JP6380122B2 - Ejector - Google Patents

Description

  The present invention relates to an ejector that sucks fluid by a suction action of a jet fluid ejected at a high speed.

  Conventionally, Patent Document 1 is applied to a vapor compression refrigeration cycle apparatus, and sucks refrigerant from a refrigerant suction port by a suction action of a jet refrigerant injected at a high speed, and mixes the jet refrigerant and the suction refrigerant. An ejector for boosting pressure is disclosed.

  In the ejector of Patent Document 1, a substantially conical passage forming member is disposed inside the body, and a refrigerant passage having an annular cross section is formed in a gap between the body and the conical side surface of the passage forming member. In this refrigerant passage, the portion on the most upstream side of the refrigerant flow is used as a nozzle passage for depressurizing and injecting the high-pressure refrigerant, and the portion on the downstream side of the refrigerant flow in the nozzle passage is mixed with the injected refrigerant and the suction refrigerant. This is used as a diffuser passage for increasing the pressure of the mixed refrigerant.

  Furthermore, the ejector of Patent Document 1 includes a driving unit that displaces the passage forming member, and the passage forming member is displaced according to the load fluctuation of the refrigeration cycle apparatus. Thus, the ejector is appropriately operated by adjusting the passage sectional area of the refrigerant passage in accordance with the flow rate of the refrigerant circulating in the cycle.

JP 2013-177879 A

  By the way, in the ejector of patent document 1, in order to change the passage cross-sectional area of a refrigerant passage appropriately, the passage formation member formed with the metal with high durability is employ | adopted. Therefore, the weight of the passage forming member becomes heavy, and the resonance frequency of the vibration system including the passage forming member tends to be a relatively low frequency.

  For this reason, if the ejector of patent document 1 is applied to the refrigeration cycle apparatus for vehicles, for example, there is a possibility that the vibration system including the passage forming member may resonate with the vehicle vibration and generate large noise and vibration. .

  On the other hand, a means for reducing the weight of the passage forming member by forming the passage forming member with resin is conceivable.

  However, the passage forming member made of resin is more likely to be damaged or deformed than that made of metal. Further, among the passage forming members, if the conical side surface forming the refrigerant passage or a portion that receives a load when it is displaced is damaged or deformed, the passage forming member according to the load fluctuation of the refrigeration cycle apparatus. Even if it is displaced, the cross-sectional area of the refrigerant passage cannot be changed appropriately.

  In view of the above-described points, an object of the present invention is to appropriately adjust the passage cross-sectional area of a refrigerant passage while reducing the weight of the passage formation member in an ejector including the passage formation member.

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 decompression space (30b) for decompressing the refrigerant flowing in from the refrigerant inlet (31a), a suction passage (13b) communicating with the downstream side of the refrigerant flow in the decompression space (30b) and circulating the refrigerant sucked from the outside A body (30) having a pressure increasing space (30e) for mixing the injection refrigerant injected from the decompression space (30b) and the suction refrigerant sucked from the suction passage (13b), and at least partly A passage forming member that is disposed in the decompression space (30b) and in the pressurization space (30e) and has a conical shape whose cross-sectional area increases as the distance from the decompression space (30b) increases. (35) and 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) flows in from the refrigerant inlet (31a). A nozzle passage (13a) that functions as a nozzle for depressurizing and injecting the refrigerant; an inner peripheral surface of a portion of the body (30) that forms the pressurizing space (30e); and an outer peripheral surface of the passage forming member (35) The refrigerant passage formed between the two is a diffuser passage (13c) that functions as a booster that mixes and boosts the injected refrigerant and the suction refrigerant,
The passage forming member (35) includes a metal portion (351, 355, 356, 357) formed of metal and a resin portion (353, 354) formed of resin, and further, the metal portion (351 357) is an outer peripheral surface of a portion forming the nozzle passage (13a), and forms an outer peripheral surface including at least a portion forming the minimum passage area portion (30m) of the nozzle passage (13a). It is a feature.

  According to this, since the channel | path formation member (35) has the resin part (353, 354), weight reduction can be achieved rather than what formed all the site | parts with the metal.

  Furthermore, since the outer peripheral surface including the site | part which forms the minimum channel | path area part (30m) of a nozzle channel | path (13a) among the outer peripheral surfaces of a channel | path formation member (35) is formed of the metal part (351 ... 357), Damage and deformation of the outer peripheral surface can be suppressed. Therefore, it is possible to suppress the passage cross-sectional area of the minimum passage area portion (30 m) of the nozzle passage (13a) from being changed due to damage or deformation of the passage forming member (35).

  As a result, according to the invention described in this claim, in the ejector including the passage forming member (35), the passage cross-sectional area of the refrigerant passage formed inside is reduced while reducing the weight of the passage forming member (35). It can be adjusted appropriately. As a result, the ejector can be appropriately operated according to the load fluctuation of the refrigeration cycle apparatus (10).

The invention according to claim 7 is an ejector applied to the vapor compression refrigeration cycle apparatus (10),
A decompression space (30b) for decompressing the refrigerant flowing in from the refrigerant inlet (31a), a suction passage (13b) communicating with the downstream side of the refrigerant flow in the decompression space (30b) and circulating the refrigerant sucked from the outside A body (30) having a pressure increasing space (30e) for mixing the injection refrigerant injected from the decompression space (30b) and the suction refrigerant sucked from the suction passage (13b), and at least partly A passage forming member that is disposed in the decompression space (30b) and in the pressurization space (30e) and has a conical shape whose cross-sectional area increases as the distance from the decompression space (30b) increases. (35) and an elastic member (40) for applying a load to 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) flows in from the refrigerant inlet (31a). A nozzle passage (13a) that functions as a nozzle for depressurizing and injecting the refrigerant; an inner peripheral surface of a portion of the body (30) that forms the pressurizing space (30e); and an outer peripheral surface of the passage forming member (35) The refrigerant passage formed between the two is a diffuser passage (13c) that functions as a booster that mixes and boosts the injected refrigerant and the suction refrigerant,
The passage forming member (35) has a metal portion (352) formed of metal and a resin portion (353, 354) formed of resin, and the metal portion (352) is a passage forming member. Of (35), the elastic member (40) is formed with a contact portion.

  According to this, since the channel | path formation member (35) has the resin part (353, 354), weight reduction can be achieved compared with the case where all the parts are formed with a metal.

  Furthermore, since the site | part with which an elastic member (40) contact | abuts is formed of the metal part (352) among the channel | path formation members (35), the damage and deformation | transformation of the said site | part can be suppressed. Therefore, when the passage forming member (35) is displaced, it is possible to prevent the load received by the passage forming member (35) from the elastic member (40) from changing.

  As a result, according to the invention described in this claim, in the ejector including the passage forming member (35), the passage cross-sectional area of the refrigerant passage formed inside is reduced while reducing the weight of the passage forming member (35). It can be adjusted appropriately. As a result, the ejector can be operated appropriately as in the first aspect of the invention.

  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 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 axial direction expanded sectional view of the passage formation member of a 1st embodiment. It is a Mollier diagram which shows the change of the state of the refrigerant | coolant in the ejector type refrigeration cycle of 1st Embodiment. It is an axial direction expanded sectional view which shows the modification of the channel | path formation member of 1st Embodiment. It is an axial direction expanded sectional view which shows another modification of the channel | path formation member of 1st Embodiment. It is an axial direction expanded sectional view of the passage formation member of a 2nd embodiment. It is an axial direction expanded sectional view of the passage formation member of a 3rd embodiment. It is an axial direction expanded sectional view of the channel formation member of a 4th embodiment.

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

  Further, the ejector refrigeration cycle 10 of the present embodiment employs an HFC-based refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure. doing. 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.

  In the ejector refrigeration cycle 10, the compressor 11 boosts and discharges the refrigerant until the refrigerant is sucked into a high-pressure refrigerant. Specifically, the compressor 11 of the present embodiment is an electric compressor configured by housing a fixed capacity type compression mechanism and an electric motor that drives the compression mechanism in one housing.

  As this compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed. Further, the operation (rotation speed) of the electric motor is controlled by a control signal output from a control device to be described later, and either an AC motor or a DC motor may be adopted.

  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 heat radiator 12 exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d, and dissipates the high-pressure gas-phase refrigerant to condense and condense the part 12a. In addition, the receiver 12b that separates the gas-liquid of the refrigerant that has flowed out of the condensing unit 12a and stores excess liquid-phase refrigerant, and the liquid-phase refrigerant that has flowed out of the receiver 12b and the outside air blown from the cooling fan 12d exchange heat. This is a so-called subcool condenser that includes a supercooling unit 12c that supercools the liquid refrigerant.

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

  The ejector 13 functions as a refrigerant pressure reducing means for reducing the pressure of the supercooled high-pressure liquid-phase refrigerant that has flowed out of the radiator 12 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 also functions as a refrigerant circulating means (refrigerant transporting means) for sucking (transporting) and circulating the refrigerant flowing out of the evaporator 14.

  Furthermore, the ejector 13 according to the present embodiment also functions as a gas-liquid separation unit that separates the gas-liquid of the decompressed refrigerant. That is, the ejector 13 of the present embodiment is configured as an ejector with a gas-liquid separation function (ejector module).

  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 parts having the same functions 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 has a housing body 31 that is formed of a prismatic or columnar metal or resin and forms the outer shell of the ejector 13. Further, a nozzle body 32, a middle body 33, and a lower body 34 are fixed inside the housing body 31.

  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 to the inlet side of the compressor 11 A gas-phase refrigerant outlet 31d and the like are formed.

  Further, in the present embodiment, an orifice 30i as a pressure reducing means for reducing the pressure of the refrigerant flowing into the evaporator 14 is disposed in the liquid phase refrigerant passage connecting the gas-liquid separation space 30f and the liquid phase refrigerant outlet 31c. .

  The nozzle body 32 is formed of a substantially conical metal member that tapers in the refrigerant flow direction. Further, the nozzle body 32 is fixed to the inside of the housing body 31 by means such as press fitting so that the axial direction is the vertical direction (the vertical direction in FIG. 2). 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.

  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 around the central axis of the swirl 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 reduced until the pressure is reached.

  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.

  Furthermore, a passage for changing the passage cross-sectional area of the minimum passage area portion 30m while forming the smallest passage area portion 30m having the smallest passage cross-sectional area of the refrigerant passage in the pressure reduction space 30b. A forming member 35 is disposed.

  The passage forming member 35 is formed in a substantially conical shape that gradually spreads 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. That is, the passage forming member 35 is formed in a conical shape whose cross-sectional area increases as it moves away from the decompression space 30b side. The detailed configuration of the passage forming member 35 will be described later.

  Accordingly, as shown in FIG. 3, the tip 131 is formed as a refrigerant passage formed between the inner peripheral surface of the portion of the nozzle body 32 that forms the pressure reducing space 30 b and the upper outer peripheral surface of the passage forming member 35. And the divergent part 132 is formed. The tapered portion 131 is a refrigerant passage that is formed on the upstream side of the refrigerant flow with respect to the minimum passage area portion 30m and that the passage cross-sectional area up to the minimum passage area portion 30m gradually decreases. The divergent portion 132 is a refrigerant passage that is formed on the downstream side of the refrigerant flow from the minimum passage area portion 30m, and the passage cross-sectional area gradually increases.

  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 circular to coaxial). Donut shape excluding a small-diameter circular shape arranged on the top). Furthermore, the passage cross-sectional area in the divergent portion 132 gradually increases toward the downstream side of the refrigerant flow.

  In the present embodiment, the 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 by such a passage shape is the nozzle passage 13a that functions as a Laval nozzle, and the refrigerant The pressure of the refrigerant is reduced and the flow rate of the refrigerant is increased so as to be supersonic.

  Next, as shown in FIG. 2, the middle body 33 is provided with a through hole penetrating the front and back (up and down) at the center thereof. Further, the middle body 33 is formed of a metal disk-like member that houses a drive mechanism 37 that displaces the passage forming member 35 on the outer peripheral side of the through hole. 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.

  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 cross-sectional 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. 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 for mixing the refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the suction passage 30d. The central axis of the pressurizing space 30e is arranged coaxially with the central axes of the swirling space 30a and the decompressing space 30b.

  A lower side of the passage forming member 35 is disposed in the boosting space 30e. Further, the refrigerant passage formed between the inner peripheral surface of the portion forming the pressurizing space 30e of the middle body 33 and the outer peripheral surface on the lower side of the passage forming member 35 has a passage sectional area toward the downstream side of the refrigerant flow. It is formed into a shape that gradually expands. Thereby, in this refrigerant path, the velocity energy of the mixed refrigerant of the injection refrigerant and the suction refrigerant can be converted into pressure energy.

  Therefore, 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, as shown in FIG. A diffuser passage 13c that functions as a diffuser (a boosting unit) for mixing and boosting is configured. The cross section of the diffuser passage 13c perpendicular to the central axis is also formed in an annular shape.

  Next, a drive mechanism 37 that is disposed inside the middle body 33 and that is a drive means for displacing the passage forming member 35 will be described. The drive mechanism 37 includes a circular thin plate-like diaphragm 37a that 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) changes in pressure according to the temperature of the refrigerant on the outlet side of the evaporator 14 (specifically, the refrigerant that has flowed out of the evaporator 14). An enclosed space 37b in which a temperature sensitive medium is enclosed is configured. 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 the present embodiment is a medium mainly composed of R134a.

  On the other hand, the lower space of the two spaces partitioned by the diaphragm 37a constitutes an introduction space 37c for introducing the refrigerant on the outlet side of the evaporator 14 through a communication path (not shown). Accordingly, the temperature of the refrigerant on the outlet side of the evaporator 14 is transmitted to the temperature sensitive medium enclosed in the enclosed space 37b via the lid member 37d and the diaphragm 37a that partition the inflow space 30c and the enclosed space 37b.

  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 on the outlet side of the evaporator 14 flowing into the introduction space 37c. For this reason, it is preferable that the diaphragm 37a is made of a tough material that is rich in elasticity and has good heat conduction. Accordingly, a thin metal plate such as stainless steel (SUS304) may be used as the diaphragm 37a, or a rubber made material such as EPDM (ethylene propylene diene copolymer rubber) containing a base fabric that is excellent in pressure resistance and sealability. May be.

  Further, the upper end side of a columnar actuating rod 37e is joined to the center of the diaphragm 37a by means such as welding, and the outer peripheral side of the lowermost portion (bottom) of the passage forming member 35 is fixed to the lower end side of the actuating rod 37e. Has been. Thereby, the diaphragm 37a and the passage forming member 35 are connected, and the passage forming member 35 is displaced in accordance with the displacement of the diaphragm 37a, and the passage sectional area in the minimum passage area portion 30m of the nozzle passage 13a is adjusted.

  More specifically, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree) increases, the saturation pressure of the temperature-sensitive medium enclosed in the enclosed space 37b increases, and the pressure in the introduction space 37c increases from the internal pressure of the enclosed space 37b. The differential pressure after subtracting is increased. Thereby, the diaphragm 37a displaces the channel | path formation member 35 in the direction (vertical direction lower side) which enlarges the channel | path cross-sectional area in the minimum channel | path area part 30m.

  On the other hand, when the temperature (superheat degree) of the refrigerant on the outlet side of the evaporator 14 is lowered, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37b is lowered, and the pressure of the introduction space 37c is subtracted from the internal pressure of the enclosed space 37b. The differential pressure is reduced. Thereby, the diaphragm 37a displaces the passage forming member 35 in a direction (vertical direction upper side) in which the passage sectional area in the minimum passage area portion 30m is reduced.

  Thus, the diaphragm 37a displaces the passage forming member 35 according to the superheat degree of the evaporator 14 outlet side refrigerant, so that the superheat degree of the evaporator 14 outlet side refrigerant approaches the predetermined reference superheat degree KSH. The passage sectional area in the minimum passage area portion 30m is adjusted. The gap between the operating rod 37e and the middle body 33 is sealed by a sealing member such as an O-ring (not shown), and the refrigerant does not leak from the gap even if the operating rod 37e is displaced.

  Further, the bottom surface of the passage forming member 35 receives a load of a coil spring 40 fixed to the lower body 34. The coil spring 40 is an elastic member that applies a load that biases the passage forming member 35 toward the side that reduces the cross-sectional area of the passage in the minimum passage area portion 30m. By adjusting this load, the valve opening pressure of the passage forming member 35 can be changed to change the target reference superheat degree KSH.

  In the present embodiment, a plurality of (specifically, two) columnar spaces are provided on the outer peripheral side of the middle body 33, and two thin drive diaphragms 37a are fixed inside the spaces, so that the two drive mechanisms 37 are fixed. Although it comprises, the number of the drive mechanisms 37 is not limited to this. In addition, when providing the drive mechanism 37 in multiple places, it is desirable to arrange | position at equal angle intervals with respect to a central axis, respectively.

  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, there is formed a gas-liquid separation space 30f for separating the gas-liquid refrigerant flowing out from the diffuser passage 13c formed in the pressure increasing space 30e.

  The gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space, and the central axis of the gas-liquid separation space 30f is also the central axis of the swirl space 30a, the decompression space 30b, the pressurization space 30e, and the like. And are arranged on the same axis. Further, the refrigerant flowing out from the diffuser passage 13c to the gas-liquid separation space 30f has a speed component in a turning direction that turns around the central axis. Therefore, the gas-liquid refrigerant is separated in the gas-liquid separation space 30f by the action of centrifugal force.

  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 is formed in the pipe 34a to guide the gas-phase refrigerant separated in the gas-liquid separation space 30f to the gas-phase refrigerant outlet 31d of the housing body 31.

  The aforementioned coil spring 40 is fixed to the upper end of the pipe 34a. The coil spring 40 forms a vibration system together with the passage forming member 35 and the drive mechanism 37, and also has a function of attenuating vibration of the passage forming member 35 due to pressure pulsation when the refrigerant is decompressed. . An oil return hole 34c is formed on the bottom surface of the lower body 34 to return the refrigeration oil in the liquid phase refrigerant into the compressor 11 through the gas phase refrigerant outflow passage 34b.

  Here, the detailed configuration of the passage forming member 35 of the present embodiment will be described with reference to FIG. The passage forming member 35 of the present embodiment is formed of a metal portion made of metal (in this embodiment, a stainless alloy) and a resin (in this embodiment, polyphenylene sulfide (general abbreviation: PPS)). It has a resin part. Furthermore, the metal part and the resin part are integrally formed by insert molding.

  As the metal portion of the present embodiment, a top-side conical member 351 disposed on the top side of the passage forming member 35 and an annular plate-shaped member 352 disposed at a portion where the coil spring 40 abuts are provided. . In addition, as the resin portion, a bottom-side truncated cone-shaped member 353 disposed on the bottom surface of the top-side conical member 351 is provided.

  The top-side conical member 351 is a size that can form an outer peripheral surface of a portion of the passage forming member 35 that forms the nozzle passage 13a and includes at least a portion that forms the minimum passage area portion 30m. Is formed.

  More specifically, in the passage forming member 35 of the present embodiment, the portion disposed inside the decompression space 30b is formed by the top-side conical member 351 when viewed from the direction perpendicular to the central axis. . Thereby, the site | part which forms the minimum channel | path area part 30m is reliably formed with a metal part among the conical side surfaces of the channel | path formation member 35. FIG.

  As shown in FIG. 3, the nozzle passage 13 a of the present embodiment is within a range in which a line segment extending in the normal direction from the outer peripheral surface of the passage forming member 35 intersects a portion of the nozzle body 32 that forms the decompression space 30 b. Shall be formed.

  Further, a metal extending portion 351 a extending toward the bottom surface side of the bottom side truncated cone-like member 353 is provided on the bottom surface of the top side conical member 351. The extending portion 351a functions to increase the bonding area between the metal portion and the resin portion by expanding the bonding area between the metal portion and the resin portion during insert molding.

  More specifically, the extending portion 351a of the present embodiment is formed in a columnar shape arranged coaxially with the passage forming member 35, and is integrally formed on the bottom surface of the top-side conical member 351. Yes. Furthermore, the extending portion 351a may have another shape as long as the bonding area between the metal portion and the resin portion can be increased.

  Further, as shown in FIG. 1, the refrigerant inlet side of the evaporator 14 is connected to the liquid phase refrigerant outlet 31 c of the ejector 13. The evaporator 14 performs heat exchange between the low-pressure refrigerant decompressed by the ejector 13 and the blown air blown into the vehicle interior from the blower fan 14a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is a vessel.

  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 above-described various electric actuators 11, 12d, 14a and the like.

  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 the present embodiment, the configuration that controls the operation of the electric motor of the compressor 11 constitutes the discharge capacity control means.

  Next, the operation of the present embodiment in the above configuration will be described using the Mollier diagram of FIG. On the vertical axis of the Mollier diagram of FIG. 5, pressures corresponding to P0, P1, and P2 of FIG. 3 are shown. First, when the operation switch of the operation panel is turned on (ON), the control device operates the electric motor of the compressor 11, the cooling fan 12d, the blower fan 14a, and the like. Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it.

  The high-temperature and high-pressure refrigerant (point a5 in FIG. 5) discharged from the compressor 11 flows into the condensing part 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, dissipates heat, and condenses. The refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid phase refrigerant separated from the gas and liquid by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d in the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a5 in FIG. 5). Point → b5 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 (b5 point → c5 point in FIG. 5). At this time, the passage cross-sectional area in the minimum passage area 30m of the decompression space 30b is adjusted so that the degree of superheat of the evaporator 14 outlet side refrigerant (point h5 in FIG. 5) approaches a predetermined value.

  The refrigerant (h5 in FIG. 5) that has flowed out of the evaporator 14 due to the suction action of the refrigerant injected from the nozzle passage 13a causes the refrigerant suction port 31b and the suction passage 13b (more specifically, the inflow space 30c). And is sucked through the suction passage 30d). The refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13d and the like flow into the diffuser passage 13c and merge (point c5 → d5, h′5 → d5 in FIG. 5). ).

  Here, the suction passage 30d is formed in a shape in which the passage cross-sectional area gradually decreases. For this reason, the suction refrigerant passing through the suction passage 30d increases the flow velocity while decreasing its pressure (point h5 → point h′5 in FIG. 5). Thereby, the speed difference between the suction refrigerant and the injection refrigerant can be reduced, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser passage 13c can be reduced.

  In the diffuser passage 13c, the kinetic energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage cross-sectional area. As a result, the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d5 → point e5 in FIG. 5). The refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (point e5 → f5, point e5 → g5 in FIG. 5).

  The liquid-phase refrigerant separated in the gas-liquid separation space 30f is depressurized by the orifice 30i (g5 point → g′5 point in FIG. 5) and flows into the evaporator 14. The refrigerant flowing into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates (g′5 point → h5 point in FIG. 5). Thereby, blowing air is cooled.

  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 f5 → a5 in FIG. 5).

  The ejector refrigeration cycle 10 of the present embodiment operates as described above and can cool the blown air blown into the vehicle interior.

  At this time, in the ejector refrigeration cycle 10 of the present embodiment, the refrigerant whose pressure has been increased in the diffuser passage 13c is sucked into the compressor 11. Therefore, according to the ejector-type refrigeration cycle 10, the power consumption of the compressor 11 can be reduced compared with the normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the refrigerant sucked by the compressor are substantially equal. Coefficient of performance (COP) can be improved.

  Further, according to the ejector 13 of the present embodiment, by turning the refrigerant in the swirling space 30a, the refrigerant pressure on the turning center side in the swirling space 30a is reduced to the pressure that becomes the 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, the energy conversion efficiency in the nozzle passage 13a can be improved by efficiently accelerating the gas-liquid mixed state refrigerant to the sound speed by the boiling promotion by both the wall surface boiling and the interface boiling.

  Further, since the ejector 13 of the present embodiment includes the drive mechanism 37, the passage forming member 35 is displaced in accordance with the load fluctuation of the ejector refrigeration cycle 10, and the passage sectional area (minimum passage area) of the nozzle passage 13a is displaced. The cross-sectional area of the passage at the portion 30m can be adjusted. Thereby, according to the circulation flow rate of the refrigerant | coolant which circulates through a cycle, the passage sectional area in the minimum passage area part 30m can be changed appropriately, and the ejector 13 can be operated appropriately.

  Furthermore, since the passage forming member 35 of the present embodiment has the resin portion (bottom side truncated cone-like member 353), it is possible to reduce the weight as compared with the case where all the portions are formed of metal. Thereby, the resonance frequency of the vibration system including the passage forming member 35 can be set to a relatively high frequency. Therefore, it is possible to prevent the vibration system including the passage forming member 35 from resonating with vehicle vibrations and causing large noises and vibrations.

  Here, as in the ejector 13 of the present embodiment, in the configuration in which the refrigerant swirled in the swirling space 30a and made into a two-phase separated state flows into the nozzle passage 13a, cavitation at the gas-liquid interface and the minimum passage area Cavitation due to reduced pressure occurs in the portion 30m. The refrigerant bubbles generated by the cavitation pass through the minimum passage area 30m at a high speed.

  For this reason, cavitation erosion (erosion) occurs on the outer peripheral surface of the passage forming member 35 (particularly, the outer peripheral surface of the portion forming the minimum passage area portion 30m), and the outer peripheral surface of the passage forming member 35 is damaged or deformed. There is a risk of letting you. And if damage and a deformation | transformation arise in the outer peripheral surface of the channel | path formation member 35, even if the drive mechanism 37 displaces the channel | path formation member 35 according to the load fluctuation | variation of the ejector type refrigeration cycle 10, in the minimum channel | path area part 30m. The passage cross-sectional area cannot be changed appropriately.

  On the other hand, in the ejector 13 of the present embodiment, the top-side conical member 351 is provided as the metal portion, and therefore, the minimum passage area portion 30m of the passage forming member 35 in the outer peripheral surface of the passage forming member 35 is provided. The outer peripheral surface including the site | part which forms can be made into a metal. Therefore, damage and deformation of the portion forming the minimum passage area portion 30m of the passage forming member 35 can be suppressed.

  In addition, since metal generally has a smaller linear expansion coefficient than resin, it is possible to suppress the passage cross-sectional area in the minimum passage area portion 30m from being changed due to a temperature change. Furthermore, it is possible to prevent the portion of the passage forming member 35 that forms the minimum passage area portion 30m from being deformed by a temperature change and biting into the portion of the nozzle body 32 that forms the pressure reducing space 30b.

  Further, in the configuration including the coil spring 40 that applies a load to the passage forming member 35 in order to appropriately displace the passage forming member 35 as in the ejector 13 of the present embodiment, the coil spring 40 of the passage forming member 35 is included. There is a risk of causing damage or deformation in a portion that receives a load from the coil spring 40.

  Then, if damage or deformation occurs in the portion that contacts the coil spring 40 and receives a load, the displacement amount when the drive mechanism 37 displaces the passage forming member 35 changes, and the ejector refrigeration cycle 10 changes. Accordingly, the cross-sectional area of the passage 30m in the minimum passage area 30m cannot be appropriately changed according to the load fluctuation.

  On the other hand, in the ejector 13 of this embodiment, since the annular plate-shaped member 352 is provided as the metal portion, the portion of the passage forming member 35 that contacts the coil spring 40 and receives the load is made of metal. It can be. Accordingly, it is possible to suppress damage and deformation of a portion that receives a load by contacting the coil spring 40 of the passage forming member 35.

  As a result, according to the ejector 13 of the present embodiment, the passage cross-sectional area of the nozzle passage 13a can be adjusted appropriately while reducing the weight of the passage forming member 35. As a result, the ejector 13 can be appropriately operated in accordance with the load fluctuation of the ejector refrigeration cycle 10 while avoiding the vibration system including the passage forming member 35 from resonating with vehicle vibration.

  In the present embodiment, the metal portion (the top-side conical member 351, the annular plate-like member 352) and the resin portion (the bottom-side frustoconical member 353) of the passage forming member 35 are integrally formed by insert molding. Although the example which did was demonstrated, the means to integrate a metal part and a resin part is not limited to this.

  For example, the metal part and the resin part may be integrated by bonding. You may integrate by extending the extension part 351a provided in the top part side cone-shaped member 351 in the bottom part side truncated cone-shaped member 353. FIG.

  Furthermore, as shown in the modified example of FIG. 6, the male screw portion 351 b formed in the extending portion 351 a may be integrated by fastening to the female screw portion formed in the bottom side truncated cone-like member 353. By forming the male screw part 351b in the metal part having a small linear expansion coefficient in this way, it is possible to suppress the occurrence of damage or cracking in the resin part disposed on the outer peripheral side of the male screw part 351b due to temperature change. it can.

  Further, as shown in the modification of FIG. 7, the lower end of the extending portion 351 a (the end opposite to the top-side conical member 351) is projected from the bottom surface of the bottom-side truncated cone-shaped member 353, The inner peripheral side of the annular plate-like member 352 may be fixed by press-fitting into the outer peripheral side of the part. According to this, the metal part and the resin part can be integrated by sandwiching and mixing the bottom-side truncated cone-like member 353 between the bottom surface of the top-side cone-like member 351 and the plate-like member 352.

(Second Embodiment)
This embodiment demonstrates the example which changed the structure of the channel | path formation member 35 with respect to 1st Embodiment. In the passage forming member 35 of the present embodiment, as shown in FIG. 8, a conical member 354 formed in a substantially conical shape is provided as a resin portion. Further, an annular plate-like member 352 similar to that of the first embodiment and a conical cover member 355 that covers the top side surface of the conical member 354 are provided as the metal portion.

  The conical cover member 355 is formed in a hollow conical shape having no bottom surface portion, and is large enough to form an outer surface in the same range as in the first embodiment among the outer surfaces of the passage forming member 35. Is formed. Furthermore, the resin part and the metal part of the present embodiment are formed of the same material as that of the first embodiment, and are integrally formed by insert molding.

  FIG. 8 is a drawing corresponding to FIG. 4 of the first embodiment, and the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals. This also applies to FIGS. 9 and 10 below.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, also in the ejector 13 of this embodiment, the effect similar to 1st Embodiment can be acquired. Further, the metal portion and the resin portion of the present embodiment may be integrated by means such as adhesion, press-fitting, and screw fastening.

(Third embodiment)
In the present embodiment, an example in which the weight is further reduced with respect to the passage forming member 35 of the second embodiment will be described. In the passage forming member 35 of the present embodiment, as shown in FIG. 9, a conical member 354 similar to that of the second embodiment is provided as a resin portion. Furthermore, an annular plate member 352 similar to that of the first embodiment and an annular cover member 356 that covers the top side surface of the conical member 354 are provided as the metal portion.

  The annular cover member 356 is formed in a hollow truncated cone shape having no upper surface portion and no bottom surface portion, and includes an outer peripheral surface including a portion that forms at least the minimum passage area portion 30 m of the outer surface of the passage formation member 35. It is formed in the size which can form. For this reason, as shown in FIG. 9, the top of the passage forming member 35 of the present embodiment has the top of the resin conical member 354 exposed in the decompression space 30b.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the second embodiment. Therefore, also in the ejector 13 of this embodiment, the effect similar to 1st Embodiment can be acquired.

  Furthermore, in this embodiment, since the annular cover member 356 is adopted, the metal portion can be reduced, and the weight of the entire passage forming member 35 can be further reduced. Further, the metal part and the resin part of the present embodiment may be integrated by means such as insert molding, adhesion, press-fitting, and screw fastening.

(Fourth embodiment)
In the present embodiment, an example in which the weight is further reduced with respect to the passage forming member 35 of the second embodiment will be described. In the passage forming member 35 of the present embodiment, as shown in FIG. 10, a conical member 354 similar to that of the second embodiment is provided as a resin portion. Further, an annular plate member 352 similar to that of the first embodiment and a thin film cover member 357 plated so as to cover the conical side surface of the conical member 354 are provided as the metal portion.

  FIG. 10 shows an example in which the thin-film cover portion 357 is formed over substantially the entire conical side surface of the outer peripheral surface of the conical member 354, but at least the minimum passage area portion 30m of the passage forming member 35 is formed. What is necessary is just to be formed in the outer peripheral surface containing the range to do.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the second embodiment. Therefore, also in the ejector 13 of this embodiment, the passage cross-sectional area of the refrigerant passage formed inside can be appropriately adjusted while reducing the weight of the passage forming member 35 as in the first embodiment.

  Further, in the present embodiment, since the thin film cover portion 357 is employed, the metal portion can be reduced, and the weight of the entire passage forming member 35 can be further reduced. In the present embodiment, the thin film cover member 357 is formed by performing metal plating on the conical member 354. However, the thin film cover member 357 may be formed by metal coating.

(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. Further, the means disclosed in each of the above embodiments may be appropriately combined within a practicable range.

  (1) In the above-described embodiment, as a metal part, a metal part (top side conical member 351, each cover member 355) for suppressing damage and deformation of a portion forming the minimum passage area part 30m of the passage forming member 35. 357) and the example in which both the metal portion (annular plate-like member 352) for suppressing damage and deformation of the portion receiving the load by contacting the coil spring 40 of the passage forming member 35 have been described. , Either one may be used.

  (2) In the first embodiment described above, an example in which the extended portion 351a is provided on the top-side conical member 351 has been described. However, if the metal portion and the resin portion can be appropriately joined, the extended portion 351a. Is not a required configuration. Moreover, when providing the extension part 351a, you may press-fit and fix the annular plate-shaped member 352 to the downward side (opposite side conical member 351 side) of the extension part 351a.

  (3) Each component apparatus which comprises the ejector type refrigerating cycle 10 is not limited to what was disclosed by the above-mentioned embodiment.

  For example, in the above-described embodiment, an example in which an electric compressor is employed as the compressor 11 has been described. However, the compressor 11 is driven by a rotational driving force transmitted from a vehicle traveling engine via a pulley, a belt, or the like. An engine driven compressor may be employed. Furthermore, as an engine-driven compressor, a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or by changing the operating rate of the compressor by intermittently connecting an electromagnetic clutch, the refrigerant discharge capacity can be increased. A fixed capacity compressor to be adjusted can be employed.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted the subcool type heat exchanger as the heat radiator 12, you may employ | adopt the normal heat radiator which consists only of the condensation part 12a. In addition to a normal radiator, a receiver-integrated condenser that integrates a receiver (receiver) that separates the gas-liquid of the refrigerant radiated by this radiator and stores excess liquid phase refrigerant is adopted. Also good.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted the drive mechanism 37 as a drive means to which the channel | path formation member 35 of the ejector 13 is displaced, a drive means is not limited to this. For example, you may employ | adopt the thermo wax which changes a volume with temperature as a temperature-sensitive medium. Further, a drive means having a shape memory alloy elastic member may be employed, or a member that displaces the passage forming member 35 by an electric mechanism such as an electric motor or a solenoid. Also good.

  Moreover, although the above-mentioned embodiment demonstrated that R134a or R1234yf etc. were employable as a refrigerant | coolant, a refrigerant | coolant is not limited to this. For example, R600a, R410A, R404A, R32, R1234yfxf, R407C, etc. can be adopted. Or you may employ | adopt the mixed refrigerant | coolant etc. which mixed multiple types among these refrigerant | coolants.

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

  In the above-described embodiment, the radiator 12 of the ejector refrigeration cycle 10 including the ejector 13 according to the present invention is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 14 cools the blown air. Use side heat exchanger. On the other hand, the evaporator 14 may be used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 may be used as a use side heat exchanger that heats a heated fluid such as air or water.

13 Ejector 13a Nozzle passage 30m Minimum passage area 35 Passage forming member 40 Coil spring 351 Top side conical member (metal part)
352 Toroidal plate member (metal part)
353 Bottom-side frustoconical member (resin part)
354 Conical member (resin part)
355 Conical cover member (metal part)
356 Toroidal cover member (metal part)
357 Thin-film cover member (metal part)

Claims (9)

An ejector applied to a vapor compression refrigeration cycle apparatus (10),
A decompression space (30b) for decompressing the refrigerant flowing in from the refrigerant inlet (31a), a suction passage (13b) communicating with the refrigerant flow downstream side of the decompression space (30b) and circulating the refrigerant sucked from the outside ), A body (30) formed with a pressure increasing space (30e) for mixing the refrigerant injected from the pressure reducing space (30b) and the suction refrigerant sucked from the suction passage (13b);
A conical shape in which at least a part is disposed in the decompression space (30b) and in the pressurization space (30e), and the cross-sectional area increases as the distance from the decompression space (30b) increases. A passage forming member (35) formed in
Driving 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 connected to the refrigerant inlet (31a). ) Is a nozzle passage (13a) that functions as a nozzle for depressurizing and injecting the refrigerant flowing in 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 boosting unit that mixes and boosts the refrigerant;
The passage forming member (35) includes metal parts (351, 355, 356, 357) formed of metal and resin parts (353, 354) formed of resin,
The metal portion (351... 357) is an outer peripheral surface of a portion that forms the nozzle passage (13a), and includes an outer peripheral surface that includes at least a portion that forms the minimum passage area portion (30m) of the nozzle passage (13a). Ejector characterized by forming. As the metal part, a top side conical member (351) disposed on the top side of the passage forming member (35) is provided,
The ejector according to claim 1, wherein a bottom side truncated cone-like member (353) disposed on the bottom side of the top side conical member (351) is provided as the resin portion.   The extending portion (351a) extending toward the bottom surface side of the bottom side truncated cone-shaped member (353) is provided on the bottom surface of the top side conical member (351). Ejector as described in. As the resin part, a conical member (354) formed in a conical shape is provided,
The ejector according to claim 1, wherein a cover member (355, 356, 357) that covers at least a part of a side surface of the conical member (354) is provided as the metal portion.   The metal part (351, 351a) and the resin part (353) are fastened to a male screw part (351b) formed in the metal part (351a) and a female screw part provided in the resin part (353, 354). 5. The ejector according to claim 1, wherein the ejector is integrated. An elastic member (40) for applying a load to the passage forming member (35);
The ejector according to any one of claims 1 to 5, wherein the metal portion (352) is disposed at a portion of the passage forming member (35) where the elastic member (40) abuts. . An ejector applied to a vapor compression refrigeration cycle apparatus (10),
A decompression space (30b) for decompressing the refrigerant flowing in from the refrigerant inlet (31a), a suction passage (13b) communicating with the refrigerant flow downstream side of the decompression space (30b) and circulating the refrigerant sucked from the outside ), A body (30) formed with a pressure increasing space (30e) for mixing the refrigerant injected from the pressure reducing space (30b) and the suction refrigerant sucked from the suction passage (13b);
A conical shape in which at least a part is disposed in the decompression space (30b) and in the pressurization space (30e), and the cross-sectional area increases as the distance from the decompression space (30b) increases. A passage forming member (35) formed in
An elastic member (40) for applying a load to 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 connected to the refrigerant inlet (31a). ) Is a nozzle passage (13a) that functions as a nozzle for depressurizing and injecting the refrigerant flowing in 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 boosting unit that mixes and boosts the refrigerant;
The passage forming member (35) has a metal part (352) formed of metal and a resin part (353, 354) formed of resin,
The ejector according to claim 1, wherein the metal portion (352) is disposed at a portion of the passage forming member (35) where the elastic member (40) contacts. The elastic member (40) is a coil spring,
The ejector according to claim 7, wherein the metal part is formed of an annular plate-like member (352).   The body (30) is formed with a swirling space (30a) for swirling the refrigerant flowing from the refrigerant inlet (31a) to flow out to the decompression space (30b) side. Item 10. The ejector according to any one of Items 1 to 8.

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