JP6064862B2 - Ejector - Google Patents

Description

  The present invention relates to an ejector that sucks a fluid by reducing the pressure of the fluid and sucking a jet fluid ejected at a high speed.

  Conventionally, an ejector is known as a decompression device applied to a vapor compression refrigeration cycle apparatus. This type of ejector has a nozzle part that decompresses the refrigerant, sucks the gas-phase refrigerant that has flowed out of the evaporator by the suction action of the jetted refrigerant jetted from the nozzle part, and injects it at the booster (diffuser part) The pressure can be increased by mixing the refrigerant and the suction refrigerant.

  Therefore, in a refrigeration cycle apparatus including an ejector as a decompression apparatus (hereinafter referred to as an ejector-type refrigeration cycle), the power consumption of the compressor can be reduced by utilizing the refrigerant pressure-increasing action in the pressure-increasing section 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 apparatus.

  Furthermore, Patent Document 1 discloses an ejector that is applied to an ejector-type refrigeration cycle and that has a nozzle portion that depressurizes the refrigerant in two stages. More specifically, in the ejector disclosed in Patent Document 1, the refrigerant in the high-pressure liquid phase is decompressed by the first nozzle until the gas-liquid two-phase state is obtained, and the refrigerant in the gas-liquid two-phase state is supplied to the second nozzle. Inflow.

  Thereby, in the ejector of patent document 1, the boiling of the refrigerant | coolant in a 2nd nozzle is accelerated | stimulated, the nozzle efficiency as the whole nozzle part is improved, and it is going to aim at the further improvement of COP as the whole ejector type refrigeration cycle. Yes.

  Moreover, in a general ejector, the diffuser part (pressure | voltage rise part) is arrange | positioned coaxially on the extension line | wire of the axial direction of a nozzle part. Further, Patent Document 2 describes that the ejector efficiency can be improved by relatively reducing the spread angle of the diffuser portion arranged in this way.

  The nozzle efficiency is the energy conversion efficiency when the pressure energy of the refrigerant is converted into kinetic energy in the nozzle portion, and the ejector efficiency is the energy conversion efficiency of the entire ejector.

Japanese Patent No. 3331604 JP 2003-14318 A

  However, in the ejector of Patent Document 1, for example, when the thermal load of the ejector-type refrigeration cycle becomes low, and the pressure difference (high-low pressure difference) between the pressure of the high-pressure side refrigerant and the pressure of the low-pressure side refrigerant in the cycle is reduced, There is a case where the first nozzle is depressurized by a high-low pressure difference, and the refrigerant is hardly depressurized by the second nozzle.

  In such a case, the nozzle efficiency improvement effect due to the flow of the gas-liquid two-phase refrigerant into the second nozzle cannot be obtained, and the refrigerant cannot be sufficiently boosted in the diffuser section.

  On the other hand, by applying the diffuser portion having a relatively small spread angle disclosed in Patent Literature 2 to the ejector of Patent Literature 1 and improving the ejector efficiency, the diffuser portion is also at a low load of the ejector refrigeration cycle. A means for sufficiently increasing the pressure of the refrigerant can be considered.

  However, when such a diffuser portion is applied, the length of the nozzle portion in the axial direction as a whole becomes longer, so that the size of the ejector becomes unnecessarily large at the normal load of the ejector refrigeration cycle. Is a problem.

Therefore, the present inventors previously described Japanese Patent Application No. 2012-184950 (hereinafter referred to as a prior application example).
An ejector applied to an ejector refrigeration cycle,
A swirling space for swirling the refrigerant flowing out of the radiator, a decompression space for depressurizing the refrigerant flowing out of the swirling space, and a suction passage for sucking the refrigerant flowing out of the evaporator in communication with the refrigerant flow downstream side of the depressurizing space And a body part in which a pressure increasing space is formed to increase the pressure by mixing the injected refrigerant injected from the pressure reducing space and the suction refrigerant sucked from the suction passage;
A passage forming member that is at least partially disposed in the decompression space and in the pressurization space and is formed in a conical shape whose cross-sectional area expands with distance from the decompression space;
Drive means for displacing the passage forming member,
Nozzle passage functioning as a nozzle in which a refrigerant passage formed between an inner peripheral surface of a portion of the body forming a decompression space and an outer peripheral surface of the passage forming member decompresses and injects the refrigerant flowing out of the swirling space. Form the
A refrigerant passage formed between an inner peripheral surface of a part of the body that forms a pressure increasing space and an outer peripheral surface of the passage forming member serves as a diffuser passage that functions as a diffuser that increases the pressure by mixing the injected refrigerant and the suction refrigerant. Forming,
Furthermore, a gas-liquid separation space is formed in the body, which is formed by a space of a rotating body arranged coaxially with the passage forming member, and separates the gas-liquid refrigerant flowing out of the diffuser passage by the action of centrifugal force. Proposed ejector.

  In the ejector of this prior application example, the refrigerant is swirled in the swirling space, so that the refrigerant pressure on the swirling center side in the swirling space becomes the pressure that becomes the saturated liquid phase refrigerant, or the refrigerant boils under reduced pressure (causes cavitation). Can be reduced to pressure. As a result, the gas phase refrigerant is present in the swirl space in the vicinity of the swirl center line so that the gas phase refrigerant is present more on the inner circumference side than the outer circumference side of the swirl center axis, and the liquid single phase is around the gas phase. It can be.

  Then, the refrigerant in the two-phase separation state flows into the nozzle passage, and the boiling is promoted by wall surface boiling and interface boiling, so that the gas phase and the liquid phase are homogeneously mixed in the vicinity of the minimum flow path area of the nozzle passage. It becomes a gas-liquid mixed state. Further, the refrigerant in the gas-liquid mixed state in the vicinity of the minimum flow path area of the nozzle passage is blocked (choking), and the refrigerant is accelerated until the flow rate of the refrigerant in the gas-liquid mixed state becomes a two-phase sound speed.

  Thus, the refrigerant accelerated to the two-phase sonic velocity becomes an ideal two-phase spray flow that is homogeneously mixed downstream from the minimum flow path area of the nozzle passage, and can further increase the flow velocity. it can. As a result, it is possible to improve the energy conversion efficiency (corresponding to the nozzle efficiency) when converting the pressure energy of the refrigerant into the velocity energy in the nozzle passage.

  Further, in the ejector of the prior application example, when the passage forming member is formed in a conical shape whose cross-sectional area increases as the passage forming member moves away from the decompression space, when viewed from the axial direction of the passage forming member, the diffuser The axial vertical cross-sectional shape of the passage is formed in an annular shape. And while making the shape of a diffuser channel | path into the shape which spreads along the outer periphery of a channel | path formation member as it leaves | separates from the space for pressure reduction, the refrigerant | coolant which distribute | circulates a diffuser channel | path is swirled.

  Thereby, since the refrigerant | coolant flow path for raising a refrigerant | coolant in a diffuser channel | path can be formed in a spiral, it can suppress that the axial direction dimension of a diffuser channel | path expands. As a result, an increase in the size of the entire ejector can be suppressed. That is, according to the ejector of the prior application example, high nozzle efficiency can be exhibited without causing an increase in the size of the physique and regardless of the load fluctuation of the refrigeration cycle.

  Furthermore, since the ejector of the prior application example is provided with driving means for displacing the passage forming member, the refrigerant passage areas (passage cross-sectional areas) of the nozzle passage and the diffuser passage are changed according to the load fluctuation of the ejector refrigeration cycle. be able to. Therefore, the ejector can be operated appropriately by appropriately changing the passage sectional area of the minimum passage area portion of the nozzle passage in accordance with the load fluctuation of the ejector refrigeration cycle.

  Furthermore, in the ejector of the prior application, the gas-liquid refrigerant flowing out of the diffuser passage is separated by the action of centrifugal force in the gas-liquid separation space formed inside the body. In contrast to the case where the separation means is disposed, the gas-liquid refrigerant can be efficiently separated in the gas-liquid separation space, and the volume of the gas-liquid separation space can be effectively reduced.

  However, in the configuration in which the refrigerant passage areas of the nozzle passage and the diffuser passage are changed as in the ejector of the prior application, for example, the flow velocity of the refrigerant flowing into the diffuser passage is changed by changing the refrigerant passage area of the nozzle passage and the diffuser passage. When it is lowered, the speed in the swirling direction of the refrigerant flowing through the diffuser passage may be lowered.

  Such a decrease in the speed in the swirling direction of the refrigerant flowing through the diffuser passage shortens the spiral refrigerant flow path for increasing the pressure of the refrigerant in the diffuser passage, and sufficiently increases the pressure of the refrigerant in the diffuser passage. It becomes the cause that becomes impossible. Furthermore, since the centrifugal force acting on the refrigerant flowing out from the diffuser passage is reduced, the gas-liquid separation performance of the gas-liquid separation space is deteriorated.

  In view of the above points, an object of the present invention is to provide an ejector capable of exhibiting high nozzle efficiency and high boosting performance irrespective of load fluctuations of the refrigeration cycle without causing an increase in size of the physique.

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 (30a) for swirling the refrigerant flowing in from the refrigerant inlet (31a), a decompression space (30b) for decompressing the refrigerant flowing out of the swirling space (30a), and a refrigerant flow downstream of the decompression space (30b). A suction passage (13b) that communicates and sucks refrigerant from the outside, and a pressurization space (30e) that mixes the refrigerant injected from the decompression space (30b) and the suction refrigerant sucked from the suction passage (13b). ) Is formed, and at least a part of the body (30) is disposed in the decompression space (30b) and the boosting space (30e), and the body (30) is disconnected as the distance from the decompression space (30b) increases. A passage forming member (35) formed in a conical shape with an increased area, and a drive means (37) for displacing the passage forming member (35),
The refrigerant passage formed between the inner peripheral surface of the part forming the decompression space (30b) in the body (30) and the outer peripheral surface of the passage forming member (35) is a refrigerant that has flowed out of the swirling space (30a). Is a nozzle passage (13a) that functions as a nozzle for depressurizing and injecting, between the inner peripheral surface of the body (30) forming the pressurizing space (30e) and the outer peripheral surface of the passage forming member (35) The refrigerant passage formed between them is a diffuser passage (13c) that functions as a diffuser for mixing and increasing the pressure of the injected refrigerant and the suction refrigerant, and the diffuser passage (13c) is perpendicular to the axial direction of the passage forming member (35). The cross-sectional shape in a simple cross section is formed in an annular shape,
Furthermore, a connecting member (38) for transmitting a driving force from the driving means (37) to the passage forming member (35) is provided, and the connecting member (38) has a plate-like portion (38b) formed in a plate shape. The plate surface of the plate-like portion (38b) is inclined so as to guide the flow of the refrigerant in the direction around the axis of the passage forming member (35).

  According to this, the energy conversion efficiency (equivalent to nozzle efficiency) in the nozzle passage (13a) can be improved by swirling the refrigerant in the swirling space (30a) as in the prior application example. Further, by rotating the refrigerant flowing through the diffuser passage (13c), it is possible to suppress an increase in the axial dimension of the diffuser passage (13c) as in the prior application example. Furthermore, since the drive means (37) is provided, the ejector can be appropriately operated as in the prior application example.

  In addition, according to the present invention, the plate surface of the plate-like portion (38b) of the connecting member (38) guides the flow of the refrigerant in the direction around the axis of the passage forming member (35). Therefore, the swirling flow of the refrigerant flowing through the diffuser passage (13c) can be promoted. Therefore, for example, even if the refrigerant passage area of the diffuser passage (13c) is changed to reduce the flow velocity of the refrigerant flowing into the diffuser passage (13c), the speed in the swirling direction of the refrigerant flowing through the diffuser passage (13c) decreases. Can be suppressed.

  Thereby, it can suppress that the spiral refrigerant flow path for pressurizing a refrigerant | coolant in a diffuser channel | path (13c) becomes short, and can suppress the fall of the pressure | voltage rise amount of the refrigerant | coolant in a diffuser channel | path (13c). Furthermore, since the swirling flow of the refrigerant flowing through the diffuser passage (13c) can be promoted using the connecting member (38), it is not necessary to provide a dedicated member for promoting the swirling flow.

  As a result, high energy conversion efficiency (equivalent to the nozzle efficiency of the prior art) can be exhibited in the nozzle passage (13a) regardless of the load fluctuation of the refrigeration cycle device (10) without causing an increase in the size of the physique, It is possible to provide an ejector capable of exhibiting high pressure increasing performance in the diffuser passage (13c).

  Furthermore, as in the invention described in claim 2, in the ejector described in claim 1, the connecting member (38) is rotatable about a rotation axis extending parallel to the axial direction of the passage forming member (35). The cross section includes the plate-like portion (38b) in the axially vertical cross section of the passage forming member (35) and extends from the axial center of the passage forming member (35) toward the rotation center of the connecting member (38). Among the plate surface of the line segment (L1) and the plate-like portion (38b), the refrigerant flow most downstream end from the refrigerant flow most upstream end portion (Q1) on the plate surface arranged on the axial center side of the passage forming member (35). When the angle formed between the line segment (L2) extending toward the portion (Q2) is the inclination angle θ, the drive means (37) is inclined as the passage forming member (35) is displaced. The angle θ may be changed.

  According to this, since the inclination angle θ can be appropriately changed according to the load fluctuation of the refrigeration cycle apparatus (10), the swirling flow of the refrigerant flowing through the diffuser passage (13c) is effectively promoted. Can do. Accordingly, it is possible to provide an ejector capable of exhibiting high pressure increasing performance in the diffuser passage (13c) regardless of the load fluctuation of the refrigeration cycle apparatus (10).

The invention according to claim 3 is an ejector applied to the vapor compression refrigeration cycle apparatus (10),
A swirling space (30a) for swirling the refrigerant flowing in from the refrigerant inlet (31a), a decompression space (30b) for decompressing the refrigerant flowing out of the swirling space (30a), and a refrigerant flow downstream of the decompression space (30b). A suction passage (13b) that communicates and sucks refrigerant from the outside, and a pressurization space (30e) that mixes the refrigerant injected from the decompression space (30b) and the suction refrigerant sucked from the suction passage (13b). ) Is formed, and at least a part of the body (30) is disposed in the decompression space (30b) and the boosting space (30e), and the body (30) is disconnected as the distance from the decompression space (30b) increases. A passage forming member (35) formed in a conical shape with an increased area, and a drive means (37) for displacing the passage forming member (35),
The refrigerant passage formed between the inner peripheral surface of the part forming the decompression space (30b) in the body (30) and the outer peripheral surface of the passage forming member (35) is a refrigerant that has flowed out of the swirling space (30a). Is a nozzle passage (13a) that functions as a nozzle for depressurizing and injecting, between the inner peripheral surface of the body (30) forming the pressurizing space (30e) and the outer peripheral surface of the passage forming member (35) The refrigerant passage formed between them is a diffuser passage (13c) that functions as a diffuser for mixing and increasing the pressure of the injected refrigerant and the suction refrigerant, and the diffuser passage (13c) is perpendicular to the axial direction of the passage forming member (35). The cross-sectional shape in a simple cross section is formed in an annular shape,
Furthermore, a turning promotion member (38) that promotes the turning flow of the refrigerant flowing through the diffuser passage (13c) is provided, and the turning promotion member (38) guides the flow of the refrigerant in the direction around the axis of the passage forming member (35). It has a plate-like part (38b) and is configured to be rotatable around a rotation axis extending parallel to the axial direction of the passage forming member (35).
A line segment extending from the axial center of the passage forming member (35) toward the rotational center of the turning promotion member (38) in a cross section including the plate-like portion (38b) in the vertical cross section in the axial direction of the passage forming member (35). (L1) and the refrigerant flow most downstream end (Q1) from the refrigerant flow most upstream end (Q1) on the plate surface arranged on the axial center side of the passage forming member (35) among the plate surfaces of the plate-like portion (38b) ( When the angle formed with the line segment (L2) extending toward Q2) is defined as the inclination angle θ, the inclination angle θ as the drive means (37) displaces the passage forming member (35). Changes.

  According to this, since the turning promotion member (38) configured to include the plate-like portion (38b) for guiding the refrigerant flow in the direction around the axis of the passage forming member (35) is provided, the diffuser passage (13c) is provided. ), The swirling flow of the refrigerant that circulates can be promoted. Furthermore, since the inclination angle θ can be appropriately changed according to the load fluctuation of the refrigeration cycle apparatus (10), the swirling flow of the refrigerant flowing through the diffuser passage (13c) can be effectively promoted.

  Therefore, as in the first aspect of the invention, high energy conversion efficiency (nozzle of the prior art) is achieved in the nozzle passage (13a) regardless of the load fluctuation of the refrigeration cycle apparatus (10) without increasing the size of the physique. It is possible to provide an ejector capable of exhibiting a high boosting performance in the diffuser passage (13c).

  Further, the refrigerant flowing through the diffuser passage (13c) is swirling in the same direction as the refrigerant swirling in the swirling space (30a), so that a spiral shape for boosting the refrigerant in the diffuser passage (13c) is formed. It is possible to effectively suppress the refrigerant flow path from being shortened, and to effectively suppress a decrease in the pressure increase amount of the refrigerant in the diffuser passage (13c).

  In the above claims, the passage forming member (35) is not limited to one that is strictly formed from a shape whose cross-sectional area expands as it is separated from the decompression space (30b). The shape of the diffuser passage (13c) is expanded to the outside as the distance from the decompression space (30b) is increased. Including what can be.

  Further, “conically formed” is not limited to the meaning that the passage forming member (35) is formed in a complete conical shape, and includes a shape close to a cone or a portion of the cone. It also includes the meaning of being formed. Specifically, the shape in which the axial cross-sectional shape is not limited to an isosceles triangle, the shape in which the two sides sandwiching the apex are convex on the inner peripheral side, the shape in which the two sides sandwiching the apex are convex on the outer peripheral side, Furthermore, it is meant to include those having a semicircular cross section.

  Further, the above-mentioned “promoting the swirling flow of the refrigerant flowing through the diffuser passage (13c)” means only promoting the swirling flow of the refrigerant from the inlet side to the outlet side of the diffuser passage (13c). However, at least a part of the refrigerant flowing through the diffuser passage (13c) (for example, refrigerant on the inlet side of the diffuser passage (13c), refrigerant on the outlet side of the diffuser passage (13c), diffuser passage (13c) This also includes promoting the swirling flow of the refrigerant just before flowing out of the

  In addition, 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 an axial sectional view of the ejector of the first embodiment. It is typical sectional drawing for demonstrating the function of each refrigerant path of the ejector of 1st Embodiment. It is an enlarged view of the operating rod periphery of the ejector of 1st Embodiment. It is VV 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 sectional drawing corresponding to FIG. 5 in 2nd Embodiment. It is sectional drawing corresponding to FIG. 5 in 3rd Embodiment. It is sectional drawing corresponding to FIG. 5 in 4th Embodiment. It is sectional drawing corresponding to FIG. 5 in 5th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the diffuser channel | path of other embodiment.

(First embodiment)
1st Embodiment of this invention is described using FIGS. As shown in FIG. 1, the ejector 13 of this embodiment is applied to a vapor compression 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.

  First, in the ejector refrigeration cycle 10, the compressor 11 increases the pressure until the refrigerant is sucked into a high-pressure refrigerant and is discharged. 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 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 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 ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as a refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. . Of course, an HFO refrigerant (specifically, R1234yf) or the like may be adopted as the refrigerant. 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.

  Further, 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 and flowing it to the downstream side, and is described later by the suction action of the refrigerant flow injected at a high speed. It functions as a refrigerant circulating means (refrigerant transporting means) that sucks (transports) and circulates the refrigerant flowing out of the evaporator 14 that circulates. 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. FIG. 3 is a schematic cross-sectional view for explaining the function of each refrigerant passage of the ejector 13, and the same parts as those in FIG. 2 are denoted by the same reference numerals.

  First, the ejector 13 of this embodiment is provided with the body 30 comprised by combining a some structural member, as shown in FIG. Specifically, the body 30 includes a housing body 31 that is formed of a prismatic or columnar metal and forms the outer shell of the ejector 13, and a nozzle body 32 and a middle body 33 are provided inside the housing body 31. The lower body 34 and the like are fixed.

  The housing body 31 includes a refrigerant inlet 31 a that allows the refrigerant flowing out of the radiator 12 to flow into the interior, a refrigerant suction port 31 b that sucks the refrigerant flowing out of the evaporator 14, and a gas-liquid separation space formed inside the body 30. The liquid-phase refrigerant outlet 31c that causes the liquid-phase refrigerant separated in 30f to flow out to the refrigerant inlet side of the evaporator 14 and the gas-phase refrigerant separated in the gas-liquid separation space 30f flow out to the suction side of the compressor 11. The gas-phase refrigerant outlet 31d to be made is formed.

  The nozzle body 32 is formed of a substantially conical metal member that tapers in the refrigerant flow direction, and is press-fitted into the housing body 31 such that the axial direction is parallel to the vertical direction (vertical direction in FIG. 2). It is fixed by means. Between the upper side of the nozzle body 32 and the housing body 31, a swirling space 30a for swirling the refrigerant flowing from the refrigerant inlet 31a is formed.

  The swirling space 30a is formed in a rotating body shape, and the central axis shown by the one-dot chain line in FIG. 2 extends in the vertical direction. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (central axis) on the same plane. More specifically, the swirl space 30a of the present embodiment is formed in a substantially cylindrical shape. Of course, you may form in the shape etc. which combined the cone or the truncated cone, and the cylinder.

  Furthermore, the refrigerant inflow passage 31e that connects the refrigerant inlet 31a and the swirling space 30a extends in the tangential direction of the inner wall surface of the swirling space 30a when viewed from the central axis direction of the swirling space 30a. Thereby, the refrigerant that has flowed into the swirl space 30a from the refrigerant inflow passage 31e flows along the inner wall surface of the swirl space 30a and swirls in the swirl space 30a.

  The refrigerant inflow passage 31e does not need to be formed so as to completely coincide with the tangential direction of the swirl space 30a when viewed from the central axis direction of the swirl space 30a, and at least in the tangential direction of the swirl space 30a. As long as a component is included, it may be formed including a component in another direction (for example, a component in the axial direction of the swirling space 30a).

  Here, since centrifugal force acts on the refrigerant swirling in the swirling space 30a, the refrigerant pressure on the central axis side is lower than the refrigerant pressure on the outer peripheral side in the swirling space 30a. 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 30a is set to the pressure that becomes the saturated liquid phase refrigerant, or the refrigerant boils under reduced pressure (causes cavitation). The pressure is lowered to the pressure.

  Such adjustment of the refrigerant pressure on the central axis side in the swirling space 30a can be realized by adjusting the swirling flow velocity of the refrigerant swirling in the swirling space 30a. Further, the swirl flow rate can be adjusted by adjusting the area ratio between the passage sectional area of the refrigerant inflow passage 31e and the vertical sectional area in the axial direction of the swirling space 30a, for example. Note that the swirling flow velocity in the present embodiment means the flow velocity in the swirling direction of the refrigerant in the vicinity of the outermost peripheral portion of the swirling space 30a.

  Further, in the nozzle body 32, a decompression space 30b is formed in which the refrigerant that has flowed out of the swirl space 30a is decompressed and flows out downstream. The decompression space 30b is formed in a rotating body shape in which a cylindrical space and a frustoconical space that continuously spreads from the lower side of the cylindrical space and gradually expands in the refrigerant flow direction. The central axis of the working space 30b is arranged coaxially with the central axis of the swirling space 30a.

  Further, inside the decompression space 30b, there is formed a minimum passage area portion 30m having the smallest refrigerant passage area in the decompression space 30b, and a passage forming member 35 that changes the passage area of the minimum passage area portion 30m. Has been placed. The passage forming member 35 is formed in a substantially conical shape that gradually expands toward the downstream side of the refrigerant flow, and the central axis thereof is arranged coaxially with the central axis of the decompression space 30b. In other words, the passage forming member 35 is formed in a conical shape whose cross-sectional area increases as the distance from the decompression space 30b increases.

  As the refrigerant passage formed between the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle body 32 and the outer peripheral surface on the upper side of the passage forming member 35, as shown in FIG. The tip 131 is formed on the upstream side of the refrigerant flow from the portion 30m and gradually decreases in the refrigerant passage area until reaching the minimum passage area 30m, and the refrigerant passage is formed on the downstream side of the refrigerant flow from the minimum passage area 30m. A divergent portion 132 whose area gradually increases is formed.

  In the divergent section 132, the decompression space 30b and the passage forming member 35 are overlapped (overlapped) when viewed from the radial direction, so that the shape of the axial cross section of the refrigerant passage is annular (from a circular shape to a coaxial shape). (A donut shape excluding a small-diameter circular shape disposed on the surface). Furthermore, since the spread angle of the passage forming member 35 of the present embodiment is smaller than the spread angle of the frustoconical space of the decompression space 30b, the refrigerant passage area in the divergent portion 132 is directed toward the downstream side of the refrigerant flow. Gradually expanding.

  In the present embodiment, a refrigerant passage formed between the inner peripheral surface of the pressure reducing space 30b and the outer peripheral surface on the top side of the passage forming member 35 is formed as a nozzle passage 13a functioning as a nozzle by this passage shape, and the refrigerant is decompressed. At the same time, the flow rate of the refrigerant is increased so as to be the sonic velocity and injected. Further, since the refrigerant flowing into the nozzle passage 13a swirls in the swirling space 30a, the refrigerant flowing through the nozzle passage 13a and the jet refrigerant injected from the nozzle passage 13a are the same as the refrigerant swirling in the swirling space 30a. It has a velocity component in the direction of turning in the direction.

  Next, as shown in FIG. 2, the middle body 33 is provided with a rotating body-shaped through hole penetrating the front and back at the center, and driving the passage forming member 35 to be displaced to the outer peripheral side of the through hole. It is formed of a metal disk-like member that accommodates the means 37. The central axis of the through hole of the middle body 33 is arranged coaxially with the central axes of the swirl space 30a and the decompression space 30b. The middle body 33 is fixed inside the housing body 31 and below the nozzle body 32 by means such as press fitting.

  Furthermore, an inflow space 30c is formed between the upper surface of the middle body 33 and the inner wall surface of the housing body 31 facing the middle body 33 for retaining the refrigerant flowing in from the refrigerant suction port 31b. In the present embodiment, since the tapered tip portion on the lower side of the nozzle body 32 is positioned inside the through hole of the middle body 33, the inflow space 30c has a cross section when viewed from the central axis direction of the swirl space 30a and the decompression space 30b. It is formed in an annular shape.

  The suction refrigerant inflow passage 30h that connects the refrigerant suction port 31b and the inflow space 30c extends in the tangential direction of the inner peripheral wall surface of the inflow space 30c when viewed from the central axis direction of the inflow space 30c. desirable. The reason is that the refrigerant flowing into the inflow space 30c from the refrigerant suction port 31b via the suction refrigerant inflow passage 30h is swirled in the same direction as the refrigerant in the swirling space 30a, and then flows into the pressurizing space 30e described later. This is because the swirling flow of the refrigerant can be promoted.

  Further, in the through hole of the middle body 33, the lower side of the nozzle body 32 is inserted, that is, in the range where the middle body 33 and the nozzle body 32 overlap when viewed from the radial direction perpendicular to the axis, the taper tip of the nozzle body 32 is formed. The refrigerant passage area gradually decreases in the refrigerant flow direction so as to conform to the outer peripheral shape.

  Thus, a suction passage 30d is formed between the inner peripheral surface of the through hole and the outer peripheral surface on the lower side of the nozzle body 32 so as to communicate the inflow space 30c and the downstream side of the refrigerant flow in the decompression space 30b. That is, in the present embodiment, the suction passage 13b through which the suction refrigerant flows from the outer peripheral side to the inner peripheral side of the central axis is formed by the inflow space 30c and the suction passage 30d. Furthermore, the cross section perpendicular to the central axis of the suction passage 13b is also formed in an annular cross section.

  Further, in the through hole of the middle body 33, a pressure increasing space 30e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction is formed on the downstream side of the refrigerant flow in the suction passage 30d. The pressurizing space 30e is a space where the refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the suction passage 30d are mixed.

  The lower side of the above-described passage forming member 35 is disposed in the boosting space 30e. Further, the expansion angle of the conical side surface of the passage forming member 35 in the pressure increasing space 30e is smaller than the expansion angle of the frustoconical space of the pressure increasing space 30e. The flow gradually expands toward the downstream side.

  In the present embodiment, the refrigerant passage formed between the inner peripheral surface of the middle body 33 forming the pressurizing space 30e and the outer peripheral surface on the lower side of the passage forming member 35 by expanding the refrigerant passage area in this manner. Is used as a diffuser passage 13c functioning as a diffuser, and the velocity energy of the mixed refrigerant of the injection refrigerant and the suction refrigerant is converted into pressure energy. That is, in the diffuser passage 13c, the injection refrigerant and the suction refrigerant are mixed and pressurized.

  Further, the cross-sectional shape perpendicular to the central axis of the diffuser passage 13c is also formed in an annular shape, and the refrigerant flowing through the diffuser passage 13c has the same direction as the refrigerant swirling in the swirling space 30a, as schematically shown in FIG. It has a speed component in the direction of turning.

  Next, the drive means 37 which is disposed inside the middle body 33 and displaces the passage forming member 35 will be described. 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. 2, the diaphragm 37a is fixed by means such as welding so as to partition a cylindrical space formed on the outer peripheral side of the middle body 33 into two upper and lower spaces.

  Of the two spaces partitioned by the diaphragm 37a, the space on the upper side (the inflow space 30c 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 30c and the enclosed space 37b.

  More specifically, as is apparent from FIGS. 2 and 3, the suction passage 13 b is disposed on the upper side of the middle body 33 of the present embodiment, and the diffuser is disposed in the range from the central axis side to the lower side of the middle body 33. A passage 13c is arranged. Accordingly, at least a part of the driving means 37 is disposed at a position sandwiched from above and below by the suction passage 13b and the diffuser passage 13c when viewed from the radial direction of the axis.

  The enclosing space 37b of the driving means 37 is a position that overlaps with the suction passage 13b and the diffuser passage 13c when viewed from the central axis direction of the swivel space 30a, the passage forming member 35, etc., and the suction passage 13b. And it arrange | positions in the position enclosed by the diffuser channel | path 13c. 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, as shown in the enlarged view of FIG. 4, the spherical surface of the upper end portion of the operating rod 38 is in contact with the center portion of the diaphragm 37a. The actuating bar 38 is formed of a substantially cylindrical member extending in the axial direction of the passage forming member 35, and is a connecting member that transmits driving force from the driving means 37 to the passage forming member 35. Further, the outer peripheral side of the lowermost portion of the passage forming member 35 is in contact with the spherical surface of the lower end portion of the operating rod 38.

  Thereby, the passage forming member 35 is displaced with the displacement of the diaphragm 37a, and the refrigerant passage area of the nozzle passage 13a (passage cross-sectional area in the minimum passage area portion 30m) and the refrigerant passage area in the diffuser passage 13c are adjusted. Further, a screw thread 38 a is formed on the outer peripheral side of the operating rod 38, and a screw groove that is screwed with the screw thread is formed in the middle body 33.

  Therefore, when the operating rod 38 is displaced in the axial direction (vertical direction) of the passage forming member 35 in accordance with the displacement of the diaphragm 37a, the operating rod 38 is displaced in the axial direction while rotating around the central axis of the screw. become. That is, the actuating bar 38 is configured to be rotatable about a rotation axis (screw center axis) extending parallel to the axial direction of the passage forming member 35.

  In the present embodiment, the upper and lower ends of the operating rod 38 are formed into spherical surfaces, thereby reducing the frictional resistance between the operating rod 38 and the diaphragm 37a and the frictional resistance between the operating rod 38 and the passage forming member 35. The actuating rod 38 can be easily rotated.

  Moreover, the plate-shaped part 38b formed in plate shape is formed in the site | part located in the exit side of the diffuser channel | path 13c among the action | operation bars 38. As shown in FIG. The plate-like portion 38b has a plate surface that extends in the axial direction of the passage forming member 35, and as shown in the VV cross-sectional view of FIG. It is formed in a wing shape curved along.

  That is, the plate surface of the plate-like portion 38 b is inclined so as to guide the refrigerant flow in the direction around the axis of the passage forming member 35, thereby promoting the swirling flow of the refrigerant flowing through the diffuser passage 13 c. That is, the actuating bar 38 of the present embodiment has not only a function as a connecting member but also a function as a turning promotion member that promotes the turning flow of the refrigerant flowing through the diffuser passage 13c.

  Further, as described above, the actuating bar 38 rotates with the displacement in the axial direction. As shown in the VV cross-sectional view of FIG. 5, this is a cross section including the plate-like portion 38 b in the axial vertical cross section of the passage forming member 35, and the operating rod 38 is moved from the axial center of the passage forming member 35. The line segment L1 extending toward the rotation center and the refrigerant flow most upstream end Q1 on the plate surface arranged on the axial center side of the passage forming member 35 among the plate surfaces of the plate-like portion 38b, the refrigerant flow most on the plate surface. When the angle formed with the line segment L2 extending toward the downstream end Q2 is defined as an inclination angle θ, it means that the inclination angle θ changes as the operating rod 38 is displaced in the axial direction. ing.

  In addition, as shown in FIG. 5, the inclination angle θ of the present embodiment is an angle that is positioned on the outer peripheral side and formed at an acute angle among the angles formed between the line segment L1 and the line segment L2. . That is, the inclination angle θ corresponds to the angle formed by the direction of the line segment L1 and the flow direction of the refrigerant flowing out from the diffuser passage 13c, and as the inclination angle θ increases, the refrigerant becomes a velocity component in the turning direction. It is led in the direction that the ratio of increases.

  Therefore, as the inclination angle θ, the rotation center of the actuating rod 38 (the connecting member, the turning promotion member) from the axial center of the passage forming member 35 in the cross section including the plate-like portion 38b in the axial vertical section of the passage forming member 35. Formed between the line segment L1 extending toward the line and the line segment extending in the tangential direction of the most downstream portion of the refrigerant flow on the plate surface disposed on the axial center side of the passage forming member 35 in the plate surface of the plate-like portion 38b. May be adopted.

  Further, as the inclination angle θ, the rotation center of the actuating bar 38 (the connecting member, the turning promotion member) from the axial center of the passage forming member 35 in the cross section including the plate-like portion 38b in the axial vertical cross section of the passage forming member 35. From the stagnation point of the refrigerant on the plate surface side arranged on the axial center side of the passage forming member 35 to the separation point of the refrigerant at the most downstream portion of the refrigerant flow, of the line segment L1 extending toward the plate and the plate surface of the plate-like portion 38b. You may employ | adopt the angle formed between the extended line segments.

  Further, as the inclination angle θ, the rotation center of the actuating bar 38 (the connecting member, the turning promotion member) from the axial center of the passage forming member 35 in the cross section including the plate-like portion 38b in the axial vertical cross section of the passage forming member 35. A line segment L1 that extends toward the plate end and a plate end of the plate-like portion 38b located on the axial center side of the passage forming member 35 toward a plate end on the outer peripheral side from a plate end on the inner peripheral side of the plate surface. You may employ | adopt the angle formed between the extended line segments.

  Further, the bottom surface of the passage forming member 35 receives a load of a coil spring 37e fixed to the lower body 34, as shown in FIG. The coil spring 37e applies a load that urges the passage forming member 35 toward the side of reducing the refrigerant passage area in the nozzle passage 13a and the diffuser passage 13c. By adjusting this load, the coil spring 37e The valve opening pressure can be changed.

  Therefore, in the driving means 37 of the present embodiment, for example, 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 internal pressure of the enclosed space 37b is reduced. When the differential pressure obtained by subtracting the pressure of the introduction space 37c from the diaphragm becomes smaller, the diaphragm 37a is displaced toward the enclosed space 37b.

  As a result, the passage forming member 35 that receives the load of the coil spring 37e is displaced in a direction (upward in the vertical direction) to reduce the refrigerant passage area in the nozzle passage 13a and the diffuser passage 13c. At this time, in this embodiment, as shown by the broken line in FIG. 5, the operating rod 38 rotates to the side that increases the inclination angle θ.

  On the other hand, 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. When the differential pressure increases, the diaphragm 37a is displaced toward the introduction space 37c.

  As a result, the passage forming member 35 that has received the displacement of the diaphragm 37a is displaced in a direction (vertical direction lower side) in which the refrigerant passage area in the nozzle passage 13a and the diffuser passage 13c is increased. At this time, in this embodiment, as shown by the solid line in FIG. 5, the operating rod 38 rotates to the side that decreases the inclination angle θ.

  That is, in the drive means 37 of the present embodiment, the diaphragm 37a and the coil spring 37e displace the passage forming member 35 according to the degree of superheat of the refrigerant flowing out of the evaporator 14, whereby the degree of superheat of the refrigerant on the outlet side of the evaporator 14 is increased in advance. The refrigerant passage area of the nozzle passage 13a (passage cross-sectional area in the minimum passage area portion 30m) and the refrigerant passage area in the diffuser passage 13c can be adjusted so as to approach the predetermined value.

  Furthermore, in the present embodiment, a plurality (columnar spaces) are provided on the outer peripheral side of the middle body 33, and the circular thin plate diaphragms 37a are fixed inside the spaces to constitute the two drive means 37. The number of the drive means 37 is not limited to this, and when the drive means 37 is provided at a plurality of locations, it is desirable that the drive means 37 be arranged at equiangular intervals with respect to the central axis.

  Alternatively, a diaphragm formed by an annular thin plate may be fixed in a space formed in an annular shape when viewed from the axial direction, and the diaphragm and the passage forming member 35 may be connected by a plurality of operating rods. Good.

  Next, the lower body 34 is formed of a cylindrical metal member, and is fixed in the housing body 31 by means such as screwing so as to close the bottom surface of the housing body 31. Between the upper side of the lower body 34 and the middle body 33, a gas-liquid separation space 30f that separates the gas-liquid refrigerant flowing out of the diffuser passage 13c is formed.

  The gas-liquid separation space 30f is formed as a substantially cylindrical rotary body-shaped space, and the central axis of the gas-liquid separation space 30f is also arranged coaxially with the central axes of the swirl space 30a, the decompression space 30b, and the like. Has been.

  As described above, in the diffuser passage 13c, the refrigerant flows while swirling along the refrigerant passage having an annular cross section. Therefore, the refrigerant flowing from the diffuser passage 13c into the gas-liquid separation space 30f also has a velocity component in the swirling direction. doing. Accordingly, the gas-liquid refrigerant is separated by centrifugal force in the gas-liquid separation space 30f. Further, the internal volume of the gas-liquid separation space 30f is such that even if a load fluctuation occurs in the cycle and the refrigerant circulation flow rate circulating in the cycle fluctuates, the surplus refrigerant cannot be substantially accumulated. .

  At the center of the lower body 34, a cylindrical pipe 34a is provided coaxially with the gas-liquid separation space 30f and extending upward. The liquid refrigerant separated in the gas-liquid separation space 30f temporarily stays on the outer peripheral side of the pipe 34a and flows out from the liquid refrigerant outlet 31c. A gas-phase refrigerant outflow passage 34b that guides the gas-phase refrigerant separated in the gas-liquid separation space 30f to the gas-phase refrigerant outlet 31d of the housing body 31 is formed inside the pipe 34a.

  Further, the above-described coil spring 37e is fixed to the upper end portion of the pipe 34a. The coil spring 37e also functions as a vibration buffer member that attenuates the vibration of the passage forming member 35 caused by pressure pulsation when the refrigerant is depressurized. Further, an oil return hole 34c for returning the refrigeration oil in the liquid-phase refrigerant into the compressor 11 through the gas-phase refrigerant outflow passage 34b is formed in the root part (lowermost part) of the pipe 34a.

  As shown in FIG. 1, the 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 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 31 d 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. This control device performs various calculations and processes based on the control program stored in the ROM, and controls the operations of the various electric actuators 11b, 12d, 14a 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 present embodiment in the above configuration will be described with reference to the Mollier diagram of FIG. The vertical axis of the Mollier diagram shows pressures corresponding to P0, P1, and P2 in FIG. First, when the operation switch of the operation panel is turned on (ON), the control device operates the electric motor 11b, the cooling fan 12d, the blower fan 14a, and the like of the compressor 11. Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it.

  The high-temperature and high-pressure gas-phase refrigerant (point a6 in FIG. 6) 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 from the 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. 6). a6 point → b6 point).

  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 b6 → point c6 in FIG. 6). At this time, the refrigerant passage area in the minimum passage area portion 30m of the nozzle passage 13a is adjusted so that the degree of superheat of the evaporator 14 outlet side refrigerant approaches a predetermined value.

  The refrigerant flowing out of the evaporator 14 is sucked through the refrigerant suction port 31b and the suction passage 13b (the inflow space 30c and the suction passage 30d) by the suction action of the injection refrigerant injected from the nozzle passage 13a. Furthermore, the refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b and the like flow into the diffuser passage 13c (point c6 → d6, h6 → d6 in FIG. 6).

  In the diffuser passage 13c, the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area. As a result, the pressure of the mixed refrigerant rises while the injection refrigerant and the suction refrigerant are mixed (d6 point → e6 point in FIG. 6). The refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (point e6 → f6, point e6 → g6 in FIG. 6).

  The liquid-phase refrigerant separated in the gas-liquid separation space 30f flows out from the liquid-phase refrigerant outlet 31c and flows into the evaporator 14. The refrigerant that has flowed into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates to cool the blown air (g6 point → h6 point in FIG. 6). On the other hand, the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out of the gas-phase refrigerant outlet 31d, is sucked into the compressor 11, and is compressed again (point f6 → a6 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. Further, in the ejector refrigeration cycle 10, since the refrigerant whose pressure is increased in the diffuser passage 13c is sucked into the compressor 11, the driving power of the compressor 11 can be reduced and the cycle efficiency (COP) can be improved. .

  Furthermore, according to the ejector 13 of the present embodiment, by turning the refrigerant in the swirl space 30a, the refrigerant pressure on the swivel center side in the swirl space 30a is reduced to the pressure that becomes a saturated liquid phase refrigerant, or the refrigerant is depressurized. The pressure can be reduced to boiling (causing cavitation). Thus, the gas phase refrigerant is present in the swirl space 30a in the vicinity of the swirl center line, and the liquid single phase is surrounded by the two-phase separation so that a larger amount of gas-phase refrigerant exists on the inner periphery side than the outer periphery side of the swirl center shaft. State.

  As the refrigerant in the two-phase separation state flows into the nozzle passage 13a in this manner, the tip 131 of the nozzle passage 13a has a wall surface boiling that occurs when the refrigerant is separated from the outer peripheral side wall surface of the annular refrigerant passage. Boiling of the refrigerant is promoted by interfacial boiling by boiling nuclei generated by cavitation of the refrigerant on the central axis side of the annular refrigerant passage. Thereby, the refrigerant flowing into the minimum passage area 30m of the nozzle passage 13a is in a gas-liquid mixed state in which the gas phase and the liquid phase are uniformly mixed.

  Then, the flow of refrigerant in the gas-liquid mixed state is choked in the vicinity of the minimum passage area portion 30m, and the gas-liquid mixed state refrigerant that has reached the speed of sound by this choking is accelerated by the divergent portion 132 and injected. The Thus, by promoting boiling by both wall boiling and interfacial boiling, the gas-liquid mixed refrigerant can be efficiently accelerated until it reaches the speed of sound, so that the energy conversion efficiency in the nozzle passage 13a (corresponding to the nozzle efficiency of the prior art) is increased. Can be improved.

  Further, in the ejector 13 of the present embodiment, the passage forming member 35 is formed in a conical shape in which the cross-sectional area increases with distance from the decompression space 30b, and the cross-sectional shape of the diffuser passage 13c is annular. Therefore, the shape of the diffuser passage 13c can be made to expand along the outer periphery of the passage forming member 35 as the distance from the decompression space 30b increases, and the refrigerant flowing through the diffuser passage 13c is swirled. be able to.

  As a result, the refrigerant flow path for increasing the pressure of the refrigerant in the diffuser passage 13c can be formed in a spiral shape, so that the diffuser portion is formed in a shape extending in the axial direction of the nozzle portion as in the prior art. Thus, it is possible to suppress an increase in the dimension of the diffuser passage 13c in the axial direction (the axial direction of the passage forming member 35). As a result, an increase in size of the ejector 13 as a whole can be suppressed.

  In addition to this, in the ejector 13 of the present embodiment, the plate surface of the plate-like portion 38b of the actuating rod 38 that is the rotation promoting member is inclined so as to guide the flow of the refrigerant in the direction around the axis of the passage forming member 35. Therefore, the swirling flow of the refrigerant flowing through the diffuser passage 13c can be promoted. Therefore, for example, even if the refrigerant passage area of the diffuser passage 13c is changed to reduce the flow velocity of the refrigerant flowing into the diffuser passage, it is possible to prevent the speed in the swirling direction of the refrigerant flowing through the diffuser passage 13c from decreasing. .

  Thereby, it can suppress that the spiral refrigerant flow path for pressurizing a refrigerant | coolant in the diffuser channel | path 13c becomes short, and can suppress the fall of the pressure | voltage rise amount of the refrigerant | coolant in the diffuser channel | path 13c. Furthermore, the centrifugal force acting on the refrigerant flowing out of the diffuser passage 13c and flowing into the gas-liquid separation space 30f is suppressed from being reduced, and the deterioration of the gas-liquid separation performance in the gas-liquid separation space 30f is suppressed. You can also.

  Moreover, in the ejector 13 of this embodiment, since the action | operation rod 38 which is a connection member is utilized as a turning promotion member, it is not necessary to provide the exclusive member for promoting a turning flow.

  That is, according to the ejector 13 of the present embodiment, high energy conversion efficiency can be exhibited in the nozzle passage 13a without causing an increase in the size of the physique, regardless of the load fluctuation of the ejector refrigeration cycle 10, and In addition, an ejector capable of exhibiting high boosting performance in the diffuser passage 13c can be realized.

  Further, since the ejector 13 of the present embodiment is provided with the drive means 37, the passage forming member 35 is displaced according to the load fluctuation of the ejector refrigeration cycle 10, and the refrigerant passage areas of the nozzle passage 13a and the diffuser passage 13c are increased. Can be adjusted. Therefore, the ejector 13 can be appropriately operated in accordance with the load fluctuation of the ejector refrigeration cycle 10.

  Further, as the driving means 37 displaces the passage forming member 35 and expands the refrigerant passage area of the diffuser passage 13c, the operating rod 38 rotates to reduce the inclination angle θ, so that the load on the ejector refrigeration cycle 10 is increased. According to the fluctuation, the swirling flow of the refrigerant flowing through the diffuser passage 13c can be effectively promoted.

  For example, when the heat load of the ejector refrigeration cycle 10 is increased and the refrigerant passage area of the diffuser passage 13c is increased, the inclination angle θ can be reduced accordingly. Therefore, when the heat load of the ejector type refrigeration cycle 10 increases and the flow velocity of the refrigerant flowing into the diffuser passage 13c increases, the refrigerant flowing out of the diffuser passage 13c without unnecessarily promoting the swirling flow. Pressure loss can be reduced.

  On the other hand, when the heat load of the ejector refrigeration cycle 10 is reduced and the refrigerant passage area of the diffuser passage 13c is reduced, the inclination angle θ can be increased accordingly. Therefore, when the heat load of the ejector refrigeration cycle 10 decreases and the flow rate of the refrigerant flowing into the diffuser passage 13c decreases, the swirling flow of the refrigerant flowing through the diffuser passage 13c can be appropriately promoted.

  Furthermore, since the enclosed space 37b in which the temperature sensitive medium is enclosed in the driving means 37 is disposed at a position sandwiched between the suction passage 13b and the diffuser passage 13c, the space between the suction passage 13b and the diffuser passage 13c is arranged. The space formed can be effectively used. As a result, the enlargement of the physique as the whole ejector can be further suppressed.

  Moreover, since the enclosed space 37b is disposed at a position surrounded by the suction passage 13b and the diffuser passage 13c, the temperature of the refrigerant flowing out of the evaporator 14 flowing through the suction passage 13b without being affected by the outside air temperature or the like. Can be satisfactorily transmitted to the temperature sensitive medium, and 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.

  Further, since the body 30 of the ejector 13 of the present embodiment is formed with a gas-liquid separation space 30f for separating the gas-liquid of the refrigerant flowing out from the diffuser passage 13c, a gas-liquid separation means is provided separately from the ejector 13. In contrast, the volume of the gas-liquid separation space 30f can be effectively reduced.

  That is, in the gas-liquid separation space 30f of this embodiment, as described above, the refrigerant flowing out of the diffuser passage 13c has already swirled, so that the space for generating or growing the swirling flow of the refrigerant in the gas-liquid separation space 30f. There is no need to provide. Therefore, the volume of the gas-liquid separation space 30f can be effectively reduced as compared with the case where the gas-liquid separation means is provided separately from the ejector 13.

(Second Embodiment)
In the present embodiment, an example in which the cross-sectional shape of the plate-like portion 38b is modified with respect to the first embodiment will be described. Specifically, in the ejector 13 of the present embodiment, the cross-sectional shape of the plate-like portion 38b is formed in a flat plate shape. That is, as shown in the cross-sectional view of FIG. 7, the plate-like portion 38b of the present embodiment has a plate surface on the opposite side to the plate surface on the axial center side of the passage forming member 35 among the plate surfaces of the plate-like portion 38b. Is formed. FIG. 7 is a drawing corresponding to FIG. 5 of the first embodiment.

  Further, in the present embodiment, since the plate-like portion 38b is formed in a flat plate shape, the outlet side passage area (in the refrigerant passage formed between the adjacent plate-like portions 38b during normal operation of the ejector refrigeration cycle 10 ( The area on the A2 side in FIG. 7 can be made larger than the area on the inlet side passage (the area on the A1 side in FIG. 7). That is, as shown in the cross-sectional view of FIG. 7, the plurality of plate-like portions 38 b can be arranged in a speed reduction blade row as a relation of A1 <A2.

  Other configurations and operations are the same as those in the first embodiment. Even if the cross-sectional shape of the plate-like portion 18b is formed like the ejector 13 of the present embodiment, the same effect as that of the first embodiment can be obtained. Furthermore, in this embodiment, since the plate-shaped part 38b is formed in flat form, the action | operation rod 38 can be formed easily with respect to the case where it forms in a wing | blade shape like 1st Embodiment.

  Moreover, in the ejector 13 of this embodiment, since the several plate-shaped part 38b is arrange | positioned at the speed reducing blade row, it is possible to gradually increase the cross-sectional area of the refrigerant passage formed between the plate-shaped parts 38b. it can. Therefore, the refrigerant passage formed between the plate-like portions 38b can function as a diffuser that converts the velocity energy of the refrigerant into pressure energy. As a result, the ejector 13 can exhibit a higher boosting performance.

  In the present embodiment, the cross-section of the plate-like portion 38b is arranged so that the plurality of plate-like portions 38b are arranged in a reduction blade row at least within the movable range of the plate-like portion 38b during normal operation of the ejector refrigeration cycle 10. A shape is formed.

  That is, generally, as the inclination angle θ increases, the inlet-side passage area and the outlet-side passage area of the refrigerant passage formed between the adjacent plate-like portions 38b approach the same value. That is, as the inclination angle θ increases, the relationship of A1≈A2 is established, and the plurality of plate-like portions 38b approach the constant velocity blade row arrangement. The same applies to the plate-like portion 38b of the following embodiment.

(Third embodiment)
In the present embodiment, an example in which the cross-sectional shape of the plate-like portion 38b is modified as shown in the cross-sectional view of FIG. Specifically, the cross-sectional shape of the plate-like portion 38b of the present embodiment is formed in a shape in which the plate thickness in the circumferential direction gradually increases from the axial center side to the outer peripheral side of the passage forming member 35. FIG. 8 is a drawing corresponding to FIG. 5 of the first embodiment.

  Thereby, in this embodiment, at the time of normal operation of the ejector refrigeration cycle 10, the inlet side passage area (A1 side area in FIG. 8) and the outlet side passage area of the refrigerant passage formed between the adjacent plate-like portions 38b. (A2 side area in FIG. 8) is set to a substantially equivalent value. That is, in the present embodiment, as shown in the cross-sectional view of FIG. 8, a plurality of plate-like portions 38b can be arranged in a constant velocity cascade as a relationship of A1≈A2.

  Other configurations and operations are the same as those in the first embodiment. Even if the cross-sectional shape of the plate-like portion 18b is formed like the ejector 13 of the present embodiment, the same effect as that of the first embodiment can be obtained.

  Further, in the ejector 13 of the present embodiment, the plurality of plate-like portions 38b are arranged in a constant velocity cascade, so that the passage cross-sectional area of the refrigerant passage formed between the plate-like portions 38b is made substantially constant. Can do. Therefore, it is difficult to change the pressure and flow velocity of the refrigerant flowing through the refrigerant passage formed between the plate-like portions 38b.

(Fourth embodiment)
In the present embodiment, an example in which the cross-sectional shape of the plate-like portion 38b is deformed as shown in the cross-sectional view of FIG. 9 will be described. Specifically, the cross-sectional shape of the plate-like portion 38b of the present embodiment is formed in a shape in which the plate thickness in the circumferential direction gradually increases from the axial center side to the outer peripheral side of the passage forming member 35. The degree to which the plate thickness is made thicker than the form is increased. FIG. 9 is a drawing corresponding to FIG. 5 of the first embodiment.

  Thereby, in this embodiment, at the time of normal operation of the ejector type refrigeration cycle 10, the inlet side passage area (area on the A1 side in FIG. 9) of the refrigerant passage formed between the adjacent plate-like portions 38b is the outlet side passage. The area is larger than the area (area on the A2 side in FIG. 9). That is, as shown in the cross-sectional view of FIG. 9, the plurality of plate-like portions 38b can be arranged in the speed-up blade row arrangement (acceleration blade row arrangement) as A1> A2.

  Other configurations and operations are the same as those in the first embodiment. Even if the cross-sectional shape of the plate-like portion 18b is formed like the ejector 13 of the present embodiment, the same effect as that of the first embodiment can be obtained.

  Further, in the ejector 13 of the present embodiment, since the plurality of plate-like portions 38b are arranged in the speed increasing blade row, the passage cross-sectional area of the refrigerant passage formed between the plate-like portions 38b is gradually reduced. Can do. Therefore, the flow rate of the refrigerant flowing through the refrigerant passage formed between the plate-like portions 38b can be increased, and the swirling flow of the refrigerant flowing through the diffuser passage 13c can be further promoted.

(Fifth embodiment)
In this embodiment, as shown in the cross-sectional view of FIG. 10, the cross-sectional shape of the plate-like portion 38b is formed in a triangular shape. Furthermore, in this embodiment, the inlet side passage area (area on the A1 side in FIG. 10) and the outlet side passage area (area on the A2 side in FIG. 10) of the refrigerant passage formed between the adjacent plate-like portions 38b are substantially reduced. As an equivalent value, as in the third embodiment, a plurality of plate-like portions 38b are arranged in a constant velocity cascade as a relationship of A1≈A2.

  Other configurations and operations are the same as those in the first embodiment. Therefore, according to the ejector 13 of the present embodiment, the same effect as that of the third embodiment can be obtained.

(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-described embodiment, the example in which the actuating rod 38 that is a connecting member that transmits driving force from the driving unit 37 to the passage forming member 35 has a function as a turning promotion member has been described. Is not limited to this. For example, you may comprise by the plate-shaped member etc. which were comprised separately from the action | operation rod 38. FIG.

  Further, in the above-described embodiment, as shown in FIG. 4, the swirl promoting member is constituted by the operating rod 38 arranged so as to cross the refrigerant outlet side of the diffuser passage 13c, and the swirling flow of the refrigerant flowing through the diffuser passage 13c. However, depending on the operating conditions of the ejector refrigeration cycle 10, the swirling flow of the refrigerant from the inlet side to the outlet side of the diffuser passage 13c may not be promoted.

  Specifically, as shown by a thick solid line in FIG. 11, among the speed components of the refrigerant flowing through the diffuser passage 13c, the speed component in the turning direction becomes extremely small with respect to the speed component in the axial direction, The speed component in the turning direction may be almost lost. In addition, in FIG. 11, when it sees from an axial direction, the flow direction of the refrigerant | coolant which flows along the conical side surface of the channel | path formation member 35 is typically shown, and the plate-shaped part 38b of the action | operation rod 38 is also typically shown. It is illustrated in a flat plate shape.

  Even under such operating conditions, according to the ejector of the above-described embodiment, the turning promotion member is provided on the refrigerant outlet side of the diffuser passage 13c. Therefore, at least the refrigerant on the outlet side of the diffuser passage 13c and the diffuser passage 13c. The swirling flow of the refrigerant immediately before flowing out of the refrigerant can be promoted. Therefore, the swirl promoting member is effective in that the centrifugal force acting on the refrigerant flowing into the gas-liquid separation space 30f is suppressed from being reduced, and the deterioration of the gas-liquid separation performance in the gas-liquid separation space 30f can be suppressed. It is.

  (2) In the above-described embodiment, as the driving means 37 for displacing the passage forming member 35, the enclosed space 37b in which the temperature-sensitive medium whose pressure changes with temperature change is enclosed, and the pressure of the temperature-sensitive medium in the enclosed space 37b Although the example which employ | adopted what was comprised with the diaphragm 37a displaced according to is 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. In this case, it is only necessary to change the inclination angle θ of the plate-like portion by rotating the operating rod 38 by providing a thread on the operating rod 38 as in the above embodiment.

  Further, a drive unit that displaces the passage forming member 35 by an electric motor may be employed. In this case, if a plate-like portion is provided on the shaft connecting the electric motor and the passage forming member 35, and the inclination angle θ of the plate-like portion is changed as the electric motor displaces the passage forming member 35, Good.

  (3) In the above-described embodiment, the example in which the inclination angle θ is decreased as the driving unit 37 displaces the passage forming member 35 to increase the refrigerant passage area of the diffuser passage 13c has been described. The relationship between the refrigerant passage area 13c and the inclination angle θ is not limited to this.

  For example, the inclination angle θ may be increased as the driving means 37 displaces the passage forming member 35 to increase the refrigerant passage area of the diffuser passage 13c. That is, an optimum inclination angle θ that can promote the swirling flow of the refrigerant flowing through the diffuser passage 13c according to the load fluctuation of the ejector refrigeration cycle 10 to be applied may be achieved.

  (4) In the above-described embodiment, the example in which the plate-like portion 38b is disposed on the outlet side of the diffuser passage 13c has been described. However, if the swirling flow of the refrigerant flowing through the diffuser passage 13c can be promoted by the plate-like portion 38b. , May be arranged at any position. In the above-described embodiment, the plate-like portion 38b has a plate surface extending in the axial direction of the passage forming member 35. However, the plate-like portion 38b is not limited to this, and the plate surface is a passage. The forming member 35 may be inclined with respect to the axial direction.

  (5) Although the details of the liquid-phase refrigerant outlet 31c and the gas-phase refrigerant outlet 31d of the ejector 13 are not described in the above-described embodiment, a decompression unit (for example, an orifice) that decompresses the refrigerant at these refrigerant outlets Alternatively, a fixed side throttle made of a capillary tube) may be arranged. For example, a fixed throttle may be added to the liquid-phase refrigerant outlet 31c, and the ejector 13 may be applied to an ejector refrigeration cycle including a two-stage booster compressor.

  (6) Although the material of the passage forming member 35 is not described in the above embodiment, the passage forming member 35 may be formed of metal (for example, aluminum) or may be formed of resin. For example, by forming the passage forming member 35 with resin to reduce the weight, the driving means 37 can be reduced in size, and the physique of the ejector 13 as a whole can be further reduced in size.

  (7) 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 / hot storage, a cooling / heating device for a vending machine, and the like.

  (8) 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.

DESCRIPTION OF SYMBOLS 10 Ejector-type refrigeration cycle 13 Ejector 13a Nozzle passage 13b Suction passage 13c Diffuser passage 30 Body 35 Passage formation member 38 Actuating rod 38b Plate-like part

Claims (7)

An ejector applied to a vapor compression refrigeration cycle apparatus (10),
A swirling space (30a) for swirling the refrigerant flowing in from the refrigerant inlet (31a), a decompression space (30b) for decompressing the refrigerant flowing out of the swirling space (30a), and a refrigerant flow downstream of the decompression space (30b) The suction passage (13b) that communicates with the outside and sucks the refrigerant from the outside, and the pressure rising that mixes the injection refrigerant injected from the decompression space (30b) and the suction refrigerant sucked from the suction passage (13b) A body (30) in which a space (30e) is formed;
At least a portion is disposed in the decompression space (30b) and in the pressurization space (30e), and is formed in a conical shape whose cross-sectional area increases with distance from the decompression space (30b). A passage forming member (35),
Drive means (37) for displacing the passage forming member (35),
The refrigerant passage formed between the inner peripheral surface of the body (30) forming the decompression space (30b) and the outer peripheral surface of the passage forming member (35) is the swirling space (30a). A nozzle passage (13a) that functions as a nozzle for depressurizing and injecting the refrigerant flowing out from
The refrigerant passage formed between the inner peripheral surface of the body (30) forming the pressurizing space (30e) and the outer peripheral surface of the passage forming member (35) is the injection refrigerant and the suction A diffuser passage (13c) that functions as a diffuser for mixing and increasing the pressure of the refrigerant;
The diffuser passage (13c) is formed in an annular shape in cross section perpendicular to the axial direction of the passage forming member (35),
Furthermore, a connecting member (38) for transmitting a driving force from the driving means (37) to the passage forming member (35) is provided,
The connecting member (38) has a plate-like portion (38b) formed in a plate shape,
The ejector characterized in that the plate surface of the plate-like portion (38b) is inclined so as to guide the flow of the refrigerant in the direction around the axis of the passage forming member (35). The connecting member (38) is configured to be rotatable around a rotation axis extending parallel to the axial direction of the passage forming member (35),
Of the vertical cross section in the axial direction of the passage forming member (35), the cross section including the plate-like portion (38b) is directed from the axial center of the passage forming member (35) to the rotational center of the connecting member (38). The line flow (L1) extending and the refrigerant flow from the most upstream end (Q1) of the refrigerant flow in the plate surface arranged on the axial center side of the passage forming member (35) among the plate surfaces of the plate-like portion (38b). When the angle formed with the line segment (L2) extending toward the most downstream end (Q2) is the inclination angle θ,
2. The ejector according to claim 1, wherein the inclination angle θ changes as the driving means (37) displaces the passage forming member (35). An ejector applied to a vapor compression refrigeration cycle apparatus (10),
A swirling space (30a) for swirling the refrigerant flowing in from the refrigerant inlet (31a), a decompression space (30b) for decompressing the refrigerant flowing out of the swirling space (30a), and a refrigerant flow downstream of the decompression space (30b) The suction passage (13b) that communicates with the outside and sucks the refrigerant from the outside, and the pressure rising that mixes the injection refrigerant injected from the decompression space (30b) and the suction refrigerant sucked from the suction passage (13b) A body (30) in which a space (30e) is formed;
At least a portion is disposed in the decompression space (30b) and in the pressurization space (30e), and is formed in a conical shape whose cross-sectional area increases with distance from the decompression space (30b). A passage forming member (35),
Drive means (37) for displacing the passage forming member (35),
The refrigerant passage formed between the inner peripheral surface of the body (30) forming the decompression space (30b) and the outer peripheral surface of the passage forming member (35) is the swirling space (30a). A nozzle passage (13a) that functions as a nozzle for depressurizing and injecting the refrigerant flowing out from
The refrigerant passage formed between the inner peripheral surface of the body (30) forming the pressurizing space (30e) and the outer peripheral surface of the passage forming member (35) is the injection refrigerant and the suction A diffuser passage (13c) that functions as a diffuser for mixing and increasing the pressure of the refrigerant;
The diffuser passage (13c) is formed in an annular shape in cross section perpendicular to the axial direction of the passage forming member (35),
And a swirl facilitating member (38) for facilitating swirl flow of the refrigerant flowing through the diffuser passage (13c),
The turning promotion member (38) has a plate-like portion (38b) for guiding the flow of the refrigerant in the direction around the axis of the passage forming member (35), and the axial direction of the passage forming member (35). It is configured to be rotatable around a rotation axis that extends in parallel,
Of the vertical cross section in the axial direction of the passage forming member (35), the cross section including the plate-like portion (38b) is directed from the axial center of the passage forming member (35) to the rotational center of the turning promotion member (38). And the refrigerant flow from the most upstream end (Q1) of the refrigerant flow in the plate surface arranged on the axial center side of the passage forming member (35) among the plate surface of the plate-like portion (38b). When the angle formed with the line segment (L2) extending toward the most downstream end (Q2) of the flow is the inclination angle θ,
The ejector according to claim 1, wherein the inclination angle θ changes as the driving means (37) displaces the passage forming member (35).   The inclination angle θ decreases as the driving means (37) displaces the passage forming member (35) to increase the refrigerant passage area of the diffuser passage (13c). Or the ejector of 3.   The ejector according to any one of claims 1 to 4, wherein the plate-like portion (38b) is disposed on an outlet side of the diffuser passage (13c).   The gas-liquid separation space (30f) for separating the gas-liquid of the refrigerant flowing out from the pressurizing space (30e) is formed in the body (30). The ejector as described in one.   The ejector according to any one of claims 1 to 6, wherein the refrigerant flowing through the diffuser passage (13c) is swirling in the same direction as the refrigerant swirling in the swirling space (30a). .

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