitutes the inflow passage forming member described in the claims, and the cylindrical member 33c constitutes the swirl space forming member, and the middle body 33 The upper disk-shaped member 33b constitutes a nozzle passage forming member, and the tapered tip end portion 35a of the refrigerant passage forming member 35 constitutes an area adjusting member.

  In other words, in this embodiment, the swirl space forming member and the nozzle passage forming member are integrally formed on the body 30 (specifically, the middle body 33). Of course, the middle body 33 may be configured by a plurality of members, and the swirl space forming member and the nozzle passage forming member may be configured by separate members from the body 30. Further, in the present embodiment, the area adjusting member is integrally formed with the refrigerant passage forming member 35.

  Here, since the swirling space 30b of the present embodiment is formed in a columnar shape, the refrigerant pressure on the central axis side is changed to the refrigerant on the outer peripheral side by the action of the centrifugal force generated by the swirling of the refrigerant in the swirling space 30b. Lower than pressure. Therefore, in the present embodiment, during normal operation of the ejector refrigeration cycle 10, the refrigerant pressure on the central axis side in the swirling space 30b is reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation).

  Such adjustment of the refrigerant pressure on the central axis side in the swirling space 30b can be performed by adjusting the number of the plurality of rectifying plates 34a and the inclination angle, or adjusting the arrangement of the plurality of rectifying plates 34a (for example, increasing For example)

  Next, among the inflow / outflow ports 31 a to 31 d formed in the housing body 31, the refrigerant suction port 31 b communicates with a space formed between the lower side of the upper surface of the housing body 31 and the upper side of the upper body 32. ing. This space constitutes an inflow space 30e for allowing the refrigerant sucked from the refrigerant suction port 31b to flow in. The inflow space 30e is also formed as a cylindrical space, and its central axis is the central axis of the swirling space 30b and the like. It is arranged on the same axis.

  Further, in the present embodiment, when the refrigerant flows into the inflow space 30e from the refrigerant suction port 31b, the refrigerant in the inflow space 30e is caused to flow in the tangential direction of the outer periphery of the inflow space 30e, thereby It is swung in the same direction as the refrigerant. The shaft 36a of the electric actuator 36 described above is disposed so as to penetrate the center of the inflow space 30e in the vertical direction.

  The upper body 32 is a disk-shaped member that is formed in a circular shape when viewed from the central axis direction, and has a through hole that penetrates the front and back at the center. Further, the outer peripheral portion of the upper body 32 is fixed to the inner peripheral wall surface of the housing body 31.

  On the lower side of the upper body 32, the aforementioned refrigerant passage forming member 35 is disposed. Between the lower surface of the upper body 32 and the conical outer peripheral wall surface on the upper side of the refrigerant passage forming member 35, the refrigerant outlet of the divergent space 30 d formed on the lower side of the inflow space 30 e and the refrigerant passage forming member 35. A suction passage 30f is formed to communicate with the side. The suction passage 30f has an annular cross section perpendicular to the central axis direction, and allows the refrigerant that has flowed in from the inflow space 30e to flow out toward the outer periphery in the radial direction.

  Furthermore, between the upper surface of the upper disk-shaped member 33b of the middle body 33 and the lower surface of the upper body 32 on the outer peripheral side of the refrigerant passage forming member 35, the refrigerant injected from the divergent space 30d and the refrigerant suction A diffuser space 30g is formed as a pressure increasing space in which the suction refrigerant sucked through the inlet 31b through the inflow space 30e and the suction passage 30f is mixed to increase the pressure.

  The diffuser space 30g has an annular cross section perpendicular to the central axis direction, and a mixed refrigerant of the injected refrigerant and the suction refrigerant flows from the inner peripheral side toward the outer peripheral side. Accordingly, it is possible to increase the pressure of the mixed refrigerant by gradually increasing the refrigerant passage area in the flow direction of the mixed refrigerant and converting the velocity energy of the mixed refrigerant into pressure energy.

  Note that the jet refrigerant injected from the divergent space 30d into the diffuser space 30g and the suction refrigerant flowing into the diffuser space 30g from the suction passage 30f both speed in the direction of turning in the same direction as the refrigerant swirling in the swirling space 30b. Has ingredients. Therefore, the refrigerant flowing through the diffuser space 30g and the refrigerant flowing out of the diffuser space 30g also have a velocity component in the direction of turning in the same direction as the refrigerant swirling in the swirling space 30b.

  Thus, by having the velocity component in which the injection refrigerant and the suction refrigerant flow in the same direction, energy loss (mixing loss) when the injection refrigerant and the suction refrigerant are mixed in the diffuser space 30g can be reduced. it can.

  A gas-liquid separation space 30h is formed on the outer peripheral side of the diffuser space 30g to separate the gas-liquid refrigerant flowing out of the diffuser space 30g. The gas-liquid separation space 30h is formed in a cylindrical shape in the space formed in the housing body 31 from the lower side of the upper body 32 to the upper side of the lower disk-shaped member 33a of the middle body 33. ing.

  As described above, the refrigerant flowing out of the diffuser space 30g has a velocity component in a direction swirling in the same direction as the refrigerant swirling in the swirling space 30b. Accordingly, the gas-liquid refrigerant is separated in the gas-liquid separation space 30h by the action of centrifugal force, and the separated liquid-phase refrigerant is stored below the gas-liquid separation space 30h.

  Here, as shown in FIG. 2, the bottom surface of the gas-liquid separation space 30h is formed by a lower disk-shaped member 33a of the middle body 33, and a cylinder of the middle body 33 is formed at the center of the gas-liquid separation space 30h. A shaped member 33c is arranged.

  Therefore, in the present embodiment, the middle body 33 is formed of a metal (for example, aluminum) having excellent heat conductivity or a heat conductive resin, so that the liquid phase refrigerant in the gas-liquid separation space 30h and the cylindrical member 33c are disposed inside. Heat exchange with the refrigerant in the formed swirl space 30b is possible, and further, the liquid phase refrigerant in the gas-liquid separation space 30h and the refrigerant inflow passage 30a formed on the lower side of the lower disk-shaped member 33a are circulated. The heat exchange with the refrigerant is possible.

  Of the inflow / outflow ports 31a to 31d formed in the housing body 31, the liquid phase refrigerant outflow port 31c communicates with the lower side of the gas / liquid separation space 30h and is separated in the gas / liquid separation space 30h. Let the refrigerant flow out. Further, the gas-phase refrigerant outlet 31d communicates with the upper side of the gas-liquid separation space 30h, and causes the liquid-phase refrigerant separated in the gas-liquid separation space 30h to flow out.

  Further, the inlet side of the evaporator 14 is connected to the liquid-phase refrigerant outlet 31c as shown in FIG. 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 whose rotation speed (amount of blown air) is controlled by a control voltage output from the control device. A refrigerant suction port 31 b of the ejector 13 is connected to the outlet side of the evaporator 14. Further, the suction side of the compressor 11 is connected to the gas-phase refrigerant outlet 31d of the ejector 13.

  Next, a control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. The control device performs various calculations and processes based on the control program stored in the ROM, and controls the operations of the various electric control target devices 11b, 12d, 14a, 36 and the like described above.

  In addition, the control device includes an internal air temperature sensor that detects the temperature inside the vehicle, an external air temperature sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and an air temperature (evaporator temperature) of the evaporator 14. A sensor group for air conditioning control such as an evaporator temperature sensor to detect, an outlet side temperature sensor to detect the temperature of the radiator 12 outlet side refrigerant, and an outlet side pressure sensor to detect the pressure of the radiator 12 outlet side refrigerant are connected, Detection values of these sensor groups are input.

  Furthermore, an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input to the control device. The As various operation switches provided on the operation panel, there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.

  Note that the control device of the present embodiment is configured integrally with control means for controlling 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 the control means of each control target device. For example, in this embodiment, the structure (hardware and software) which controls the action | operation of the electric motor 11b of the compressor 11 comprises the discharge capability control means.

  Next, the operation of the ejector refrigeration cycle 10 of the present embodiment having the above-described configuration will be described using the Mollier diagram of FIG. First, when the operation switch of the operation panel is turned on (ON), the control device operates the electric motor 11b of the compressor 11, the cooling fan 12d, the blower fan 14a, the electric actuator 36 that displaces the refrigerant passage forming member 35, and the like. . Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it.

  The high-temperature and high-pressure gas-phase refrigerant (point a4 in FIG. 4) discharged from the compressor 11 flows into the condenser 12a of the radiator 12 and exchanges heat with the blown air (outside air) blown from the cooling fan 12d. , Dissipates heat and condenses. The refrigerant that has dissipated heat in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid-phase refrigerant separated by gas and liquid in the receiver unit 12b exchanges heat with the blown air blown from the cooling fan 12d in the supercooling unit 12c, and further dissipates heat to become a supercooled liquid-phase refrigerant (see FIG. 4). a4 point → b4 point).

  The supercooled liquid phase refrigerant that has flowed out of the supercooling section 12c of the radiator 12 is isentropically depressurized in a nozzle passage formed by a refrigerant passage extending from the tapered space 30c of the ejector 13 to the divergent space 30d. It is injected from 30d (b4 point → c4 point in FIG. 4). At this time, the control device controls the operation of the electric actuator 36 so that the degree of superheat of the refrigerant on the outlet side of the evaporator 14 approaches a predetermined value.

  The refrigerant flowing out of the evaporator 14 is sucked through the refrigerant suction port 31b, the inflow space 30e, and the suction passage 30f by the suction action of the refrigerant injected from the divergent space 30d. Furthermore, the refrigerant injected from the divergent space 30d and the suction refrigerant sucked through the suction passage 30f and the like flow into the diffuser space 30g (point c4 → d4, point h4 → d4 in FIG. 4).

  In the diffuser space 30g, the velocity energy of the refrigerant is converted into pressure energy by expansion of the refrigerant passage area. As a result, the pressure of the mixed refrigerant rises while the injection refrigerant and the suction refrigerant are mixed (d4 point → e4 point in FIG. 4). The refrigerant that has flowed out of the diffuser space 30g is gas-liquid separated in the gas-liquid separation space 30h (point e4 → f4, point e4 → g4 in FIG. 4).

  The liquid-phase refrigerant separated in the gas-liquid separation space 30h flows out from the liquid-phase refrigerant outlet 31c and flows into the evaporator 14. The refrigerant flowing into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates, and the blown air is cooled (point g4 → h4 in FIG. 4). On the other hand, the gas-phase refrigerant separated in the gas-liquid separation space 30h flows out from the gas-phase refrigerant outlet 31d, is sucked into the compressor 11 and compressed again (point f4 → a4 in FIG. 4).

  The ejector refrigeration cycle 10 of the present embodiment operates as described above and can cool the blown air blown into the vehicle interior. Further, in the ejector-type refrigeration cycle 10, since the refrigerant whose pressure has been increased in the diffuser space 30g is sucked into the compressor 11, the driving power of the compressor 11 can be reduced and cycle efficiency (COP) can be improved. .

  Further, in the ejector refrigeration cycle 10 of the present embodiment, a subcool type condenser is employed as the radiator 12, so that under normal operating conditions, the refrigerant flowing into the ejector 13 is a supercooled liquid phase refrigerant. Can do. Therefore, according to the ejector 13 of the present embodiment, the energy conversion efficiency corresponding to the nozzle efficiency of the prior art can be effectively improved as described below.

  That is, according to the ejector 13 of the present embodiment, the supercooled liquid phase refrigerant is swirled in the swirling space 30b, and the refrigerant is boiled under reduced pressure at the swirling center side in the swirling space 30b (causes cavitation). Can be reduced to pressure. Thereby, the refrigerant | coolant in the turning space 30b can be made into the gas-liquid mixed state in which more gaseous-phase refrigerant | coolants exist in the inner peripheral side rather than the outer peripheral side of a turning center axis | shaft.

  Then, the gas-liquid mixed refrigerant in which the gas-phase refrigerant is unevenly distributed on the swivel center axis side is caused to flow into the nozzle passage formed by the refrigerant passage extending from the tapered space 30c to the divergent space 30d. The boiling of the liquid refrigerant can be promoted by wall boiling and interface boiling. Thereby, the state of the refrigerant in the vicinity of the minimum passage area portion 33d can be an ideal gas-liquid mixed state in which the gas-phase refrigerant and the liquid-phase refrigerant are homogeneously mixed.

  Furthermore, the refrigerant in the ideal gas-liquid mixed state is blocked (choking), and the flow rate of the refrigerant can be accelerated until it becomes equal to or higher than the two-phase sound speed. And it can accelerate further by enlarging a passage area by making the refrigerant | coolant which became 2 phase sound speed or more flow into the divergent space 30d. Thereby, the energy conversion efficiency (equivalent to the nozzle efficiency of a prior art) at the time of converting the pressure energy of a refrigerant | coolant into speed energy in a nozzle channel | path can be improved effectively.

  However, even if the subcool condenser is employed as the radiator 12 as in the ejector refrigeration cycle 10 of the present embodiment, the radiator 12 is used under operating conditions where the outside air temperature is relatively high, for example. The refrigerant cannot be cooled until it reaches the supercooled liquid phase state, and the gas-liquid two-phase refrigerant having a relatively high dryness may flow into the ejector 13.

  And when the gas-liquid two-phase refrigerant having a relatively high dryness flows into the swirl space 30b, the ratio of the liquid-phase refrigerant in the gas-liquid mixed refrigerant flowing into the nozzle passage from the swirl space 30b decreases, There is a risk that the amount of liquid-phase refrigerant that can be boiled in the vicinity of the minimum passage area portion 33d may be reduced. As a result, the injection refrigerant injected from the nozzle passage cannot be sufficiently accelerated, and the energy conversion efficiency in the nozzle passage may not be sufficiently improved.

  On the other hand, according to the ejector 13 of the present embodiment, the refrigerant in the swirl space 30b and the refrigerant in the gas-liquid separation space 30h are configured to be able to exchange heat. The refrigerant in the swirl space 30b can be cooled by the refrigerant in the gas-liquid separation space 30h.

  Therefore, even if the refrigerant flowing into the swirl space 30b is a gas-liquid two-phase refrigerant having a relatively high dryness, the dryness of the refrigerant can be reduced in the swirl space 30b and flows into the nozzle passage. It can suppress that the ratio of the liquid phase refrigerant | coolant of the refrigerant | coolant of a gas-liquid mixed state falls. Thereby, it can suppress that the quantity of the liquid phase refrigerant which can be boiled in the vicinity of the minimum channel | path area part 33d reduces.

  As a result, irrespective of the state of the refrigerant flowing into the swirling space 30b, the injection refrigerant injected from the nozzle passage can be sufficiently increased, and the energy conversion efficiency in the nozzle passage can be sufficiently improved.

  Furthermore, in this embodiment, the swirl space 30b is formed on the inner peripheral side of the cylindrical member 33c constituting the swirl space forming member, and the gas-liquid separation space 30h is formed on the outer peripheral side of the cylindrical member 33c. Therefore, it is possible to realize a configuration that allows heat exchange between the refrigerant in the swirl space 30b and the refrigerant in the gas-liquid separation space 30h very easily.

  Further, according to the ejector 13 of the present embodiment, the refrigerant in the swirl space 30b and the refrigerant in the gas-liquid separation space 30h are configured to be able to exchange heat, and the refrigerant flowing through the refrigerant inflow passage 30a Since the refrigerant in the gas-liquid separation space 30h is configured to be able to exchange heat, the refrigerant in the swirl space 30b can be more effectively cooled. As a result, the energy conversion efficiency in the nozzle passage can be reliably improved.

  Further, in this embodiment, the refrigerant inflow passage 30a is formed on the lower side in the vertical direction of the gas-liquid separation space 30h, so that the refrigerant in the swirl space 30b and the liquid-phase refrigerant in the gas-liquid separation space 30h are very easily obtained. Can be configured to exchange heat with each other.

  Further, according to the ejector 13 of the present embodiment, the refrigerant passage forming member 35 that guides the flow direction of the injection refrigerant and the flow direction of the suction refrigerant from the central axis side to the outer peripheral side is provided, and the shape of the diffuser space 30g is The mixed refrigerant with the suction refrigerant flows from the central axis side to the outer peripheral side.

  Thereby, it can suppress that the dimension of the center direction of a diffuser space expands with respect to the structure in which the diffuser space 30g is formed in the shape extended in the axial direction of a nozzle like a prior art. As a result, an increase in size of the ejector 13 as a whole can be suppressed.

  Further, according to the ejector 13 of the present embodiment, since the electric actuator 36 is provided as a driving means, the tapered tip 35a that is the area adjusting member is displaced according to the load fluctuation of the ejector refrigeration cycle 10, The passage sectional area in the minimum passage area portion 33d can be adjusted. Therefore, the ejector 13 can be appropriately operated in accordance with the load fluctuation of the ejector refrigeration cycle 10.

  Here, the divergent space 30d of the present embodiment is formed between the upper surface of the upper disk-shaped member 33b of the lower body 34 and the conical outer peripheral wall surface on the lower side of the refrigerant passage forming member 35. It is formed between the lower surface of the upper body 32 and the conical outer peripheral wall surface above the refrigerant passage forming member 35. Therefore, when the electric actuator 36 displaces the refrigerant passage forming member 35 in order to displace the tapered tip portion 35a, the refrigerant passage areas of the divergent space 30d and the suction passage 30f also change.

  On the other hand, in the present embodiment, the degree of change in the passage sectional area of the divergent space 30d and the suction passage 30f when the electric actuator 36 displaces the refrigerant passage forming member 35 is the passage sectional area in the minimum passage area portion 33d. Therefore, the change in the cross-sectional area of the divergent space 30d and the suction passage 30f has little influence on the energy conversion efficiency of the ejector 13.

  Further, in the ejector 13 of the present embodiment, the refrigerant inlet 31 a connected to the discharge port side of the compressor 11 and the gas-phase refrigerant outlet 31 d connected to the suction side of the compressor 11 are provided on the same side surface of the housing body 31. The liquid phase refrigerant outlet 31c connected to the refrigerant inlet side of the evaporator 14 and the refrigerant suction port 31b connected to the refrigerant outlet side of the evaporator 14 are arranged on the side surface facing this surface.

  Further, the refrigerant inlet 31a is arranged on the lower side in the vertical direction of the gas-phase refrigerant outlet 31d, and the liquid phase refrigerant outlet 31c is arranged on the lower side in the vertical direction of the refrigerant suction port 31b. The arrangement of the inflow / outflow ports 31a to 31d is the same as the arrangement of the inflow / outflow ports in a box-type temperature expansion valve that is a decompression device of a refrigeration cycle apparatus applied to a general vehicle air conditioner. Therefore, the ejector of the present embodiment can exhibit high mounting compatibility when used as a decompression device for a refrigeration cycle apparatus applied to a general vehicle air conditioner.

(Second Embodiment)
In the present embodiment, an example will be described in which the configuration of the driving means for displacing the tapered tip 35a, which is an area adjusting member, is changed with respect to the first embodiment as shown in FIG. In FIG. 5, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The drive means 37 of the present embodiment is disposed inside the upper body 32, below the inflow space 30 e, and on the outer peripheral side of a through hole provided in the center of the upper body 32.

  The driving means 37 is configured to have a circular thin plate-like diaphragm 37a which is a pressure responsive member. More specifically, as shown in FIG. 5, the diaphragm 37 a is fixed by means such as welding so as to partition a cylindrical space formed inside the upper body 32 into two upper and lower spaces.

  Of the two spaces partitioned by the diaphragm 37a, the space on the upper side (the inflow space 30e side) constitutes an enclosed space 37b in which a temperature-sensitive medium whose pressure changes according to the temperature of the refrigerant flowing out of the evaporator 14 is enclosed. Yes. A temperature sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed in the enclosed space 37b so as to have a predetermined density. Therefore, the temperature sensitive medium in this embodiment is R134a.

  On the other hand, the lower space of the two spaces partitioned by the diaphragm 37a constitutes an introduction space 37c into which the refrigerant flowing out of the evaporator 14 is introduced via a communication path (not shown). Therefore, the temperature of the refrigerant flowing out of the evaporator 14 is transmitted to the temperature-sensitive medium enclosed in the enclosed space 37b through the lid member 37d and the diaphragm 37a that partition the inflow space 30e and the enclosed space 37b.

  Here, as is apparent from FIG. 5, an inflow space 30 e is formed on the upper side of the upper body 32 of the present embodiment, and a suction passage 30 f is formed on the lower side of the upper body 32.

  Accordingly, at least a part of the driving means 37 is disposed at a position sandwiched from the up and down direction by the inflow space 30e and the suction passage 30f when viewed from the radial direction of the central axis, and the inflow when viewed from the central axis direction. It arrange | positions in the position which overlaps with the space 30e and the suction passage 30f. As a result, the temperature of the refrigerant flowing out of the evaporator 14 is transmitted to the enclosed space 37b, and the internal pressure of the enclosed space 37b becomes a pressure corresponding to the temperature of the refrigerant flowing out of the evaporator 14.

  Further, the diaphragm 37a is deformed according to a differential pressure between the internal pressure of the enclosed space 37b and the pressure of the refrigerant flowing out of the evaporator 14 flowing into the introduction space 37c. For this reason, the diaphragm 37a is preferably formed of a tough material having high elasticity and good heat conduction, and is preferably formed of a thin metal plate such as stainless steel (SUS304).

  Further, the upper end side of a columnar actuating rod 37e is joined to the center portion of the diaphragm 37a by means such as welding, and the outermost peripheral side of the refrigerant passage forming member 35 is fixed to the lower end side of the actuating rod 37e. Thereby, the diaphragm 37a and the refrigerant passage forming member 35 are connected, and the refrigerant passage forming member 35 and the tapered tip portion 35a are displaced in accordance with the displacement of the diaphragm 37a, and the passage sectional area in the minimum passage area portion 33d is adjusted.

  Specifically, when the temperature (superheat degree) of the refrigerant flowing out of the evaporator 14 increases, the saturation pressure of the temperature-sensitive medium enclosed in the enclosed space 37b increases, and the pressure in the introduction space 37c is subtracted from the internal pressure of the enclosed space 37b. Increased differential pressure. Thereby, the diaphragm 37a displaces the tapered tip portion 35a in the direction in which the passage cross-sectional area in the minimum passage area portion 33d is enlarged (downward in the vertical direction).

  On the other hand, when the temperature (superheat degree) of the refrigerant flowing out of the evaporator 14 is lowered, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37b is lowered, and the difference obtained by subtracting the pressure of the introduction space 37c from the internal pressure of the enclosed space 37b. The pressure is reduced. As a result, the diaphragm 37a displaces the tapered tip 35a in a direction (upward in the vertical direction) in which the passage cross-sectional area in the minimum passage area portion 33d is reduced.

  As described above, the diaphragm 37a displaces the refrigerant passage forming member 35 in the vertical direction according to the degree of superheat of the refrigerant flowing out of the evaporator 14, so that the degree of superheating of the refrigerant flowing out of the evaporator 14 approaches a predetermined value. The passage sectional area in the minimum passage area portion 33d can be adjusted. The gap between the operating rod 37e and the upper body 32 is sealed by a sealing member such as an O-ring (not shown), and the refrigerant does not leak from the gap even if the operating rod 37e is displaced.

  Further, the bottom surface of the refrigerant passage forming member 35 receives a load of a coil spring 40 disposed above the upper disk member 33b of the middle body 33 so as to cross the divergent space 30d in the vertical direction.

  The coil spring 40 applies a load that biases the refrigerant passage forming member 35 toward the side (the upper side in FIG. 5) that reduces the passage cross-sectional area in the minimum passage area 33d, and adjusts this load. Thereby, the valve opening pressure of the refrigerant passage forming member 35 can be changed to change the target degree of superheat.

  Here, since the refrigerant injected from the divergent space 30d flows between the windings of the coil spring 40, it is desirable to employ a coil spring 40 having a wire diameter or pitch that hardly obstructs the refrigerant flow in the divergent space 30d. .

  In the present embodiment, a plurality of (specifically, two as shown in FIG. 5) columnar spaces are provided in the upper body 32, and circular thin-plate diaphragms 37a are respectively provided in the spaces. Although the two driving means 37 are fixed, the number of the driving means 37 is not limited to this. In addition, when providing the drive means 37 in multiple places, it is desirable to arrange | position at equal angle intervals with respect to a central axis, respectively.

  Further, a diaphragm formed of an annular thin plate is fixed in a space formed in an annular shape when viewed from the central axis direction, and the diaphragm and the refrigerant passage forming member 35 are connected by a plurality of operating rods. It is good also as a structure. Other configurations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, also in the ejector 13 of this embodiment, the refrigerant in the swirl space 30b and the refrigerant in the gas-liquid separation space 30h are configured to be able to exchange heat, and furthermore, the refrigerant flowing through the refrigerant inflow passage 30a and the gas-liquid separation space 30h. Since the internal refrigerant is configured to be able to exchange heat, the energy conversion efficiency in the nozzle passage can be sufficiently improved regardless of the state of the refrigerant flowing into the swirling space 30b, as in the first embodiment.

  Further, according to the ejector 13 of the present embodiment, the driving means 37 is disposed inside the upper body 32 and is formed at least above the upper body 32 with respect to the temperature sensitive medium enclosed in the enclosed space 37b. The temperature of the refrigerant in the inflow space 30e is set to voltage. Thereby, the space which the upper body 32 occupies can be utilized effectively, and the enlargement of the physique as the ejector 13 whole can be suppressed further.

  Further, since the enclosed space 37b is disposed at a position surrounded by the inflow space 30e and the suction passage 30f, the temperature of the refrigerant flowing out of the evaporator 14 can be transmitted to the temperature sensitive medium without being affected by the outside air temperature. The pressure in the enclosed space 37b can be changed. That is, the pressure in the enclosed space 37b can be accurately changed according to the temperature of the refrigerant flowing out of the evaporator 14.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above embodiment, the swirl space 30b is formed on the inner peripheral side of the cylindrical member 33c constituting the swirl space forming member, and the gas-liquid separation space 30h is formed on the outer peripheral side of the cylindrical member 33c. The example in which heat exchange between the refrigerant in the swirl space 30b and the refrigerant in the gas-liquid separation space 30h has been described, but the arrangement relationship between the swirl space 30b and the gas-liquid separation space 30h is not limited thereto. For example, the gas-liquid separation space 30h may be disposed on the lower side of the swirl space 30b so that the refrigerant in the swirl space 30b exchanges heat with the refrigerant in the gas-liquid separation space 30h.

  Moreover, in the above-mentioned embodiment, the example which enabled the heat exchange with the refrigerant | coolant which distribute | circulates the refrigerant | coolant in the revolving space 30b and the refrigerant | coolant inflow passage 30a by forming the refrigerant | coolant inflow passage 30a in the downward side of the revolving space 30b. Although demonstrated, the arrangement | positioning relationship of the turning space 30b and the gas-liquid separation space 30h is not limited to this. For example, the refrigerant inflow passage 30a may be arranged in a spiral shape on the outer peripheral side of the swirling space 30b, and heat may be exchanged between the refrigerant in the swirling space 30b and the refrigerant flowing through the refrigerant inflow passage 30a.

  (2) In the above embodiment, the mixed refrigerant of the injected refrigerant and the suction refrigerant has an annular shape that flows from the central axis side to the outer peripheral side, but the diffuser space 30g is not limited to this. For example, if heat exchange between the refrigerant in the swirl space 30b and the refrigerant in the gas-liquid separation space 30h is possible, the diffuser space 30g may be formed in a shape extending in the axial direction of the nozzle as in the prior art. Good.

  (3) In the above-described second embodiment, as the driving means 37 for displacing the tapered tip portion 35a, the enclosed space 37b in which the temperature sensitive medium that changes in pressure with temperature change is enclosed, and the temperature sensitive medium in the enclosed space 37b Although the example which employ | adopted what was comprised with the diaphragm 37a displaced according to the pressure of this was demonstrated, a drive means is not limited to this.

  For example, a thermowax that changes in volume depending on temperature may be employed as the temperature-sensitive medium, or a structure having a shape memory alloy elastic member as the driving means may be employed. Further, as in the second embodiment, a drive unit that displaces the refrigerant passage forming member 35 by an electric motor may be employed.

  (4) In the above-described embodiment, details of the liquid-phase refrigerant outlet 31c of the ejector 13 and the liquid-phase refrigerant outlet of the gas-liquid separator 60 are not described. Means (for example, a side fixed throttle made of an orifice or a capillary tube) may be arranged.

  (5) In the above-described embodiment, the example in which the ejector refrigeration cycle 10 including the ejector 13 of the present invention is applied to a vehicle air conditioner has been described. However, the application of the ejector refrigeration cycle 10 including the ejector 13 of the present invention is described. Is not limited to this. For example, the present invention may be applied to a stationary air conditioner, a cold storage container, a cooling / heating device for a vending machine, and the like.

  (6) In the above-described embodiment, the example in which the outer periphery side of the upper body 32, the middle body 33, and the lower body 34 is fixed in the housing body 31 in order from the upper side by press-fitting is described. The fixing of the middle body 33 and the lower body 34 is not limited to this. When fixing by other means, it is desirable to interpose a seal member such as an O-ring between the inner peripheral side of the housing body 31 and the outer peripheral side of the upper body 32, the middle body 33, and the lower body 34.

  (7) In the above-described embodiment, an example in which a subcool type heat exchanger is employed as the radiator 12 has been described. However, an ordinary radiator including only the condensing unit 12a may be employed. Moreover, although the above-mentioned embodiment demonstrated the example which formed the structural member of the body 30 of the ejector 13 with the metal, a material will not be limited if the function of each structural member can be exhibited. Therefore, you may form these structural members with resin.

  (8) In the above-described embodiment, the example in which the refrigerant passage forming member 35 is formed in a shape in which the bottom surfaces of two conical members are bonded to each other has been described. It is not limited to a member formed in a conical shape, but is formed in a shape close to a cone, a shape including a conical shape in part, or a combination of a conical shape, a cylindrical shape, a truncated cone shape, etc. The meaning is included.

  Specifically, the shape in which the axial cross-sectional shape is not limited to an isosceles triangle, the two sides sandwiching the apex are convex on the inner peripheral side, and the two sides sandwiching the apex are convex on the outer peripheral side. You may employ | adopt what a shape and also cross-sectional shape become a semicircle shape.

10 Ejector Refrigeration Cycle 13 Ejector 30 Body 30b Swivel Space 30c Tapered Space (Nozzle Path)
30d Suehiro space (nozzle passage)
30f Suction passage 30h Gas-liquid separation space 33b Upper disk-shaped member (nozzle passage forming member)
33c Cylindrical member (swirl space forming member)

Claims (7)

An ejector applied to a vapor compression refrigeration cycle apparatus (10),
A swirl space forming member (33c) that forms a swirl space (30b) for swirling the refrigerant;
A nozzle passage forming member (33b) that forms nozzle passages (30c, 30d) that function as nozzles for depressurizing and injecting the refrigerant flowing out of the swirling space (30b);
A refrigerant suction port (31b) that sucks the refrigerant by a suction action of the high-speed jet refrigerant jetted from the nozzle passages (30c, 30d), the jetted refrigerant, and a suction refrigerant sucked from the refrigerant suction port (31b) A body (30) in which a pressurized space (30g) for converting the velocity energy of the mixed refrigerant into pressure energy and a gas-liquid separation space (30h) for separating the gas-liquid of the refrigerant flowing out from the pressurized space (30g) are formed. And
An ejector, wherein the refrigerant in the swirl space (30b) and the refrigerant in the gas-liquid separation space (30h) are configured to be able to exchange heat. The swirl space forming member (33c) is formed in a cylindrical shape,
The swirling space (30b) is formed on the inner peripheral side of the swirling space forming member (33c),
The ejector according to claim 1, wherein the gas-liquid separation space (30h) is formed on an outer peripheral side of the swirl space forming member (33c). An inflow passage forming member (34) that forms a refrigerant inflow passage (30a) that guides the refrigerant that has flowed out of the radiator (12) that dissipates high-pressure refrigerant in the refrigeration cycle device (10) into the swirling space (30b). Prepared,
The ejector according to claim 1 or 2, wherein heat exchange is possible between the refrigerant flowing through the refrigerant inflow passage (30a) and the refrigerant in the gas-liquid separation space (30h).   The ejector according to claim 3, wherein the refrigerant inflow passage (30a) is formed on the lower side in the vertical direction of the gas-liquid separation space (30h). A refrigerant passage forming member (35) for guiding the flow direction of the jet refrigerant from the central axis of the nozzle passage forming member (33b) to the outer peripheral side;
5. The pressurization space (30 g) is formed in a shape in which the mixed refrigerant flows from the center axis side to the outer periphery side of the nozzle passage forming member (33 b). Ejector as described in. An area adjusting member (35a) for changing the refrigerant passage area of the minimum passage area portion (33d) formed by the nozzle passage forming member (33b) and having the smallest refrigerant passage area;
The ejector according to any one of claims 1 to 5, further comprising driving means (36, 37) for displacing the area adjusting member (35a). The drive means (37) includes a sealed space (37b) in which a temperature-sensitive medium whose pressure changes according to a temperature change is sealed, and a pressure response that is displaced according to the pressure of the temperature-sensitive medium in the sealed space (37b). Comprising a member (37a),
The body (30) has an inflow space (30e) into which the suction refrigerant flows,
The ejector according to claim 6, wherein the temperature-sensitive medium changes in pressure when at least the temperature of the refrigerant in the inflow space (30e) is transmitted.

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