JP2017053574A - Ejector - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an ejector which can properly change a passage cross section area of a refrigerant passage according to a load variation of an employed refrigeration cycle device.SOLUTION: An ejector 13 has a diaphragm 371 which is displaced according to the pressure of a temperature-sensing medium which is sealed into a sealing space 37a as a drive mechanism 37 which changes a passage cross section area of a refrigerant passage by displacing a passage forming member 35 which forms the refrigerant passage in the ejector. When fixing the drive mechanism 37 to a nozzle body 32, the fixation is performed so that a part of an inner wall face of a suction passage 13b for making an evaporator-outlet side refrigerant circulate is formed at one face of the drive mechanism 37, and a bypass passage 13d for making a part of the evaporator-outlet side refrigerant circulate is formed between the other face and the nozzle body 32. By this constitution, the passage cross section area of the refrigerant passage can be properly changed according to a temperature change of the evaporator-outlet side refrigerant.SELECTED DRAWING: Figure 3

Description

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

  Conventionally, in Patent Document 1, applied to a vapor compression refrigeration cycle apparatus, the refrigerant is decompressed, and the evaporator outlet side refrigerant is sucked from the refrigerant suction port by the suction action of the injected refrigerant injected at a high speed, An ejector is disclosed in which an injection refrigerant and a suction refrigerant (that is, an evaporator outlet side refrigerant) are mixed to increase the pressure.

  In the ejector disclosed in Patent Document 1, a substantially conical passage forming member is disposed inside the body, and an annular refrigerant passage is formed 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 boosting pressure.

  Further, the ejector of Patent Document 1 includes a drive mechanism that changes the passage cross-sectional area of the refrigerant passage by displacing the passage formation member. Thereby, in the ejector of patent document 1, the passage sectional area of the refrigerant passage is changed according to the load fluctuation of the refrigeration cycle apparatus (in other words, fluctuation of the circulating refrigerant flow rate circulating in the cycle), and the ejector is operated appropriately. I am trying to let you.

  More specifically, the drive mechanism of Patent Document 1 is displaced according to a temperature sensing part (encapsulation space forming member) that forms an enclosed space in which the temperature sensitive medium is enclosed, a pressure of the temperature sensitive medium, and the like. It has a diaphragm (pressure responsive member). The passage sectional area of the refrigerant passage is changed by transmitting the displacement of the diaphragm to the passage forming member.

  The drive mechanism is formed in an annular shape, and is fixed inside the body so that the surface on one side in the axial direction forms part of the inner wall surface of the suction passage. The suction passage is a refrigerant passage through which the suction refrigerant sucked from the refrigerant suction port is circulated. Thereby, in the ejector of patent document 1, the heat which an evaporator exit side refrigerant | coolant has is transmitted to a temperature-sensitive medium, and it is going to change the passage cross-sectional area of a refrigerant path according to the temperature of an evaporator exit side refrigerant | coolant.

JP 2015-45493 A

  However, when the drive mechanism is fixed inside the body as in the ejector of Patent Document 1, the heat of the refrigerant other than the evaporator outlet side refrigerant flowing through the suction passage through the body is contained in the enclosed space. It will be transmitted to the temperature sensitive medium. For example, the heat of the high-temperature and high-pressure refrigerant flowing into the upstream side of the nozzle passage is transferred to the temperature-sensitive medium via the body.

  Therefore, in the ejector of patent document 1, there exists a possibility that the passage cross-sectional area of a refrigerant passage cannot be changed appropriately according to the circulating refrigerant flow rate.

  In view of the above points, an object of the present invention is to provide an ejector that can appropriately change the cross-sectional area of the refrigerant passage in accordance with the load fluctuation of the applied refrigeration cycle apparatus.

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) that decompresses the refrigerant, a suction passage (13b) that communicates with the downstream side of the refrigerant flow in the decompression space (30b) and distributes the refrigerant sucked from the refrigerant suction port (31b), and a decompression space A body (30) having a pressure increasing space (30e) into which the injected refrigerant injected from (30b) and the suction refrigerant sucked through the suction passage (13b) flow, and at least a part of which is for decompression A passage forming member (35) disposed in the space (30b) and in the pressure increasing space (30e) and having a conical shape whose outer diameter increases with distance from the pressure reducing space (30b). And a drive mechanism (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) serves as a nozzle that decompresses and injects the refrigerant. The functioning nozzle passage (13a) is a 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). , A diffuser passage (13c) that functions as a boosting unit that boosts the pressure by mixing the injected refrigerant and the suction refrigerant,
The drive mechanism (37) includes a pressure responsive member (371) that deforms according to the pressure in the enclosed space (37a) in which a temperature-sensitive medium that changes in pressure with temperature change is enclosed, and the suction passage (13b). ) Is fixed to the body (30) so as to form a part of the inner wall surface, and further, a bypass passage through which a part of the suction refrigerant flows between the drive mechanism (37) and the body (30). (13d) is formed.

  According to this, since the drive mechanism (37) is fixed to the body (30) so as to form a part of the inner wall surface of the suction passage (13b), the heat of the suction refrigerant is contained in the enclosed space (37a). It can be transmitted to the temperature sensitive medium. Furthermore, since the bypass passage (13d) is formed between the drive mechanism (37) and the body (30), the heat of the refrigerant other than the suction refrigerant is reduced by the refrigerant flowing through the bypass passage (13d). Transmission to the temperature sensitive medium via (30) can be suppressed.

  Therefore, the temperature and pressure of the temperature sensitive medium can be accurately changed according to the temperature of the suction refrigerant. As a result, by transmitting the displacement of the pressure responsive member (371) to the passage forming member (35), the passage sectional area of the nozzle passage (13a) and the diffuser passage ( The passage sectional area of 13c) can be appropriately changed.

  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 a typical expanded sectional view for explaining each refrigerant passage and drive mechanism of the ejector of a 1st embodiment. It is IV-IV sectional drawing of FIG. 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 typical sectional drawing for demonstrating the bypass passage of the ejector of 2nd Embodiment. It is typical sectional drawing for demonstrating the bypass passage of the ejector of 3rd Embodiment. It is typical sectional drawing for demonstrating the bypass channel and drive mechanism of the ejector of 4th Embodiment. It is typical sectional drawing for demonstrating the bypass channel and drive mechanism of the ejector of 5th Embodiment. It is typical sectional drawing for demonstrating the bypass channel and drive mechanism of the ejector of 6th 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 blown air that is blown into a vehicle interior that is a space to be air-conditioned. Therefore, the cooling target fluid of the ejector refrigeration cycle 10 of the present embodiment is blown air.

  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.

  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. The compressor 11 according to the present embodiment is disposed in an engine room together with an engine (internal combustion engine) that outputs a driving force for vehicle travel. Further, the compressor 11 is an engine-driven compressor that is driven by a rotational driving force output from the engine via a pulley, a belt, or the like.

  More specifically, in the present embodiment, a swash plate type variable displacement compressor configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity is employed as the compressor 11. The compressor 11 has a discharge capacity control valve (not shown) for changing the discharge capacity. The operation of the discharge capacity control valve is controlled by a control current output from a control device described later.

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

  More specifically, the radiator 12 is configured as a so-called subcool type condenser having a condensing unit 12a, a receiver unit 12b, and a supercooling unit 12c.

  The condensing unit 12a is a heat exchanging 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, and dissipates the high-pressure gas-phase refrigerant to condense. The receiver unit 12b is a refrigerant container that separates the gas-liquid refrigerant flowing out of the condensing unit 12a and supplies the excess liquid-phase refrigerant. The supercooling unit 12c is a heat exchanging unit that heat-exchanges the liquid refrigerant flowing out from the receiver unit 12b and the outside air blown from the cooling fan 12d to supercool the liquid refrigerant.

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

  The ejector 13 functions as a refrigerant 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 this embodiment is configured as an ejector with a gas-liquid separation function (that is, an 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 partial enlarged cross-sectional view for explaining the function of each refrigerant passage of the ejector 13 and a drive mechanism 37 to be described later. The code is attached.

  As shown in FIG. 2, the ejector 13 of the present embodiment includes a body 30 configured by combining a plurality of constituent members.

  More specifically, the body 30 has a housing body 31 that is formed of a prismatic or cylindrical metal member or resin member and forms the outer shell of the ejector 13. Furthermore, a substantially cylindrical space is formed in the housing body 31. The nozzle body 32 and the diffuser body 33 are fixed in this space.

  The housing body 31 is formed with a plurality of refrigerant inlets and outlets such as a refrigerant inlet 31a, a refrigerant suction port 31b, a liquid phase refrigerant outlet 31c, and a gas phase refrigerant outlet 31d.

  The refrigerant inlet 31a is a refrigerant inlet through which the refrigerant that has flowed out of the radiator 12 flows. The refrigerant suction port 31b is a refrigerant inflow port that sucks the refrigerant that has flowed out of the evaporator 14 described later. The liquid-phase refrigerant outlet 31 c is a refrigerant outlet that allows the liquid-phase refrigerant separated in the gas-liquid separation space 30 f formed inside the body 30 to flow out to the refrigerant inlet side of the evaporator 14. The gas-phase refrigerant outlet 31d is a refrigerant outlet through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out to the suction port side of the compressor 11.

  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. .

  Next, as shown in FIG. 2, the nozzle body 32 is disposed on the upper side inside the housing body 31. The nozzle body 32 is formed of an annular metal member. More specifically, the nozzle body 32 is formed in a large diameter portion 32a having a diameter approximately equal to the inner diameter of the substantially columnar space formed in the housing body 31, and a cylindrical shape having a smaller diameter than the large diameter portion 32a. The formed small diameter portion 32b is coaxially coupled.

  Further, the nozzle body 32 is fixed to the housing body 31 by press-fitting the outer peripheral side of the large diameter portion 32 a into the housing body 31. Note that an O-ring as a seal member is disposed between the large diameter portion 32a and the housing body 31, and the refrigerant does not leak from the gap between the large diameter portion 32a and the housing body 31.

  A swirling space 30a for swirling the refrigerant flowing from the refrigerant inflow port 31a is formed inside the large diameter portion 32a. A disk-shaped metal plate 32c is disposed above the large-diameter portion 32a, and the opening on the upper side of the swirling space 30a is closed by the metal plate 32c.

  The swirling space 30a is formed in a substantially columnar shape, and the central axis of the swirling space 30a is arranged coaxially with a central axis CL of a passage forming member 35 described later. Of course, the swirl space 30a may be formed in the shape of a rotating body in which a truncated cone and a cylinder are combined. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (center axis) on the same plane.

  The refrigerant inflow passage 31e that connects the refrigerant inlet 31a and the swirl space 30a allows the refrigerant that flows into the swirl space 30a when viewed from the central axis direction of the swirl space 30a to flow along the inner wall surface of the swirl space 30a. It is formed as follows. Thereby, the refrigerant that has flowed into the swirl space 30a from the refrigerant inflow passage 31e 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.

  In addition, a decompression space 30b is formed in the small diameter portion 32b to decompress the refrigerant that has flowed out of the swirling space 30a and to flow it downstream. The decompression space 30b is formed in a rotating body shape in which the top sides of two frustoconical spaces are joined together. The central axis of the decompression space 30b is also arranged coaxially with the central axis CL of the passage forming member 35.

  The top side of the passage forming member 35 is disposed inside the decompression space 30b. The passage forming member 35 functions to change the passage cross-sectional area of the refrigerant passage by forming a refrigerant passage in the body 30 and displacing in the central axis CL direction.

  More specifically, the passage forming member 35 is formed of a resin conical member. The central axis of the passage forming member 35 is arranged coaxially with the central axis of the swirling space 30a or the decompression space 30b. For this reason, the passage forming member 35 is formed in a substantially conical shape in which the outer diameter gradually increases with distance from the decompression space 30b (that is, toward the downstream side of the refrigerant flow).

  Further, as a refrigerant passage formed between the inner peripheral surface of the part forming the pressure reducing space 30b of the nozzle body 32 and the outer peripheral surface on the top side (that is, the upper side in the vertical direction) of the passage forming member 35, FIG. As shown in FIG. 2, a tapered portion 131 and a divergent portion 132 are formed.

  The tapered portion 131 is a refrigerant passage that is formed on the upstream side of the refrigerant flow with respect to the smallest passage area portion 30m having the smallest passage cross-sectional area and gradually reduces the passage cross-sectional area up to the smallest passage area portion 30m. 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 (that is, circular). To a donut shape excluding a small-diameter circular shape arranged coaxially). 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 with such a passage shape is the nozzle passage 13a that functions as a Laval nozzle. In the nozzle passage 13a, the pressure of the refrigerant is reduced, and the flow rate of the refrigerant is increased to be supersonic and injected.

  Further, on the bottom surface side of the large diameter portion 32a of the nozzle body 32 and on the outer peripheral side of the small diameter portion 32b, an annular groove portion 32d for accommodating the drive mechanism 37 is formed while forming a bypass passage 13d. Yes. The detailed configuration of the bypass passage 13d and the drive mechanism 37 will be described later.

  Next, the diffuser body 33 is formed of a substantially cylindrical metal member. Further, as shown in FIG. 2, the diffuser body 33 is disposed inside the housing body 31 and below the nozzle body 32. A through hole 33 a is formed in the center of the diffuser body 33 so as to penetrate the front and back (up and down). The through hole 33 a is also formed in a rotating body shape, and its central axis is arranged coaxially with the central axis CL of the passage forming member 35.

  Further, the diffuser body 33 is fixed to the housing body 31 by press-fitting the outer peripheral side thereof into the housing body 31. Note that an O-ring as a seal member is disposed between the diffuser body 33 and the housing body 31, and the refrigerant does not leak from the gap between the diffuser body 33 and the housing body 31.

  A suction space 30c is formed between the upper surface of the diffuser body 33 and the bottom surface of the large-diameter portion 32a of the nozzle body 32 opposite to the diffuser body 33, into which the refrigerant sucked from the refrigerant suction port 31b flows. In the present embodiment, since the lower end portion of the small diameter portion 32b of the nozzle body 32 extends to the inside of the through hole 33a of the diffuser body 33, the suction space 30c has an annular cross section when viewed from the central axis direction. It is formed.

  Further, a suction passage 30d is formed between the inner peripheral surface of the through-hole 33a and the outer peripheral surface of the lower end portion of the small diameter portion 32b to connect the suction space 30c and the downstream side of the refrigerant flow in the decompression space 30b. The Therefore, in the present embodiment, as shown in FIG. 3, the cross-sectional annular shape in which the suctioned refrigerant (the evaporator 14 outlet-side refrigerant described later) is circulated by the suction space 30 c and the suction passage 30 d. A suction passage 13b is formed.

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

  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 diffuser body 33 forming the pressurizing space 30e and the lower outer peripheral surface of the passage forming member 35 has a passage cross-sectional area toward the downstream side of the refrigerant flow. It is formed in 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, in the present embodiment, as shown in FIG. 3, a refrigerant passage formed between the inner peripheral surface of the diffuser body 33 that forms the pressurizing space 30 e and the outer peripheral surface on the lower side of the passage forming member 35, The diffuser passage 13c functions as a diffuser (a pressure-increasing part) that increases the pressure by mixing the injected refrigerant and the suction refrigerant. The cross-sectional shape perpendicular to the central axis of the diffuser passage 13c is also formed in an annular shape.

  Next, a drive mechanism 37 that is a drive means for displacing the passage forming member 35 will be described. As shown in FIG. 3, the drive mechanism 37 of this embodiment includes a diaphragm 371, an upper cap 372, a lower cap 373, and the like. The diaphragm 371, the upper cap 372, and the lower cap 373 are all formed in an annular shape that is large enough to overlap with the groove 32 d formed in the nozzle body 21 when viewed from the central axis CL direction.

  The upper cap 372 is a sealed space forming member that forms the sealed space 37 a together with the diaphragm 371. More specifically, the upper cap 372 is formed by forming an annular recess on the surface of the flat plate annular metal member on the diaphragm 371 side (lower side in FIG. 3). An enclosed space 37a is formed inside the recess. For this reason, the enclosed space 37a is formed in an annular shape around the central axis CL.

  The enclosed space 37a is a space in which a temperature-sensitive medium whose pressure changes with a change in temperature is enclosed. More specifically, it is a space in which a temperature sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed. Therefore, a medium mainly composed of R134a (for example, a mixed medium of R134a and helium) can be employed as the temperature sensitive medium of the present embodiment. Further, the density of the temperature sensitive medium is set so that the passage forming member 35 can be appropriately displaced during the normal operation of the cycle, as will be described later.

  The lower cap 373 is formed by providing a step portion on one end side (the lower side in FIG. 3) of the cylindrical metal member. Then, by fitting the upper cap 372 and the diaphragm 371 inside, it functions as a fixing member that fixes the outer end and the inner end of the diaphragm 371 together with the upper cap 372.

  The diaphragm 371 is a pressure responsive member that is displaced according to the pressure difference between the internal pressure of the enclosed space 37a and the pressure of the suction refrigerant flowing through the suction passage 13d (specifically, the suction space 30c). Accordingly, it is desirable that the diaphragm 371 is made of a material that is rich in elasticity and excellent in pressure resistance and airtightness.

  As such a diaphragm 371, what was formed with rubber | gum base materials, such as EPDM (ethylene propylene diene rubber) and HNBR (hydrogenated nitrile rubber) containing a base fabric (polyester), for example is employable. .

  As shown in FIG. 3, a plate member 375 and a plurality of operating rods 374 for transmitting the displacement of the diaphragm 371 to the passage forming member 35 are disposed on the lower side of the diaphragm 371. The plate member 375 is formed of a flat plate metal member. The plate member 375 is disposed so as to contact the lower surface of the diaphragm 371.

  The plurality of actuating rods 374 serve as a connecting portion that connects the diaphragm 371 and the passage forming member 35 and are formed of a cylindrical metal member extending in the direction of the central axis CL. The plurality of actuating rods 374 are inserted into through holes formed in the lower cap 373 and the diffuser body 33 and extending in the direction of the central axis CL.

  An O-ring as a seal member is disposed in the gap between the operating rod 374 and the through hole in which the diffuser body 33 is formed, and the refrigerant does not leak from the gap between the operating rod 374 and the through hole.

  Further, both end portions of the plurality of actuating rods 374 are processed into a spherical shape, the upper end portion is in contact with the bottom surface of the plate 375, and the lower end portion is on the downstream side of the diffuser passage 13c of the passage forming member 35. It is in contact with the surface forming the part. Accordingly, the displacement of the diaphragm 371 is transmitted to the passage forming member 35 via the plate 375 and the plurality of operating rods 374.

  The plurality of actuating rods 374 are desirably arranged at equiangular intervals around the central axis CL in order to appropriately transmit the displacement of the diaphragm 371 to the passage forming member 35. In FIGS. 1 to 3 and the like, an example in which two operating rods 374 are arranged around the central axis CL at intervals of 180 ° is shown for clarity of illustration, but the three operating rods 374 are illustrated. You may arrange | position at 120 degree intervals around the central axis CL.

  In this embodiment, as shown in FIGS. 2 and 3, the upper cap 372 and the lower cap 373 sandwiching the diaphragm 371 are fixed in the groove 32 d of the nozzle body 32 by means such as press fitting or caulking. Thus, the drive mechanism 37 is formed.

  For this reason, the bottom surface of the drive mechanism 37 (specifically, the bottom surface of the diaphragm 371 and the bottom surface of the plate member 375) forms a part of the inner wall surface of the suction space 30c. Therefore, the heat of the refrigerant flowing through the suction passage 13b (specifically, the suction space 30c) is transmitted to the temperature-sensitive medium enclosed in the enclosed space 37a via the diaphragm 371 and the plate member 375. .

  2 and 3, the bottom surface of the passage forming member 35 receives a load of a coil spring 40 supported by a support member 41 described later. The coil spring 40 is an elastic member that applies a load that biases the passage forming member 35 upward (the passage forming member 35 reduces the passage cross-sectional area of the minimum passage area 30m). Therefore, the passage forming member 35 is displaced so that the load received from the operating rod 374 and the load received from the coil spring 40 are balanced.

  More specifically, when the temperature (superheat degree) of the refrigerant on the outlet side of the evaporator 14 rises, the saturation pressure of the temperature-sensitive medium enclosed in the enclosed space 37a rises, and the suction passage 13b is changed from the internal pressure of the enclosed space 37a. The pressure difference obtained by subtracting the pressure of the circulating refrigerant increases. As a result, the diaphragm 371 is displaced toward the suction passage 13b, and the load that the passage forming member 35 receives from the operating rod 374 increases.

  For this reason, when the temperature (superheat degree) of the evaporator 14 outlet side refrigerant | coolant rises, the channel | path formation member 35 will be displaced to the direction (in FIG. 2, lower side) which expands 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 37a is lowered, and the refrigerant flowing through the suction passage 13b from the internal pressure of the enclosed space 37a is reduced. The pressure difference after subtracting the pressure becomes smaller. As a result, the diaphragm 371 is displaced toward the enclosed space 37a, and the load that the passage forming member 35 receives from the operating rod 374 decreases.

  For this reason, when the temperature (superheat degree) of the evaporator 14 outlet side refrigerant | coolant falls, the channel | path formation member 35 will be displaced in the direction (in FIG. 2, upper side) which reduces the channel | path cross-sectional area in the minimum channel | path area part 30m.

  In the drive mechanism 37 of the present embodiment, the passage forming member 35 is displaced according to the degree of superheat of the evaporator 14 outlet-side refrigerant in this way, whereby the degree of superheat of the evaporator 14 outlet-side refrigerant is determined in advance as a reference superheat degree. The passage cross-sectional area in the minimum passage area portion 30m is adjusted so as to approach KSH.

  Further, a part of the suction refrigerant (that is, the refrigerant on the outlet side of the evaporator 14) is circulated between the upper surface of the drive mechanism 37 (specifically, the upper surface of the upper cap 372) and the bottom surface of the groove portion 32d of the nozzle body 32. A bypass passage 13d is formed. As shown in the cross-sectional view of FIG. 4, the bypass passage 13 d is formed in an annular shape that overlaps with the drive mechanism 37 when viewed from the direction of the central axis CL. An inlet hole 13e, which is an inlet portion of the bypass passage 13d, and an outlet hole 13f, which is an outlet portion, are arranged with respect to the central axis CL.

  Furthermore, an inlet tube 42 that is a tubular member protruding into the suction passage 13b is connected to the inlet hole 13e of the bypass passage 13d formed in the body 30 (specifically, the nozzle body 32). The leading end of the introduction pipe 42 on the refrigerant inlet 42a side is bent toward the refrigerant suction port 31b. For this reason, the refrigerant inlet 42a of the introduction pipe 42 is opened so as to oppose the flow direction of the suction refrigerant. In other words, the refrigerant inlet 42a of the introduction pipe 42 opens toward the refrigerant suction port 31b.

  Next, in the space formed inside the housing body 31, on the lower side of the passage forming member 35, as shown in FIG. 2, a gas-liquid separation space that separates the gas-liquid refrigerant flowing out from the diffuser passage 13 c. 30f 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 axis CL of the passage forming member 35.

  Further, in the gas-liquid separation space 30f, the refrigerant flowing out from the diffuser passage 13c is swung around the central axis CL, and the gas-liquid refrigerant is separated by the action of centrifugal force. Further, the internal volume of the gas-liquid separation space 30f is a volume that cannot substantially store excess refrigerant even when a load fluctuation occurs in the cycle and the refrigerant circulation flow rate circulating in the cycle fluctuates. .

  At the center of the gas-liquid separation space 30f, there is provided a cylindrical pipe 31f that is arranged coaxially with the gas-liquid separation space 30f and extends upward. The liquid phase refrigerant separated in the gas-liquid separation space 30f temporarily stays on the outer peripheral side of the pipe 31f and flows out from the liquid phase refrigerant outlet 31c.

  A gas-phase refrigerant outflow passage 31g 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 31f. Furthermore, a support member 41 that supports the coil spring 40 described above is disposed inside the pipe 31f.

  The coil spring 40 also functions as a vibration buffer member that attenuates vibration of the passage forming member 35 caused by pressure pulsation when the refrigerant is depressurized. Further, the support member 41 is connected to an adjustment screw 41a that displaces the support member 41 in the central axis direction (vertical direction). Therefore, the target reference superheat degree KSH can be changed by adjusting the load that the coil spring 40 urges against the passage forming member 35 with the adjusting screw 41a.

  Next, 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 a control program stored in the ROM. Then, the operation of the above-described various electric actuators 11, 12d, 14a and the like is controlled.

  The control device is connected to a plurality of air conditioning control sensor groups such as an inside air temperature sensor, an outside air temperature sensor, a solar radiation sensor, an evaporator temperature sensor, an outlet side temperature sensor, and an outlet side pressure sensor. The detected value is input.

  More specifically, the inside air temperature sensor is an inside air temperature detecting means for detecting the temperature inside the vehicle. The outside air temperature sensor is outside air temperature detecting means for detecting outside air temperature. The solar radiation sensor is a solar radiation amount detecting means for detecting the amount of solar radiation in the passenger compartment. The evaporator temperature sensor is an evaporator temperature detecting means for detecting the temperature of the blown air (evaporator temperature) of the evaporator 14. The outlet side temperature sensor is outlet side temperature detecting means for detecting the temperature of the radiator 12 outlet side refrigerant. The outlet-side pressure sensor is outlet-side pressure detection means that detects the pressure of the radiator 12 outlet-side refrigerant.

  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 which controls the refrigerant | coolant discharge capability of the compressor 11 by controlling the action | operation of the discharge capacity control valve of the compressor 11 comprises the discharge capability control means. Of course, the discharge capacity control means may be configured as a separate control device with respect to the control device.

  Next, the operation of the present embodiment in the above configuration will be described using the Mollier diagram of FIG. First, when the operation switch of the operation panel is turned on (ON), the control device operates the electric motor 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 a in FIG. 5) discharged from the compressor 11 flows into the condenser 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, and dissipates heat to condense. The refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid phase refrigerant separated from the gas and liquid by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d by the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a in FIG. 5). Point → b).

  The supercooled liquid-phase refrigerant that has flowed out of the supercooling portion 12c of the radiator 12 passes through the nozzle passage 13a formed between the inner peripheral surface of the decompression space 30b of the ejector 13 and the outer peripheral surface of the passage forming member 35. The pressure is reduced entropically and injected (point b → point c in FIG. 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 superheat degree of the evaporator 14 outlet side refrigerant (point h in FIG. 5) approaches the reference superheat degree KSH.

  Then, the refrigerant (point h in FIG. 5) that has flowed out of the evaporator 14 by 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 suction 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 13b and the like flow into the diffuser passage 13c and merge (point c → d, point h1 → d in FIG. 5). .

  Here, the suction passage 13b of the present embodiment is formed in a shape in which the passage cross-sectional area gradually decreases in the refrigerant flow direction. For this reason, the suction refrigerant passing through the suction passage 13b increases the flow velocity while decreasing the pressure (point h → point h1 in FIG. 5). Thereby, the speed difference between the suction refrigerant and the injection refrigerant is reduced, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser passage 13c is reduced.

  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 d → point e in FIG. 5). The refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (e point → f point, e point → g point in FIG. 5).

  The liquid-phase refrigerant separated in the gas-liquid separation space 30f is decompressed by the orifice 30i (point g → point g1 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 (g1 point → h 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 from the gas-phase refrigerant outlet 31d, is sucked into the compressor 11, and is compressed again (point f → a 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.

  In the ejector refrigeration cycle 10 of this 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 portion 30m) and the cross-sectional area of the diffuser passage 13c can be adjusted. Thereby, according to the circulation flow rate of the refrigerant | coolant which circulates through a cycle, the passage sectional area etc. in the minimum passage area part 30m can be changed appropriately, and the ejector 13 can be operated appropriately.

  In the ejector 13 of the present embodiment, the drive mechanism 37 is fixed inside the body 30, and the bottom surface of the drive mechanism 37 forms a part of the inner wall surface of the suction space 30 c. Therefore, the temperature sensitive medium in the enclosed space 37a is not easily affected by the outside air temperature, and the heat of the suction refrigerant is easily transmitted to the temperature sensitive medium.

  On the other hand, a refrigerant (for example, a high-temperature and high-pressure refrigerant flowing into the nozzle passage 13a) other than the evaporator 14 outlet-side refrigerant (suction refrigerant) is provided via the metal body 30 (specifically, the nozzle body 32). Heat may be transferred to the temperature-sensitive medium in the enclosed space 37a.

  If such heat transfer occurs, the temperature of the temperature sensitive medium becomes a value different from the temperature of the refrigerant on the outlet side of the evaporator 14, so that the nozzle passage 13 a and The passage cross-sectional area of the diffuser passage 13c cannot be changed appropriately.

  On the other hand, in the ejector 13 of the present embodiment, a bypass passage 13d is formed between the upper surface of the drive mechanism 37 and the bottom surface of the groove 32d of the nozzle body 32. Therefore, the suction refrigerant flowing through the bypass passage 13d prevents the heat of the refrigerant other than the suction refrigerant from being transmitted to the temperature sensitive medium via the body 30 (specifically, the nozzle body 32). it can.

  Therefore, the temperature and pressure of the temperature sensitive medium can be accurately changed according to the temperature of the suction refrigerant. As a result, the passage cross-sectional areas of the nozzle passage 13a and the diffuser passage 13c can be appropriately changed according to the load fluctuation of the ejector refrigeration cycle 10.

  Further, in the ejector 13 of the present embodiment, the introduction pipe 42 is connected to the inlet hole 13e of the bypass passage 13d, and the refrigerant inlet 42a of the introduction pipe 42 opens toward the refrigerant suction port 31b. According to this, a part of the suction refrigerant can surely flow into the bypass passage 13d using the dynamic pressure of the suction refrigerant flowing into the suction passage 13b via the refrigerant suction port 31b.

  Moreover, in the ejector 13 of this embodiment, since the inlet hole 13e of the bypass passage 13d is formed in the nozzle body 32, the introduction pipe 42 can be easily connected to the bypass passage 13d.

  Further, in the ejector 13 of the present embodiment, the inlet hole 13e and the outlet hole 13f of the bypass passage 13d are arranged with respect to the central axis CL as viewed from the direction of the central axis CL.

  Therefore, the suction refrigerant flowing into the bypass passage 13d does not flow in any way, and is evenly distributed over substantially the entire upper surface of the drive mechanism 37 as shown by the thick solid arrow in FIG. Flowing. Thereby, it can suppress favorably that the heat which refrigerant | coolants other than an attraction | suction refrigerant | coolant have via the nozzle body 32 will be transmitted to a temperature sensitive medium.

(Second Embodiment)
This embodiment demonstrates the example which changed the arrangement | positioning aspect of the exit hole 13f of the bypass passage 13d as shown in FIG. 6 with respect to 1st Embodiment. FIG. 6 is a schematic cross-sectional view corresponding to FIG. 4 described in the first embodiment. In FIG. 6, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  More specifically, the outlet holes 13f of the present embodiment are provided at a plurality of (specifically, three) locations. By changing the cross-sectional area of each outlet hole 13f, the outlet holes 13f of FIG. As indicated by the thick solid arrow, the suction refrigerant flowing into the bypass passage 13d is made to flow evenly over substantially the entire upper surface of the drive mechanism 37.

  The plurality of outlet holes 13f of the present embodiment are arranged at equiangular intervals when viewed from the direction of the central axis CL. Further, the inlet hole 13e and the outlet hole 13f farthest from the inlet hole 13e are arranged on the object with respect to the central axis CL, as in the first embodiment. The passage sectional area of the outlet hole 13f farthest from the inlet hole 13e is formed larger than the passage sectional area of the other outlet holes 13f.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, according to the ejector refrigeration cycle 10 of the present embodiment, COP can be improved as in the first embodiment. Further, according to the ejector 13 of the present embodiment, the passage sectional area of the refrigerant passage can be appropriately changed according to the load fluctuation of the ejector refrigeration cycle 10 as in the first embodiment.

(Third embodiment)
In the present embodiment, an example in which the shape of the bypass passage 13d is changed as shown in FIG. 7 with respect to the first embodiment will be described. FIG. 7 is a schematic cross-sectional view corresponding to FIG. 4 described in the first embodiment.

  More specifically, the bypass passage 13d of the present embodiment is formed in an arc shape that overlaps with the drive mechanism 37 when viewed from the central axis CL direction. And the inlet hole 13e is arrange | positioned at the circumferential direction one end side of the bypass channel 13d. Further, the outlet hole 13f is disposed on the other circumferential end side of the bypass passage 13d. Accordingly, in the present embodiment, as indicated by a thick solid arrow in FIG. 7, the suction refrigerant that has flowed into the bypass passage 13 d flows in an arc shape over substantially the entire upper surface of the drive mechanism 37.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 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 first embodiment can be obtained.

(Fourth embodiment)
In the present embodiment, as shown in FIG. 8, the outer diameter of the drive mechanism 37 is enlarged, and the inlet hole 13 e and the outlet hole 13 f of the bypass passage 13 d are provided in the lower cap 373 of the drive mechanism 37 as compared with the first embodiment. The formed example will be described. FIG. 8 is a schematic cross-sectional view corresponding to FIG. 3 described in the first embodiment.

  For this reason, the introduction pipe 42 of this embodiment is fixed to the lower cap 373. Further, in the present embodiment, the introduction pipe 42 is made of a material having a higher thermal conductivity (specifically, a nanocarbon tube or copper) than at least the rubber diaphragm 371.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 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 first embodiment can be obtained.

  Moreover, in the ejector 13 of this embodiment, since the inlet hole 13e is formed in the lower cap 373, the heat | fever which the evaporator 14 exit side refrigerant | coolant which distribute | circulates the inlet hole 13e has is easy to be transmitted to a temperature sensitive medium. Furthermore, since the introduction pipe 42 made of a material having a relatively high thermal conductivity is connected to the inlet hole 13e provided in the lower cap 373, the introduction pipe 42 is made to function as a temperature sensitive cylinder, and the evaporator It becomes easy to transmit the heat which 14th exit side refrigerant | coolant has to a temperature sensitive medium. As a result, the passage sectional area of the refrigerant passage can be changed more appropriately.

(Fifth embodiment)
In the present embodiment, as shown in FIG. 9, the inner diameter of the drive mechanism 37 is enlarged, and the inlet hole 13 e of the bypass passage 13 d is placed on the inner peripheral side of the enclosed space 37 a in the lower cap 373 as shown in FIG. 9. The example formed in the site | part is demonstrated. FIG. 9 is a schematic cross-sectional view corresponding to FIG. 3 described in the first embodiment.

  Further, in the present embodiment, a slit groove 32f that is recessed in the direction of the central axis CL from the bypass passage 13d side is formed in a portion of the lower cap 373 on the outer peripheral side of the enclosed space 37a. The slit groove 32f forms a space into which the evaporator 14 outlet-side refrigerant that has flowed into the bypass passage 13d flows, and is formed in an annular shape when viewed from the direction of the central axis CL.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the fourth embodiment. Therefore, according to the ejector 13 of the present embodiment, the same effect as that of the fourth embodiment can be obtained.

  Further, in the ejector 13 of the present embodiment, the slit groove 32f is formed in an annular shape on the outer peripheral side of the enclosed space 37a. Therefore, it is possible to more effectively suppress the heat of the refrigerant other than the suction refrigerant from being transferred to the temperature-sensitive medium through the body 30 by the suction refrigerant flowing into the slit groove 32f. As a result, the passage sectional area of the refrigerant passage can be changed more appropriately.

(Sixth embodiment)
In the present embodiment, an example in which the arrangement of the drive mechanism 37 is changed as shown in FIG. 10 with respect to the first embodiment will be described. FIG. 10 is a schematic cross-sectional view corresponding to FIG. 3 described in the first embodiment.

  More specifically, in this embodiment, the groove part 32d formed in the nozzle body 32 is abolished. In addition, a bypass passage 13 d is formed on the upper surface of the diffuser body 33 (that is, the surface facing the nozzle body 32), and an annular groove 33 c for accommodating the drive mechanism 37 is formed.

  Furthermore, in this embodiment, as shown in FIG. 10, by fixing the upper cap 372 and the lower cap 373 with the diaphragm 371 sandwiched in the groove portion 33c of the diffuser body 33 by means such as press fitting or caulking. A drive mechanism 37 is formed.

  For this reason, the upper surface of the drive mechanism 37 (specifically, the upper surface of the upper cap 372) forms part of the inner wall surface of the suction space 30c. Therefore, the heat of the refrigerant flowing through the suction passage 13b (specifically, the suction space 30c) is transmitted to the temperature-sensitive medium enclosed in the enclosed space 37a via the upper cap 372.

  In the present embodiment, a bypass passage 13d is formed between the bottom surface of the drive mechanism 37 (specifically, the bottom surface of the diaphragm 371 and the bottom surface of the plate member 375) and the bottom surface of the groove 33c of the diffuser body 33. Yes.

  The diffuser body 33 is formed with the same inlet hole 13e and outlet hole 13f as in the first embodiment. An inlet pipe 42 similar to that in the first embodiment is connected to the inlet hole 13e. Accordingly, the introduction pipe 42 of the present embodiment extends from the lower side to the upper side and protrudes into the suction passage 13b.

  Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, according to the ejector 13 and the ejector refrigeration cycle 10 of the present embodiment, the same effects as those of the first embodiment can be obtained.

  That is, in the ejector 13 of the present embodiment, the bypass passage 13 d is formed between the bottom surface of the drive mechanism 37 and the bottom surface of the groove portion 33 c of the diffuser body 33. Therefore, the suction refrigerant flowing through the bypass passage 13d prevents the heat of the refrigerant other than the suction refrigerant from being transmitted to the temperature-sensitive medium via the body 30 (specifically, the diffuser body 33). Can do.

(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) The means disclosed in each of the above embodiments may be appropriately combined within a practicable range. For example, the outlet hole 13f and the bypass passage 13d described in the second and third embodiments may be applied to the ejector described in the fourth to sixth embodiments. For example, the diffuser body 33 of the ejector 13 described in the sixth embodiment may be provided with a slit groove that performs the same function as the slit groove 32f described in the fifth embodiment.

  (2) The shape of the slit groove 32f described in the fifth embodiment is not limited to the shape recessed in the central axis CL direction. As long as it can suppress that the heat | fever which refrigerant | coolants other than a suction refrigerant | coolant has transmitted to a temperature-sensitive medium via the body 30 may be formed in a part of circumference | surroundings of the enclosure space 37a.

  (3) The configuration of the ejector 13 is not limited to that disclosed in the above-described embodiment.

  For example, the pressure responsive member is not limited to the rubber diaphragm 371. You may employ | adopt the metal diaphragm formed with the thin plate-shaped metal. Further, the rubber diaphragm 371 described in the above embodiment may be provided with a resin barrier film having low permeability of the temperature sensitive medium.

  Further, a swirl promoting means for promoting the swirl flow of the refrigerant flowing through the diffuser passage 13c may be added to the ejector 13.

  According to this, since the spiral refrigerant flow path can be formed in the diffuser passage 13c, it is possible to prevent the refrigerant flow path in the diffuser passage 13c from being shortened and the pressure increase performance of the ejector 13 from being lowered. . Furthermore, the swirling flow of the refrigerant flowing into the gas-liquid separation space 30f can be promoted, and the gas-liquid separation performance in the gas-liquid separation space 30f can be improved.

  Such swirl promoting means may be configured by arranging a rectifying plate in a portion where the diffuser passage of the passage forming member 35 and the diffuser body 33 is formed, or by providing a groove in the portion. Also good. When a rectifying plate is disposed as the swirling flow promoting means, the lower end portion of the actuating rod 374 may be connected or brought into contact with the upper end portion of the rectifying plate.

  Further, an oil return hole that allows the gas-liquid separation space 30f and the gas-phase refrigerant outflow passage 31g to communicate with each other may be formed in a portion of the housing body 31 that forms the bottom surface of the gas-liquid separation space 30f. Then, the refrigerating machine oil dissolved in the liquid refrigerant may be returned to the suction side of the compressor 11 through the oil return hole.

  (4) 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 engine-driven variable displacement compressor is employed as the compressor 11 has been described. However, as the compressor 11, the operating rate of the compressor is changed by the on / off of an electromagnetic clutch. You may employ | adopt the fixed capacity type compressor which adjusts a refrigerant | coolant discharge capability. Furthermore, you may employ | adopt an electric compressor provided with a fixed displacement type compression mechanism and an electric motor, and act | operating by supplying electric power. In the electric compressor, the refrigerant discharge capacity can be controlled by adjusting the rotation speed of the electric motor.

  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 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, R407C, HFO-1234ze, HFO-1234zd, and the like can be employed. Or you may employ | adopt the mixed refrigerant | coolant etc. which mixed multiple types among these refrigerant | coolants.

  (5) 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.

DESCRIPTION OF SYMBOLS 10 Ejector type refrigeration cycle 13 Ejector 13a, 13b Nozzle passage, suction passage, diffuser passage 13c, 13d Diffuser passage, bypass passage 30 Body 35 Passage forming member 37 Drive mechanism 37a Enclosed space 371 Diaphragm (pressure response member)

Claims (8)

An ejector applied to a vapor compression refrigeration cycle apparatus (10),
A decompression space (30b) for decompressing the refrigerant, 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 refrigerant suction port (31b), and the decompression A body (30) in which a pressurizing space (30e) into which the injected refrigerant injected from the use space (30b) and the suction refrigerant sucked through the suction passage (13b) flow is formed;
At least a portion is disposed in the decompression space (30b) and in the pressurization space (30e), and has a conical shape whose outer diameter increases with distance from the decompression space (30b). A formed passage forming member (35);
A drive mechanism (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) depressurizes and injects the refrigerant. A nozzle passage (13a) that functions as a nozzle to
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 drive mechanism (37) includes a pressure responsive member (371) that is deformed according to the pressure in the enclosed space (37a) in which a temperature-sensitive medium whose pressure changes with temperature change is enclosed, and the suction passage. (13b) is fixed to the body (30) so as to form part of the inner wall surface;
Further, an ejector characterized in that a bypass passage (13d) through which a part of the suction refrigerant flows is formed between the drive mechanism (37) and the body (30). A tubular member (42) protruding into the suction passage (13b) is connected to the inlet portion (13e) of the bypass passage (13d),
The ejector according to claim 1, wherein the refrigerant inlet (42a) of the tubular member (42) is opened so as to face the flow direction of the suction refrigerant.   The inlet (13e) of the bypass passage (13d) to which the tubular member (42) is connected is formed in at least one of the body (30) and the drive mechanism (37). Item 3. The ejector according to Item 2. When viewed from the central axis (CL) direction of the passage forming member (35), the drive mechanism (37) and the bypass passage (13d) are formed in an annular shape overlapping each other,
Furthermore, when viewed from the direction of the central axis (CL), the inlet portion (13e) and the outlet portion (13f) of the bypass passage (13d) are arranged with respect to the central axis (CL). The ejector according to any one of claims 1 to 3, wherein: When viewed from the central axis (CL) direction of the passage forming member (35), the drive mechanism (37) and the bypass passage (13d) are formed in an annular shape overlapping each other,
Furthermore, when viewed from the direction of the central axis (CL), the outlet portions (13f) of the bypass passage (13d) are provided at a plurality of locations. Ejector described in one. When viewed from the central axis (CL) direction of the passage forming member (35), the drive mechanism (37) is formed in an annular shape,
When viewed from the direction of the central axis (CL), the bypass passage (13d) is formed in an arc shape at least partially overlapping the drive mechanism (37),
Furthermore, the inlet portion (13e) of the bypass passage (13d) is disposed on one end side in the circumferential direction of the bypass passage (13d), and the outlet portion (13e) of the bypass passage (13d) The ejector according to any one of claims 1 to 3, wherein the ejector is disposed on the other circumferential end side of (13d).   Furthermore, the slit groove | channel (32f) into which the said suction | inhalation refrigerant | coolant flows is provided in at least one of the outer peripheral side of the said enclosure space (37a), and an inner peripheral side, The one of Claim 1 thru | or 6 characterized by the above-mentioned. The ejector as described in one.   The body (30) is formed with a swirling space (30a) for swirling the refrigerant flowing into the decompression space (30b) around the central axis of the passage forming member (35). Item 8. The ejector according to any one of Items 1 to 7.

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