JPWO2017043336A1 - Ejector - Google Patents

Abstract

The ejector (100) forms a body (200) in which a pressure reducing space (222), a suction passage (231), and a pressure increasing space (232) are formed, a nozzle passage (224), and a diffuser passage (232a). A valve member (240). The ejector (100) includes a drive mechanism (250) that displaces the valve member in the axial direction, and a base member (270) having a valve support portion (272) that slidably supports the valve member. The body is formed with a gas-liquid separation space (261) for separating the gas-liquid refrigerant flowing out of the diffuser passage, and a gas-phase refrigerant outflow passage (263) for discharging the gas-phase refrigerant separated in the gas-liquid separation space. ing. The gas-phase refrigerant outflow passage has a gas-phase refrigerant inlet portion (263a) that opens at a position away from the valve member in the gas-liquid separation space. And at least the valve support part in the base member is disposed between the gas-phase refrigerant inlet part and the valve member.

Description

Cross-reference to related applications

  This application is based on Japanese application number 2015-179257 for which it applied on September 11, 2015, and uses the description here.

  The present disclosure relates to an ejector that is a momentum transport pump that depressurizes a fluid and performs fluid transport by suction of a working fluid ejected at high speed.

  Conventionally, an ejector is known as a decompression device applied to a vapor compression refrigeration cycle. In this type of ejector, the refrigerant flowing out of the evaporator is sucked by the suction action of the jet refrigerant injected from the nozzle part that decompresses the refrigerant, and the jet refrigerant and the sucked refrigerant are mixed in the booster part (that is, the diffuser part). Thus, the voltage is boosted. In a refrigeration cycle provided with this ejector, it is possible to reduce the power consumption of the compressor by utilizing the refrigerant boosting action in the boosting section of the ejector.

  Here, in the ejector applied to the refrigeration cycle, if the nozzle portion is configured with a fixed throttle, the flow rate of the refrigerant cannot be adjusted, and the operation corresponding to the load fluctuation of the refrigeration cycle cannot be realized.

  On the other hand, in accordance with the temperature and pressure of the refrigerant that has flowed out of the evaporator (that is, the suction refrigerant), the throttle opening degree (that is, the passage sectional area) of the nozzle passage that depressurizes the refrigerant and the diffuser passage that increases the pressure of the refrigerant. An ejector that can be adjusted has been proposed (see, for example, Patent Document 1).

  The ejector of Patent Document 1 includes a drive mechanism that displaces a passage forming member that forms each passage according to the pressure and temperature of the suction refrigerant as an adjustment mechanism that adjusts the throttle opening of the nozzle passage and the diffuser passage.

  Furthermore, in the ejector of Patent Document 1, a gas-liquid separation space is formed in the body of the ejector for separating the gas-liquid refrigerant flowing out from the diffuser passage by the action of centrifugal force. The ejector of Patent Document 1 causes the gas-phase refrigerant separated in the gas-liquid separation space to flow out to the refrigerant suction side of the compressor, and causes the liquid-phase refrigerant separated in the gas-liquid separation space to flow out to the refrigerant inlet side of the evaporator. It has a configuration.

JP 2015-45493 A

  Incidentally, when the refrigeration cycle to which the ejector described in Patent Document 1 is actually operated, the refrigerant can be boosted in the diffuser passage, but the effect of reducing the power consumption of the compressor cannot be sufficiently obtained. was there.

  Therefore, the present inventors investigated factors that reduce the effect of reducing the power consumption of the compressor. As a result, it has been found that the cause is a large pressure loss in the gas-phase refrigerant outflow passage through which the gas-phase refrigerant separated in the gas-liquid separation space flows out.

  The reason for this is that the ejector of Patent Document 1 is configured to support the passage forming member at the refrigerant inlet portion of the gas-phase refrigerant outflow passage, and the opening area at the refrigerant inlet portion of the gas-phase refrigerant outflow passage is the passage forming member. It is mentioned that it becomes small by the support part. That is, the pressure loss in the gas-phase refrigerant outflow passage is increased because the support portion of the passage forming member becomes a flow resistance of the gas-phase refrigerant that flows out to the refrigerant suction side of the compressor through the gas-phase refrigerant outflow passage. It is thought that it will end.

  An object of the present disclosure is to suppress a pressure loss when a gas-liquid separated gas-phase refrigerant flows in an ejector having a gas-liquid separation function.

  According to one aspect of the present disclosure, an ejector applied to a vapor compression refrigeration cycle has the following configuration.

That is, the ejector
A pressure reducing space for reducing the pressure of the refrigerant flowing in from the refrigerant inlet, a suction passage for sucking the refrigerant from the outside, and a pressure increase by mixing the injected refrigerant injected from the pressure reducing space and the suction refrigerant sucked from the suction passage A body in which a boosting space is formed;
At least a part of the pressure reducing space and the pressure increasing space are disposed, and an annular nozzle passage for injecting the refrigerant under reduced pressure between the body and the portion forming the pressure reducing space, and the pressure increasing space in the body are formed. A valve member that forms an annular diffuser passage for mixing and increasing the pressure of the injected refrigerant and the suction refrigerant between the parts;
A drive mechanism for displacing the valve member in the axial direction of the nozzle passage and the diffuser passage;
And a base member having a valve support portion that slidably supports the valve member.

  The body is formed with a gas-liquid separation space for separating the gas-liquid refrigerant flowing out from the diffuser passage, and a gas-phase refrigerant outflow passage for letting out the gas-phase refrigerant separated in the gas-liquid separation space. In addition, the gas-phase refrigerant outflow passage has a gas-phase refrigerant inlet that opens at a position away from the valve member in the gas-liquid separation space. And at least the valve support part in the base member is disposed between the gas-phase refrigerant inlet part and the valve member.

  Thus, if the valve support part of the base member is arranged between the gas-phase refrigerant inlet part and the valve member, the gas-phase refrigerant separated from the valve-support part in the gas-liquid separation space is the gas-phase refrigerant. It can suppress that it becomes a distribution resistance at the time of flowing in into an entrance part. Therefore, in an ejector having a gas-liquid separation function, it is possible to suppress a pressure loss when the gas-phase refrigerant circulates inside the body. As a result, it is possible to improve the performance of the refrigeration cycle.

  According to another aspect of the present disclosure, the base member of the ejector includes a substrate portion that fixes the valve support portion to the body. The substrate portion extends in a direction intersecting the central axis of the valve member and is fixed to a side wall portion positioned in a direction intersecting the central axis of the valve member in the body so as not to reach the gas-phase refrigerant outflow passage. ing.

  In the configuration in which the base member is fixed to the side wall portion located in the direction intersecting the central axis of the valve member in the body so as not to reach the gas-phase refrigerant outflow passage, the base member is outside the gas-phase refrigerant outflow passage in the body. It will be fixed to the part located in. For this reason, an ejector provided with this configuration does not cause the base plate portion of the base member to narrow the gas-phase refrigerant outflow passage. In addition, the ejector of this configuration can sufficiently secure the internal space of the gas-phase refrigerant outflow passage as compared with the configuration in which the base member is fixed to the portion located inside the gas-phase refrigerant outflow passage in the body. Can sufficiently suppress pressure loss when flowing through the gas-phase refrigerant outflow passage.

  Moreover, according to another viewpoint of this indication, the ejector is being fixed to the board | substrate part so that a valve support part may protrude toward a valve member side from a board | substrate part. According to this, since the valve support portion does not reach the gas-phase refrigerant outflow passage, the valve support portion becomes a flow resistance when the gas-phase refrigerant separated in the gas-liquid separation space flows into the gas-phase refrigerant inlet portion. This can be prevented.

It is a whole refrigeration cycle block diagram provided with the ejector which concerns on 1st Embodiment. It is a typical sectional view of the ejector concerning a 1st embodiment. It is sectional drawing which shows a part of drive mechanism of the ejector which concerns on 1st Embodiment. It is sectional drawing of the base member of the ejector which concerns on 1st Embodiment. It is VV sectional drawing of FIG. It is typical sectional drawing which shows the flow of the refrigerant | coolant inside the ejector which concerns on 1st Embodiment. It is typical sectional drawing which shows the flow of the refrigerant | coolant in the turning part of the base member which concerns on 1st Embodiment. It is sectional drawing of the base member of the ejector which concerns on the modification of 1st Embodiment. It is typical sectional drawing of the ejector which concerns on 2nd Embodiment. It is sectional drawing which shows the valve member and base member of the ejector which concern on 2nd Embodiment. It is XI-XI sectional drawing of FIG.

  Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. Note that, in each of the following embodiments, parts that are the same as or equivalent to the matters described in the preceding embodiment are denoted by the same reference numerals, and the description thereof may be omitted.

  Moreover, in each embodiment, when only a part of the component is described, the component described in the preceding embodiment can be applied to the other part of the component.

  The following embodiments can be partially combined with each other even if they are not particularly specified as long as they do not cause any trouble in the combination.

(First embodiment)
The present embodiment will be described with reference to FIGS. In the present embodiment, an example in which the ejector 100 of the present disclosure is applied to the vapor compression refrigeration cycle 10 illustrated in FIG. 1 will be described.

  The refrigeration cycle 10 of the present embodiment is applied to a vehicle air conditioner capable of adjusting the temperature of blown air that is blown into a vehicle interior that is an air conditioning target space. In the refrigeration cycle 10, an HFC refrigerant (for example, R134a) is adopted as the refrigerant. Refrigerating machine oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  Therefore, the refrigeration cycle 10 of the present embodiment constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. Of course, an HFO refrigerant (specifically, R1234yf) or the like may be employed as the refrigerant.

  As shown in FIG. 1, the refrigeration cycle 10 includes a compressor 11, a radiator 12, an ejector 100, and an evaporator 13 as main components.

  The compressor 11 is a fluid machine that draws in refrigerant and compresses and discharges the drawn refrigerant. The compressor 11 of this embodiment is rotationally driven by a vehicle running engine via an electromagnetic clutch and a belt (not shown). The compressor 11 is configured by a variable displacement compressor in which the refrigerant discharge capacity is changed by inputting a control signal from a control device (not shown) to the electromagnetic capacity control valve, for example. In addition, the compressor 11 may be comprised with the electric compressor rotated by the electric motor. When the compressor 11 is configured by an electric compressor, the refrigerant discharge capacity is varied depending on the rotation speed of the electric motor.

  The radiator 12 releases heat of the high-pressure refrigerant to the outside air by exchanging heat of the high-pressure refrigerant discharged from the compressor 11 with vehicle exterior air (that is, outside air) forcedly blown by the outdoor fan 12a. This is a heat-dissipating heat exchanger that condenses and liquefies the refrigerant.

  In the present embodiment, a subcool condenser is used as the radiator 12. Specifically, the radiator 12 is separated by a condensing unit 121 that radiates and condenses high-pressure refrigerant, a receiver 122 that separates the gas-liquid refrigerant flowing out of the condensing unit 121 and stores excess refrigerant, and the receiver 122. It has the supercooling part 123 which supercools the made liquid phase refrigerant | coolant. The refrigerant outflow side in the supercooling section 123 of the radiator 12 is connected to the refrigerant inlet 211 of the ejector 100.

  The ejector 100 functions as a decompression device that decompresses the high-pressure refrigerant in the liquid phase that has flowed out of the radiator 12, and also performs fluid transportation that circulates the refrigerant by suction action (that is, entrainment action) of the refrigerant flow ejected at high speed. It also functions as a refrigerant circulation device. The specific configuration of the ejector 100 will be described later.

  The evaporator 13 absorbs heat from the outside air introduced into the air conditioning case of the vehicle air conditioner (not shown) or the air inside the vehicle (that is, the inside air) by the indoor blower 13a and evaporates the refrigerant flowing through the inside. It is an exchanger. The refrigerant outflow side of the evaporator 13 is connected to the refrigerant suction port 212 of the ejector 100.

  Next, a control device (not shown) will be described. The control device includes a well-known microcomputer including a storage unit such as a CPU, a ROM, and a RAM and its peripheral circuits. Various operation signals from the operation panel by the occupant, detection signals from various sensor groups, and the like are input to the control device. The control device executes various calculations and processes based on a control program stored in the storage unit using an input signal or the like, and controls operations of various devices. The storage unit is composed of a non-transitional tangible storage medium.

  Next, the detailed configuration of the ejector 100 of the present embodiment will be described with reference to FIGS. Here, the up and down arrows shown on the drawing such as FIG. 2 indicate the up and down directions in a state where the ejector 100 is mounted on the vehicle. Moreover, the dashed-dotted line CL in FIG. 2 has shown the axis line of the central axis of the valve member 240 mentioned later.

  The ejector 100 according to the present embodiment includes, as main components, a drive mechanism that displaces the body 200, the valve member 240, and the valve member 240 in the axial direction of the nozzle passage 224 and the diffuser passage 232a (that is, the vertical direction in FIG. 2). 250.

  As shown in FIG. 2, the ejector 100 of this embodiment is provided with the body 200 comprised by combining a some structural member. The body 200 of this embodiment is configured by fixing a nozzle body 220, a diffuser body 230, a lower body 260, and the like inside a housing body 210 that constitutes an outer shell of the ejector 100.

  The housing body 210 is composed of a member made of a metal such as a prism or a resin. The housing body 210 has a refrigerant inlet 211 and a refrigerant suction port 212 formed on the upper end side thereof. The refrigerant inlet 211 is a refrigerant introduction part that allows high-pressure refrigerant to flow from the high-pressure side of the refrigeration cycle 10 (that is, the radiator 12). The refrigerant suction port 212 is a refrigerant suction unit that sucks the low-pressure refrigerant that has flowed out of the evaporator 13.

  The housing body 210 has a liquid-phase outlet 213 and a gas-phase outlet 214 formed on the lower end side thereof. The liquid phase outlet 213 is a liquid phase refrigerant derivation unit that causes the liquid phase refrigerant separated in the gas-liquid separation space 261 described later to flow out to the refrigerant inlet side of the evaporator 13. The gas-phase outlet 214 is a gas-phase refrigerant outlet that allows the gas-phase refrigerant separated in the gas-liquid separation space 261 to flow out to the suction side of the compressor 11.

  The nozzle body 220 is accommodated on the upper end side inside the housing body 210. More specifically, the nozzle body 220 is a housing so that a part of the nozzle body 220 overlaps with the refrigerant inlet 211 when viewed from a direction orthogonal to the direction of the axis CL (that is, the vertical direction) of the valve member 240 described later. Housed in the body 210.

  The nozzle body 220 of the present embodiment is composed of a member made of metal. The nozzle body 220 is fixed inside the housing body 210 by means such as press-fitting so that the axial direction thereof is along the axis line CL of the central axis of the valve member 240.

  The nozzle body 220 includes a barrel portion 220a formed in a size that fits the internal space of the housing body 210, and a cylindrical nozzle portion 220b that is provided on the lower end side of the barrel portion 220a and protrudes downward. It is configured to include.

  The body 220a of the nozzle body 220 is formed with a swirling space 221 and the like for swirling the high-pressure refrigerant flowing from the refrigerant inlet 211. The nozzle portion 220b of the nozzle body 220 is formed with a decompression space 222 through which the refrigerant swirling the swirling space 221 passes.

  The swirling space 221 is a space formed in the shape of a rotating body whose central axis extends along the axis CL of the valve member 240. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (that is, the central axis) on the same plane. More specifically, the swirling space 221 of the present embodiment has a cylindrical shape. Of course, the swirl space 221 may have a conical shape or a shape obtained by combining a truncated cone and a cylinder.

  Further, the swirling space 221 according to the present embodiment communicates with the refrigerant inlet 211 via the refrigerant inflow passage 223 formed in the body 220 a of the housing body 210 and the nozzle body 220.

  The refrigerant inflow passage 223 is formed to extend in the tangential direction of the inner wall surface of the swirling space 221 when viewed from the direction of the central axis of the swirling space 221. Thereby, the refrigerant that has flowed into the swirl space 221 from the refrigerant inflow passage 223 flows along the inner wall surface of the swirl space 221 and swirls in the swirl space 221. Note that the refrigerant inflow passage 223 does not have to be formed so as to completely coincide with the tangential direction of the swirling space 221 when viewed from the direction of the central axis of the swirling space 221. In other words, if the refrigerant inflow passage 223 is formed in a shape in which the refrigerant that has flowed into the swirl space 221 flows along the inner wall surface of the swirl space 221, a component in another direction (for example, the direction of the central axis of the swirl space 221). ) May be included.

  Here, a centrifugal force acts on the refrigerant swirling in the swirling space 221. For this reason, in the swirl space 221, the refrigerant pressure on the central axis side is lower than the refrigerant pressure on the outer peripheral side. Therefore, in the present embodiment, when the refrigeration cycle 10 is operated, the refrigerant pressure on the central axis side in the swirling space 221 is the pressure that becomes a saturated liquid phase refrigerant, or the pressure at which the refrigerant boils under reduced pressure (that is, causes cavitation). To lower.

  Such adjustment of the refrigerant pressure on the central axis side of the swirling space 221 can be realized by adjusting the swirling flow velocity of the refrigerant swirling in the swirling space 221. Specifically, the swirl flow velocity can be adjusted by adjusting the ratio between the cross-sectional area of the refrigerant inflow passage 223 and the cross-sectional area of the swirl space 221 in the direction orthogonal to the central axis. Note that the above-described swirling flow velocity means the flow velocity in the swirling direction of the refrigerant in the vicinity of the outermost peripheral portion of the swirling space 221.

  The decompression space 222 is formed on the lower side of the swirl space 221 so that the high-pressure refrigerant swirled in the swirl space 221 flows. The decompression space 222 of the present embodiment is formed so that its central axis is coaxial with the swirling space 221.

  The decompression space 222 has a shape in which a tapered portion 222a and a divergent portion 222b are combined. The tapered portion 222a is configured by a truncated cone-shaped hole whose flow path cross-sectional area continuously decreases toward the downstream side in the refrigerant flow direction. Further, the divergent portion 222b is configured by a truncated cone-shaped hole whose flow path cross-sectional area continuously increases toward the downstream side in the refrigerant flow direction. In addition, the connecting portion between the tapered portion 222a and the divergent portion 222b in the decompression space 222 is a nozzle throat portion (that is, a minimum passage area portion) 222c in which the flow path cross-sectional area is reduced most.

  When viewed from a direction perpendicular to the central axis of the decompression space 222, the divergent portion 222b overlaps the decompression space 222 and an upper portion of a valve member 240 described later. Therefore, the cross-sectional shape of the divergent portion 222b is an annular shape (that is, a donut shape) perpendicular to the axis CL of the central axis of the valve member 240.

  In the present embodiment, a nozzle passage 224 in which a refrigerant passage formed between an inner peripheral surface of a portion of the nozzle body 220 forming the pressure reducing space 222 and an outer peripheral surface on the upper side of a valve member 240 described later functions as a nozzle. Is configured.

  Subsequently, the diffuser body 230 is accommodated on the lower side of the nozzle body 220 inside the housing body 210. Specifically, the diffuser body 230 is accommodated in the housing body 210 such that a part thereof overlaps the refrigerant suction port 212 when viewed from a direction orthogonal to the direction of the axis CL of the valve member 240 described later. Has been.

  The diffuser body 230 of the present embodiment is composed of a member made of metal. The diffuser body 230 is fixed to the inside of the housing body 210 by means such as press fitting so that the axial direction thereof is along the axis line CL of the valve member 240.

  In the diffuser body 230 of the present embodiment, a rotating body-shaped through hole 230a penetrating the front and back is formed at the center, and a part of a drive mechanism 250 described later is accommodated on the outer peripheral side of the through hole 230a. For this purpose, a groove 230b is formed. The through hole 230 a is formed so that the central axis thereof is coaxial with the swivel space 221 and the decompression space 222.

  A suction space forming member 280 is disposed between the upper surface of the diffuser body 230 and the lower surface of the nozzle body 220 facing the diffuser body 230. The suction space forming member 280 is formed with a through hole at the center thereof that communicates with the through hole 230 a of the diffuser body 230.

  In addition, the suction space forming member 280 is provided with a groove portion that forms a suction space 231a in which the refrigerant flowing from the refrigerant suction port 212 is retained between the diffuser body 230 and a portion facing the groove portion 230b of the diffuser body 230. ing. The suction space 231a has an annular cross section when viewed from the direction of the central axis of the swirl space 221 and the decompression space 222.

  Further, the suction space forming member 280 is formed with a communication path that guides the refrigerant flowing from the refrigerant suction port 212 to the suction space 231a. The refrigerant flowing from the refrigerant suction port 212 is introduced into the suction space 231a through the communication path. The suction space 231a may be configured by a space formed between the lower surface of the nozzle body 220 and the upper surface of the diffuser body 230. In this case, the suction space forming member 280 can be eliminated.

  In the present embodiment, the lower end portion of the nozzle body 220 is positioned inside the through hole 230 a of the diffuser body 230. Of the through hole 230a of the diffuser body 230, the space overlapping the nozzle body 220 when viewed from the radial direction has a refrigerant passage cross-sectional area that gradually decreases in the refrigerant flow direction.

  In the present embodiment, the space formed between the inner peripheral surface of the through hole 230a of the diffuser body 230 and the outer peripheral surface on the lower side of the nozzle body 220 is between the suction space 231a and the refrigerant flow downstream side of the decompression space 222. A suction passage 231b to be communicated is configured.

  In the present embodiment, the suction space 231a and the suction passage 231b form a suction portion (that is, a suction passage) 231 through which the suction refrigerant flows from the outer peripheral side to the inner peripheral side of the central axis. The suction passage 231b has an annular shape in cross section perpendicular to the central axis.

  Further, in the through hole 230a of the diffuser body 230, on the downstream side of the refrigerant flow in the suction passage 231b, a pressure increasing space 232 that is formed in a substantially truncated cone shape that gradually expands in the refrigerant flow direction is formed. The pressurizing space 232 is a space in which the refrigerant injected from the nozzle passage 224 described above and the suction refrigerant sucked from the suction part 231 are mixed and pressurized.

  The pressurizing space 232 of the present embodiment is formed such that its radial cross-sectional area increases toward the downstream side (that is, the lower side) in the refrigerant flow direction. Note that the pressurizing space 232 forms a frustoconical (ie, trumpet-shaped) space whose cross-sectional area increases toward the lower side.

  Inside the pressure increasing space 232, a lower portion of a valve member 240 described later is disposed. The spread angle of the conical side surface of the valve member 240 in the boosting space 232 is smaller than the spread angle of the frustoconical space of the boosting space 232. Thereby, the refrigerant passage formed between the inner peripheral surface of the pressurizing space 232 and the outer peripheral surface of the valve member 240 described later has its refrigerant passage area gradually expanding toward the downstream side of the refrigerant flow. .

  In the present embodiment, the refrigerant passage formed between the inner peripheral surface of the pressure increasing space 232 and the outer peripheral surface of the valve member 240 is a diffuser passage 232a that functions as a diffuser, and the velocity energy of the injected refrigerant and the suction refrigerant is set to pressure. It is converted into energy. The diffuser passage 232a has an annular shape in cross section perpendicular to the central axis.

  Subsequently, the valve member 240 will be described. The valve member 240 is a member that forms a nozzle passage 224 between the inner peripheral surface of the nozzle body 220 and a diffuser passage 232 a between the inner peripheral surface of the diffuser body 230.

  The valve member 240 is accommodated in the housing body 210 so that at least a part thereof is positioned in both the pressure reducing space 222 and the pressure increasing space 232. The valve member 240 is arranged so that the axis line CL of the central axis thereof is coaxial with the pressure reducing space 222 and the pressure increasing space 232.

  The valve member 240 of the present embodiment receives a load output from a passage forming portion 241 that forms a nozzle passage 224 and a diffuser passage 232a, a sliding shaft portion 242 supported by a base member 270 described later, and a drive mechanism 250 described later. A load receiving portion 243 is provided.

  The passage forming portion 241 of the present embodiment is made of a substantially conical resin. Specifically, the passage forming portion 241 is formed in a substantially conical shape in which the cross-sectional area (that is, the outer diameter) increases as the distance from the decompression space 222 increases.

  A portion of the passage forming portion 241 that faces the inner peripheral surface of the decompression space 222 has a divergent portion of the decompression space 222 such that an annular nozzle passage 224 is formed between the inner peripheral surface of the decompression space 222. It has a curved surface along the inner peripheral surface of 222b.

  In addition, the portion of the passage forming portion 241 that faces the inner peripheral surface of the boosting space 232 has an annular diffuser passage 232 a formed between the inner peripheral surface of the boosting space 232 and the boosting space 232. It has a curved surface along the inner peripheral surface.

  Here, as described above, the boosting space 232 is formed so as to constitute a frustoconical space, and the passage forming portion 241 has a curved surface along the inner peripheral surface of the boosting space 232. For this reason, the diffuser passage 232a is formed so as to expand in a direction intersecting the axis CL of the valve member 240. That is, the diffuser passage 232a is a refrigerant passage that moves away from the axis CL of the central axis of the valve member 240 from the upstream side to the downstream side of the refrigerant flow.

  Subsequently, the sliding shaft portion 242 is made of a rod-shaped metal extending along the axis line CL of the central axis of the valve member 240. The sliding shaft portion 242 is fixed to the passage forming portion 241 at one end side. Further, the sliding shaft portion 242 is supported by a base member 270 described later at the other end side. Thereby, the sliding shaft part 242 is slidable along the axis line CL of the central axis of the valve member 240.

  Subsequently, the load receiving portion 243 is a member that receives a load from a load transmission member 253 of the drive mechanism 250 described later. The load receiving portion 243 of the present embodiment is configured by a disk-shaped member. The center portion of the load receiving portion 243 of this embodiment is fixed to the sliding shaft portion 242. The load receiving portion 243 is made of a material having high rigidity and strength so that it does not bend even when a load from the drive mechanism 250 is applied. The load receiving portion 243 of the present embodiment is made of a metal having higher rigidity and strength than the passage forming portion 241.

  Next, the drive mechanism 250 will be described. The drive mechanism 250 displaces the valve member 240 in the axial direction of the central axis of the nozzle passage 224 and the diffuser passage 232a, that is, in the direction of the axis CL of the central axis of the valve member 240, so that the refrigerant flow path of each passage 224, 232a. It is a drive part which changes an area.

  The drive mechanism 250 of the present embodiment controls the amount of displacement of the valve member 240 so that the degree of superheat (that is, temperature and pressure) of the low-pressure refrigerant that has flowed out of the evaporator 13 is in a desired range. The drive mechanism 250 of this embodiment is accommodated in the body 200 so as not to be affected by the external ambient temperature.

  The drive mechanism 250 of this embodiment has a thin plate-like diaphragm 251 that constitutes a pressure responsive member that is displaced according to the pressure received by the pressure receiving portion, and a pair of lid portions 252a and 252b that hold the diaphragm 251.

  As shown in FIG. 3, the pair of lid portions 252a and 252c has an annular shape that matches the inner shape of the groove portion 230b so as to be accommodated in the annular groove portion 230b formed on the upper surface of the diffuser body 230 ( That is, it is formed in a donut shape.

  The diaphragm 251 is formed in an annular shape so that it can be accommodated in the pair of lid portions 252a and 252c. The diaphragm 251 moves up and down an annular space formed between the pair of lid portions 252a and 252c in a state where both the inner peripheral edge portion and the outer peripheral edge portion are sandwiched between the pair of lid portions 252a and 252c. It is being fixed so that it may be divided into two spaces.

  Of the two spaces partitioned by the diaphragm 251, the space formed between the upper lid 252 a is sealed with a temperature-sensitive medium whose pressure changes according to the temperature change of the refrigerant flowing out of the evaporator 13. A space 252b is configured. In the present embodiment, the upper lid portion 252a constitutes an enclosed space forming portion that forms an enclosed space 252b that encloses the temperature-sensitive medium together with the diaphragm.

  A temperature-sensitive medium (for example, R134a) composed mainly of the same refrigerant as the refrigerant circulating in the refrigeration cycle 10 is enclosed in the enclosure space 252b so as to have a predetermined density. The temperature sensitive medium is sealed in the sealed space 252b in a gas-liquid mixed state. In addition, as a temperature sensitive medium, you may employ | adopt the mixed fluid of the refrigerant | coolant and helium gas which circulate through a cycle, for example.

  The enclosed space 252b of this embodiment forms an annular space that matches the shape of the diaphragm 251 and is formed so as to surround the axis CL of the central axis of the valve member 240 so as not to interfere with the valve member 240. Has been.

  The upper lid portion 252a that forms the enclosed space 252b is disposed at a position adjacent to the suction portion 231. Thereby, the temperature of the suction refrigerant flowing through the suction part 231 is transmitted to the temperature sensitive medium in the enclosed space 252b, and the internal pressure of the enclosed space 252b becomes a pressure corresponding to the temperature of the suction refrigerant flowing through the suction part 231. Get closer.

  On the other hand, of the two spaces partitioned by the diaphragm 251, the space formed between the lower lid portion 252 c is a refrigerant that has flowed out of the evaporator 13 through a communication path (not shown) formed in the diffuser body 230. The introduction space 252d is introduced.

  The introduction space 252d is a pressure chamber that applies the pressure of the suction refrigerant in the suction portion (that is, the suction passage) 231 to the diaphragm 251 so as to oppose the pressure of the temperature sensitive medium. The lower lid portion 252c is formed with a through-hole portion 252e through which the refrigerant flowing through the suction portion 231 is introduced into the introduction space 252d and an upper end portion of an operating rod 253a described later is inserted.

  Thus, the temperature of the temperature-sensitive medium sealed in the sealed space 252b includes the temperature of the refrigerant flowing out of the evaporator 13 through the pair of lid portions 252a and 252c, that is, the suction refrigerant flowing through the suction portion 231. Communicated. In the present embodiment, the pair of lid portions 252a and 252c and the spaces 252b and 252d constitute a temperature sensing portion 252 that detects the temperature of the suction refrigerant flowing through the suction portion 231.

  Here, the diaphragm 251 is deformed according to the pressure difference between the internal pressure of the enclosed space 252b and the pressure of the refrigerant introduced into the introduction space 252d, and is always in contact with the refrigerant. For this reason, it is desirable that the diaphragm 251 is made of a material having excellent toughness, pressure resistance, gas barrier properties, and sealing properties.

  In this embodiment, as the diaphragm 251, for example, a base material made of a synthetic rubber such as EPDM (that is, ethylene propylene rubber) or HNBR (that is, hydrogenated nitrile rubber) containing a base fabric (for example, polyester) is employed. Yes. It is desirable that the diaphragm 251 be integrated with a rubber base material with a barrier film that suppresses leakage of the temperature sensitive medium from the enclosed space 252b. It is desirable to select a barrier film having a low permeability of the temperature sensitive medium according to the type of the temperature sensitive medium enclosed in the enclosed space 252b.

  Further, the drive mechanism 250 includes a load transmission member 253 that transmits a load generated by the displacement of the diaphragm 251 to the valve member 240.

  As shown in FIG. 2, the load transmitting member 253 includes a plurality of operating rods 253 a disposed so that one end side thereof is in contact with the load receiving portion 243 of the valve member 240, the other end side of each operating rod 253 a, and the diaphragm 251. Plate member 253b disposed so as to be in contact with both.

  Each actuating rod 253a passes through a sliding hole (not shown) formed on the radially outer side of the through hole 230a of the diffuser body 230, one end side contacts the lower outer periphery of the load receiving portion 243, and the other end side is a plate member. It arrange | positions so that 253b may be touched.

  Each actuating rod 253a is arranged at intervals in the circumferential direction of the plate member 253b (that is, the circumferential direction of the central axis of the valve member 240). It is desirable that the operating rods 253a be equally arranged in the circumferential direction of the plate member 253b so that the displacement of the diaphragm 251 is accurately transmitted to the valve member 240.

  Further, it is desirable that three or more actuating rods 253a be arranged at intervals in the circumferential direction of the diffuser body 230 so that the displacement of the diaphragm 251 is accurately transmitted to the valve member 240. More preferably, it is desirable that three actuating rods 253a are arranged at intervals in the circumferential direction of the diffuser body 230.

  Subsequently, the plate member 253b is a member for evenly transmitting the load from the diaphragm 251 to each operating rod 253a. The plate member 253b is sandwiched between the diaphragm 251 and the operating rod 253a so as to support the pressure receiving portion in the diaphragm 251. The plate member 253b of the present embodiment is disposed in the introduction space 252d.

  The plate member 253b of the present embodiment is formed in an annular shape so as to overlap with the diaphragm 251 when viewed from the direction of the axis CL of the valve member 240 in order to appropriately transmit the load generated by the displacement of the diaphragm 251 to the operating rod 253a. Has been.

  Further, the plate member 253b of the present embodiment is made of a material (for example, metal) having higher rigidity than the diaphragm 251. By interposing the plate member 253b between the diaphragm 251 and the actuating rod 253a, even if a variation in the size of each actuating rod 253a or a warp of the diaphragm 251 occurs, it is transmitted from the diaphragm 251 to the valve member 240. It can control that force changes. In particular, when the diaphragm 251 includes a rubber base material, the plate member 253b can function as a barrier that suppresses leakage of the temperature sensitive medium from the diaphragm 251.

  The drive mechanism 250 also includes a pair of urging members 254 and 255 that apply a load to the valve member 240, and a load adjustment unit 256 that adjusts the load of each urging member 254 and 255 that acts on the valve member 240. Have

  The pair of urging members 254 and 255 are members that set the displacement characteristics of the valve member 240 according to the load from the drive mechanism 250. Each biasing member 254, 255 of the present embodiment is configured by a coil spring.

  Of the pair of urging members 254 and 255, the first urging member 254 applies a load to the valve member 240 in a direction in which the refrigerant passage area of the nozzle passage 224 and the diffuser passage 232a is reduced. Of the pair of urging members 254 and 255, the second urging member 255 applies a load to the valve member 240 in the opposite direction to the first urging member 254.

  Each urging member 254, 255 of this embodiment is supported by a base member 270 described later. Each urging member 254, 255 also functions as a buffer member that attenuates vibration of the valve member 240 caused by pressure pulsation or the like when the refrigerant is depressurized.

  The load adjustment unit 256 adjusts the valve opening pressure of the valve member 240 by adjusting the load applied to the valve member 240 by the biasing members 254 and 255, and finely adjusts the target degree of superheat. It is.

  In the drive mechanism 250 configured as described above, the diaphragm 251 displaces the valve member 240 in accordance with the temperature and pressure of the refrigerant flowing out of the evaporator 13, so that the degree of superheat of the refrigerant on the outlet side of the evaporator 13 is increased in advance. Adjustment is made so as to approach the predetermined value.

  For example, when the temperature and pressure of the refrigerant flowing out of the evaporator 13 are high and the load of the refrigeration cycle 10 is high, the diaphragm 251 displaces the valve member 240 so that the refrigerant passage areas of the nozzle passage 224 and the diffuser passage 232a become large. Let Thereby, the refrigerant | coolant flow volume which circulates the inside of the refrigerating cycle 10 increases.

  On the other hand, when the temperature and pressure of the refrigerant flowing out of the evaporator 13 are low and the load of the refrigeration cycle 10 is low, the diaphragm 251 displaces the valve member 240 so that the refrigerant passage areas of the nozzle passage 224 and the diffuser passage 232a become small. Let As a result, the flow rate of the refrigerant circulating in the refrigeration cycle 10 decreases.

  Next, the configuration on the lower side of the valve member 240 in the housing body 210 will be described. A lower body 260 is accommodated below the valve member 240 in the housing body 210. More specifically, when the lower body 260 is viewed from a direction orthogonal to the direction of the axis CL (that is, the vertical direction) of the valve member 240, a part of the lower body 260 includes the liquid-phase outlet 213 and the gas-phase outlet 214. It is accommodated in the housing body 210 so as to overlap.

  In the lower body 260, a gas-liquid separation space 261 is formed between the bottom side of the valve member 240 and gas-liquid separation of the mixed refrigerant flowing out from the diffuser passage 232a. The gas-liquid separation space 261 is a substantially cylindrical space, and its central axis is formed so as to be coaxial with the central axes of the swirl space 221, the decompression space 222, and the pressurization space 232.

  In addition, a cylindrical pipe 262 is provided on the bottom surface side of the inner space of the lower body 260 so as to be coaxial with the gas-liquid separation space 261 and extending toward the valve member 240 side (that is, the upper side). Yes. Inside the pipe 262 is formed a gas-phase-side outflow passage 263 that guides the gas-phase refrigerant separated in the gas-liquid separation space 261 to the gas-phase outlet 214 formed in the housing body 210.

  In the present embodiment, the gas phase side outflow passage 262 constitutes a gas phase refrigerant outflow passage through which the gas phase refrigerant separated in the gas-liquid separation space 261 flows out. In the present embodiment, the open end on the upper end side of the pipe 262 constitutes the gas phase refrigerant inlet 263 a of the gas phase side outflow passage 263. The pipe 262 is provided in the lower body 260 so that the gas-phase refrigerant inlet 263a opens at a position away from the valve member 240 in the gas-liquid separation space 261. That is, the gas-phase refrigerant inlet portion 263a of the present embodiment opens at a position away from the passage forming portion 241 of the valve member 240. Note that the gas-phase refrigerant inlet portion 263a of the present embodiment is provided at a position away from the passage forming portion 241 so that a space is formed between the valve member 240 and the passage forming portion 241 in the axial direction. .

  Further, the liquid phase refrigerant separated in the gas-liquid separation space 261 is stored on the outer peripheral side of the pipe 262. In addition, the space on the outer peripheral side of the pipe 262 in the lower body 260 constitutes a liquid storage space 264 that stores the liquid phase refrigerant. Further, a liquid phase side outflow passage 265 that guides the liquid phase refrigerant stored in the liquid storage space 264 to the liquid phase outlet 213 formed in the housing body 210 is provided at a portion corresponding to the liquid storage space 264 in the lower body 260. Is formed.

  Here, the base member 270 is accommodated between the valve member 240 and the lower body 260 in the housing body 210 of the present embodiment. A part of the base member 270 of the present embodiment is disposed between the passage forming portion 241 and the load receiving portion 243 of the valve member 240. The base member 270 is fixed to the housing body 210 by, for example, press fitting or a fastening member such as a screw.

  Details of the base member 270 will be described with reference to FIGS. 4 and 5. As shown in FIGS. 4 and 5, the base member 270 includes a circular plate-shaped substrate portion 271 and a cylindrical valve support portion 272 fixed to the center portion of the substrate portion 271. The base plate portion 271 and the valve support portion 272 constituting the base member 270 are each formed of metal and are connected to each other by welding or the like.

  As for the board | substrate part 271, the site | part of the outer peripheral side is being fixed with respect to the housing body 210, and the valve support part 272 is being fixed to the site | part of the center side. The substrate portion 271 of this embodiment mainly functions as a member that fixes the valve support portion 272 to the body 200.

  The substrate portion 271 of this embodiment extends in a direction that intersects the central axis of the valve member 240. Specifically, the substrate portion 271 extends toward the radially outer side of the valve member 240 with the central axis of the valve member 240 as the center.

  Further, the substrate portion 271 of the present embodiment is fixed to a side wall portion that forms a space closer to the valve member 240 than the vapor phase refrigerant inlet portion 263a in the body 200 so as not to reach the vapor phase side outflow passage 263. Yes. In other words, the base member 270 of the present embodiment is fixed to a part located outside the gas phase side outflow passage 263 in the body 200. Specifically, the substrate portion 271 is fixed to a portion of the body 200 that is located on the radially outer side of the passage forming portion 241 of the valve member 240.

  The valve support portion 272 of the present embodiment is configured by a cylindrical member in which a sliding hole 272a extending along the direction of the axis line CL of the valve member 240 is formed. The sliding hole 272a is a through hole through which the sliding shaft portion 242 of the valve member 240 slides. The sliding hole 272a is formed in a size that allows the sliding shaft portion 242 of the valve member 240 to slide.

  In addition, the valve support portion 272 of the present embodiment is configured so that the valve member 240 and the gas phase refrigerant are not connected to flow resistance when the gas phase refrigerant separated in the gas-liquid separation space 261 flows into the gas phase side outflow passage 263. It arrange | positions between the entrance parts 263a. That is, the valve support portion 272 of this embodiment is disposed between the passage forming portion 241 and the gas phase refrigerant inlet portion 263a.

  Specifically, the valve support portion 272 of the present embodiment is disposed so as to protrude toward the valve member 240 side, not the gas phase refrigerant inlet portion 263a side. That is, the valve support portion 272 of the present embodiment is fixed to the substrate portion 271 so as to protrude from the substrate portion 271 toward the passage forming portion 241 side of the valve member 240.

  Further, the substrate portion 271 of the present embodiment is provided with a first spring support portion 273a that supports the lower end side of the first biasing member 254 at a portion where the valve support portion 272 is fixed. In addition, a second spring support portion 273b that supports the upper end side of the second biasing member 255 is connected to a portion of the base plate portion 271 that fixes the valve support portion 272 via a connection portion 273c. In this embodiment, each spring support part 273a, 273b and the connection part 273c comprise the load support part 273 which supports both each urging | biasing member 254,255.

  Further, in the substrate portion 271 of the present embodiment, an outlet side communication passage 274 that guides the refrigerant flowing out from the diffuser passage 232a to the gas-liquid separation space 261 is formed in a portion close to the refrigerant outlet side of the diffuser passage 232a. . The outlet side communication passage 274 is provided with a turning portion 275 for turning the refrigerant flowing out from the diffuser passage 232a around the axis of the gas-liquid separation space 261.

  As shown in FIG. 5, the swivel unit 275 of the present embodiment includes a plurality of rectifying plates 275a. Each rectifying plate 275a is disposed at a predetermined interval (for example, at equal intervals) around the axis of the valve member 240 so as to surround the refrigerant outlet side of the diffuser passage 232a.

  Each rectifying plate 275a has a radial direction perpendicular to the central axis of the diffuser passage 232a so that the flow of the refrigerant flowing out of the diffuser passage 232a is turned in the tangential direction of the outer peripheral edge of the base member 270. It has a shape extending in the intersecting direction.

  Here, the ejector 100 of the present embodiment is provided with a swirling space 221 that swirls the refrigerant that has flowed in from the refrigerant inlet 211. For this reason, in the diffuser passage 232a, a refrigerant flow along the swirling direction of the refrigerant in the swirling space 221 may occur.

  For this reason, it is desirable that the swirl unit 275 swirls the refrigerant in the same direction as the swirl direction of the refrigerant in the swirl space 221. That is, each rectifying plate 275a constituting the swirling unit 275 is desirably formed in a shape extending along the swirling direction of the refrigerant in the swirling space 221. In the diffuser passage 232a, when the refrigerant flow along the swirl direction of the refrigerant in the swirl space 221 hardly occurs, the swirl unit 275 swirls in the direction opposite to the swirl direction of the refrigerant in the swirl space 221. It may be.

  The rectifying plate 275a of the present embodiment is formed in a flat plate shape that extends linearly from the upstream side to the downstream side of the refrigerant flow in the outlet side communication passage 274. In addition, the respective rectifying plates 275a of the present embodiment are arranged so that the interval between the rectifying plates 275a increases from the refrigerant flow upstream side to the downstream side of the outlet side communication passage 274. In other words, each rectifying plate 275a of the present embodiment is arranged to be a speed reducing blade row.

  According to this, in the outlet side communication passage 274, the passage cross-sectional area gradually increases from the refrigerant flow upstream side to the downstream side. For this reason, in the exit side communication path 274, since the velocity energy of a refrigerant | coolant is converted into pressure energy, it functions also as a diffuser. As a result, the pressure increase amount of the refrigerant in the ejector 100 can be increased.

  Here, in this embodiment, the base member 270 is disposed between the passage forming portion 241 and the load receiving portion 243 of the valve member 240. For this reason, the base member 270 needs to be formed with a through hole through which each operating rod 253a passes.

  However, if each actuating rod 253a is simply formed on the base plate portion 271, each actuating rod 253a passes through the outlet side communication passage 274 (that is, crosses), so that the refrigerant passage area of the outlet side communication passage 274 is reduced. There is a concern that

  Therefore, in the present embodiment, a rectifying plate 275a is provided at a portion corresponding to each actuating rod 253a in the base member 270, and a through hole 275b through which each actuating rod 253a passes is provided in the rectifying plate 275a. According to this, even if the base member 270 is disposed between the passage forming portion 241 and the load receiving portion 243 of the valve member 240, the refrigerant passage area of the outlet side communication passage 274 is reduced by each operating rod 253a. There is nothing. This is effective in reducing the pressure loss of the refrigerant flowing out from the diffuser passage 232a.

  Next, the operation of the present embodiment based on the above configuration will be described. When an air conditioning operation switch or the like is turned on by the occupant, the electromagnetic clutch of the compressor 11 is energized by a control signal from the control device, and the rotational driving force from the vehicle running engine is supplied to the compressor 11 via the electromagnetic clutch or the like. Communicated. Then, a control signal is input from the control device to the electromagnetic capacity control valve of the compressor 11, the discharge capacity of the compressor 11 is adjusted to a desired amount, and the compressor 11 is connected to the gas phase outlet 214 of the ejector 100. The gas-phase refrigerant sucked from is compressed and discharged.

  The high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 11 flows into the condensing part 121 of the radiator 12 and is cooled by the outside air to be condensed and liquefied, and then the gas and liquid are separated by the receiver 122. Thereafter, the liquid phase refrigerant separated by the receiver 122 flows into the supercooling unit 123 and is supercooled.

  The liquid-phase refrigerant that has flowed out of the supercooling unit 123 of the radiator 12 flows into the refrigerant inlet 211 of the ejector 100. The high-pressure refrigerant that has flowed into the refrigerant inlet 211 of the ejector 100 flows into the swirling space 221 inside the ejector 100 via the refrigerant inflow passage 223, as shown in FIG. Then, the high-pressure refrigerant that has flowed into the swirl space 221 flows along the inner wall surface of the swirl space 221 and becomes a swirl flow that swirls in the swirl space 221. Such a swirl flow reduces the pressure near the swirl center to a pressure at which the refrigerant boils under reduced pressure by the action of centrifugal force, so that the swirl center side is in a two-phase separation state with a single gas phase and a single liquid phase around it. Get closer.

  The refrigerant swirling in the swirling space 221 flows into the decompression space 222 that is coaxial with the central axis of the swirling space 221 as a gas-liquid mixed phase refrigerant, and is decompressed and expanded in the nozzle passage 224. When the pressure energy of the refrigerant is converted into velocity energy during the decompression and expansion, the gas-liquid mixed phase refrigerant is ejected from the nozzle passage 224 at a high velocity.

  This point will be described in detail. First, in the nozzle passage 224, wall surface boiling occurs when the refrigerant is separated from the inner wall surface side of the tapered portion 222a of the nozzle portion 220b. In the nozzle passage 224, interfacial boiling occurs due to boiling nuclei caused by cavitation of the refrigerant on the center side. Thus, since the boiling of the refrigerant is promoted in the nozzle passage 224, the refrigerant flowing into the nozzle passage 224 approaches a gas-liquid mixed phase state in which the gas phase and the liquid phase are homogeneously mixed.

  Then, the refrigerant flowing in the gas-liquid mixed phase in the vicinity of the nozzle throat portion 222c of the nozzle portion 220b is blocked (that is, choking), and the refrigerant in the gas-liquid mixed state that has reached the speed of sound by this choking becomes the nozzle portion 220b. Is accelerated and ejected by the end wide part 222b.

  Thus, the energy conversion efficiency (that is, the nozzle efficiency) in the nozzle passage 224 can be improved by efficiently accelerating the refrigerant in the gas-liquid mixed state to the sound speed by the boiling promotion by both the wall surface boiling and the interface boiling. Can do.

  Further, the refrigerant flowing out of the evaporator 13 is sucked into the suction portion 231 through the refrigerant suction port 212 by the suction action of the refrigerant ejected from the nozzle passage 224. Then, the mixed refrigerant of the low-pressure refrigerant sucked by the suction portion 231 and the jet refrigerant jetted from the nozzle passage 224 flows into the diffuser passage 232a whose refrigerant flow passage area is enlarged toward the downstream side of the refrigerant flow, and velocity energy Is converted into pressure energy to increase the pressure.

  In addition, the valve member 240 of the ejector 100 of the present embodiment is formed in a substantially conical shape whose cross-sectional area increases as the distance from the decompression space 222 increases. For this reason, the shape of the diffuser passage 232a can be a shape that expands to the outer peripheral side as the distance from the decompression space 222 increases. Thereby, the expansion of the dimension to the direction of the axis line CL of the valve member 240 is suppressed, and the enlargement of the physique as the whole ejector 100 can be suppressed.

  Subsequently, the refrigerant flowing out of the diffuser passage 232 a flows into the outlet side communication passage 274 formed in the base member 270. As shown in FIG. 7, the refrigerant that has flowed into the outlet-side communication path 274 flows into the gas-liquid separation space 261 in a state where a turning force is applied by each rectifying plate 275a. For this reason, in the gas-liquid separation space 261, the gas-liquid of the refrigerant is separated by the action of centrifugal force.

  The gas-phase refrigerant separated in the gas-liquid separation space 261 is drawn into the suction side of the compressor 11 through the gas-phase side outflow passage 263 and the gas-phase outlet 214 and is compressed again. At this time, since the pressure of the refrigerant sucked into the compressor 11 is increased in the diffuser passage 232a of the ejector 100, the driving force of the compressor 11 can be reduced.

  Further, the liquid-phase refrigerant separated in the gas-liquid separation space 261 is stored in the liquid storage space 264 and evaporated via the liquid-phase side outflow passage 265 and the liquid-phase outlet 213 by the refrigerant suction action of the ejector 100. Flows into the vessel 13.

  In the evaporator 13, the low-pressure liquid refrigerant absorbs heat from the air flowing in the air conditioning case and evaporates. And the gaseous-phase refrigerant | coolant which flowed out from the evaporator 13 is attracted | sucked by the suction part 231 via the refrigerant | coolant suction port 212 of the ejector 100, and flows in into the diffuser channel | path 232a.

  The ejector 100 according to this embodiment described above includes the drive mechanism 250 that displaces the valve member 240. For this reason, the valve member 240 is displaced according to the load of the refrigeration cycle 10, and the refrigerant passage areas of the nozzle passage 224 and the diffuser passage 232a can be adjusted.

  In this embodiment, the diaphragm 251 and the temperature sensing part 252 of the drive mechanism 250 are formed in an annular shape so as to surround the axis CL of the central axis of the valve member 240. According to this, since the area which receives the pressure of the refrigerant in the diaphragm 251 can be sufficiently secured, the nozzle passage 224 and the diffuser passage 232a can be appropriately changed according to the pressure change of the refrigerant flowing through the suction portion 231. .

  In particular, in the present embodiment, the valve support portion 272 of the base member 270 is arranged between the gas-phase refrigerant inlet portion 263a and the valve member 240. According to this, it can suppress that the gaseous-phase refrigerant | coolant by which the valve support part 272 was isolate | separated by the gas-liquid separation space 261 becomes a distribution resistance at the time of flowing in into the gaseous-phase refrigerant inlet part 263a.

  Therefore, in the ejector 100 having the gas-liquid separation function, it is possible to suppress the pressure loss when the gas-phase refrigerant flows through the body 200. As a result, it is possible to improve the performance of the refrigeration cycle 10.

  Further, in the present embodiment, the substrate portion 271 of the base member 270 is fixed to a side wall portion that forms a space between the gas-phase refrigerant inlet portion 263a and the valve member 240. For this reason, the base member 270 is fixed to a portion located outside the gas phase side outflow passage 263 in the body 200. For this reason, in the ejector 100 of the present embodiment, the base plate portion 271 of the base member 270 does not cause the gas phase side outflow passage 263 to be narrowed. The ejector 100 according to the present embodiment ensures a sufficient internal space of the gas-phase-side outflow passage 263 as compared with the configuration in which the base member 270 is fixed to a portion of the body 200 positioned inside the gas-phase-side outflow passage 263. it can. As a result, according to the ejector 100 of the present embodiment, it is possible to sufficiently suppress the pressure loss when the gas-phase refrigerant flows through the gas-phase-side outflow passage 263.

  Moreover, the ejector 200 of this embodiment is being fixed to the board | substrate part 271 so that the valve support part 272 protrudes from the board | substrate part 271 toward the valve member 240 side. According to this, since the valve support part 272 does not reach the gas-phase-side outflow passage 263, the flow when the gas-phase refrigerant separated by the gas-liquid separation space 261 flows into the gas-phase refrigerant inlet part 263a. It can prevent becoming resistance.

  Moreover, in this embodiment, it is set as the structure which makes the valve support part 272 protrude toward the valve member 240 side instead of the gaseous-phase refrigerant | coolant inlet part 263a side. According to this, the length of the sliding shaft part 242 in the valve member 240 can be shortened. This can reduce the axial size of the ejector 100 as a whole.

  Further, in the present embodiment, the valve support portion 272 is provided on the base member 270, and the strength or the like is not required for the lower body 260 that constitutes the gas phase refrigerant inlet portion 263a and the like. For this reason, in this embodiment, it becomes possible to comprise the lower body 260 with lightweight members, such as resin. This is effective in that the overall weight of the ejector 100 can be reduced.

  Further, in the present embodiment, the swivel portion 275 is provided for the outlet side communication passage 274 of the base member 270. In this way, if the refrigerant flowing into the gas-liquid separation space 261 is swirled using the outlet side communication passage 274 of the base member, it is not necessary to separately secure a space in which the swivel portion 275 is provided. As a whole, it is possible to reduce the size. In addition, since it is not necessary to add a member for newly imparting a turning force to the refrigerant with respect to the gas-liquid separation space 261 and the like, the internal structure of the ejector 100 can be simplified. This is also effective in suppressing pressure loss when the refrigerant flows inside the ejector 100.

  In the present embodiment, the urging members 254 and 255 are supported by the load support portion 273 of the base member 270. According to this, since it is not necessary to add a member for supporting the respective biasing members 254 and 255 separately, the internal structure of the ejector 100 can be simplified. This is also effective in suppressing pressure loss when the refrigerant flows inside the ejector 100.

  Further, the valve member 240 according to the present embodiment is configured to receive a load from the drive mechanism 250 by the load receiving portion 243 instead of the passage forming portion 241. According to this, in the valve member 240, since the strength and the like are not required for the passage forming portion 241, it is possible to configure the passage forming portion 241 with a lightweight member such as resin. This is effective in that the overall weight of the ejector 100 can be reduced.

(Modification of the first embodiment)
In the first embodiment described above, an example in which each rectifying plate 275a of the swivel unit 275 is configured by a flat plate-like member extending linearly from the refrigerant flow upstream side to the downstream side of the outlet side communication passage 274 has been described. It is not limited to this.

  For example, as shown in FIG. 8, each rectifying plate 275 a may have a blade shape that curves from the upstream side to the downstream side of the refrigerant flow in the outlet side communication passage 274. According to this, since the refrigerant flow in the outlet side communication passage 274 can be gently turned, the pressure loss when the refrigerant flows through the outlet side communication passage 274 is suppressed, and the refrigerant flowing into the gas-liquid separation space 261 is reduced. It becomes possible to turn efficiently.

(Second Embodiment)
Next, a second embodiment will be described with reference to FIGS. In this embodiment, the point which is set as the structure which receives the load from the drive mechanism 250 by the channel | path formation part 241 of the valve member 240 is different from 1st Embodiment.

  As shown in FIG. 9, the valve member 240 of the present embodiment has a configuration in which the configuration corresponding to the load receiving portion 243 of the first embodiment is abolished and has a passage forming portion 241 and a sliding shaft portion 242. .

  As shown in FIG. 10, the passage forming portion 241 of the present embodiment is a part of the portion on the refrigerant outlet side of the diffuser passage 232 a so that it can directly receive the load from each actuating rod 253 a of the drive mechanism 250. Is positioned in the outlet side communication passage 274. For convenience of explanation, a portion of the passage forming portion 241 positioned in the outlet side communication passage 274 is hereinafter referred to as an outlet end portion 241a.

  As shown in FIG. 10, the outlet side end 241 a of the passage forming portion 241 is provided at least in a portion corresponding to each actuating bar 253 a in the passage forming portion 241 (that is, a portion indicated by a dotted line in FIG. 11). Specifically, the outlet side end 241a of the present embodiment is positioned between the rectifying plates 275a.

  The outlet-side end 241a of the present embodiment extends linearly from the refrigerant flow upstream side to the downstream side, as with each rectifying plate 275a, and with respect to the radial direction orthogonal to the central axis of the diffuser passage 232a. It has a shape extending in the intersecting direction.

  Further, the base member 270 of the present embodiment is a load support portion that supports the lower end side of the first urging member 254 and the upper end side of the second urging member 255 at a portion where the valve support portion 272 in the base plate portion 271 is fixed. 273 is provided.

  Other configurations are the same as those of the first embodiment. According to the configuration in which the load receiving portion 243 is abolished as in the present embodiment, the following effects can be obtained in addition to the effects described in the first embodiment. That is, according to the configuration of the present embodiment, since the load receiving portion 243 is eliminated, the length of the sliding shaft portion 242 in the valve member 240 can be shortened. This can reduce the axial size of the ejector 100 as a whole.

(Other embodiments)
As mentioned above, although embodiment of this indication was described, this indication is not limited to the above-mentioned embodiment, and can change suitably. The ejector 100 of the present disclosure can be variously modified as follows, for example.

  In the above-mentioned embodiment, although the example which comprises the turning part 275 with the some baffle plate 275a was demonstrated, it is not limited to this. For example, a plurality of groove portions extending in a direction intersecting the radial direction of the diffuser passage 232a may be provided in a portion where the outlet side communication passage 274 is formed in the substrate portion 271, and the turning portion 275 may be configured by the groove portions.

  In each of the above-described embodiments, the example in which each rectifying plate 275a is arranged to be a speed reducing blade row has been described, but the present invention is not limited to this. For example, each rectifying plate 275a may be arranged to be a speed increasing blade row so that the interval between the rectifying plates 275a becomes narrower from the upstream side to the downstream side of the refrigerant flow in the outlet side communication passage 274. According to this, since the flow velocity of the refrigerant flowing through the outlet side communication passage 274 can be increased, it is possible to promote the swirling flow of the refrigerant in the outlet side communication passage 274.

  Although it is desirable to provide the swivel part 275 with respect to the outlet side communication path 274 of the base member 270 as in the above embodiments, the present invention is not limited to this. For example, the swivel portion 275 of the outlet side communication passage 274 may be eliminated, and instead, a swivel portion may be provided on the refrigerant outlet side of the diffuser passage 232a in the valve member 240.

  In each of the above-described embodiments, the example in which the diaphragm 251 is sandwiched between the pair of lid portions 252a and 252c has been described. However, the present invention is not limited thereto, and for example, the diaphragm 251 is narrowed by the upper lid portion 252a and the groove portion 230b of the diffuser body 230. It is good also as a structure to have.

  In each of the above-described embodiments, the example in which the body 200 is configured by a combination of a plurality of components such as the housing body 210, the nozzle body 220, and the lower body 260 has been described, but the present invention is not limited to this. For example, some of a plurality of constituent members constituting the body 200 may be configured as an integrally molded product.

  In each of the above-described embodiments, the example in which the base member 270 is configured as a separate member from the body 200 has been described. However, the present invention is not limited to this. The base member 270 and some of a plurality of constituent members constituting the body 200 may be configured as an integral molded product.

  In each of the above-described embodiments, the passage forming portion 241 of the valve member 240 employs an axial cross-sectional shape that is an isosceles triangle, but is not limited thereto. For example, the passage forming portion 241 has an axial cross-sectional shape in which two sides sandwiching the apex are convex on the inner peripheral side, two sides are convex on the outer peripheral side, or the cross-sectional shape is a semicircular shape. A thing may be adopted.

  As in each of the above-described embodiments, in order to appropriately transmit the displacement of the diaphragm 251 to the valve member 240, it is desirable to dispose three operating rods 253a constituting the load transmitting member 253, but the present invention is not limited to this. . The displacement of the diaphragm 251 may be transmitted to the valve member 240 by two or four or more operating rods 253a.

  As described in the above embodiments, the diaphragm 251 is preferably made of a rubber base material. However, the present invention is not limited to this. For example, the diaphragm 251 may be made of stainless steel or the like.

  As in the above-described embodiment, it is desirable to add the urging members 254 and 255 and the load adjusting unit 256 to the drive mechanism 250, but the urging members 254 and 255 and the load adjusting unit 256 are not essential and are omitted. It may be.

  In the above-described embodiment, the example in which the swirl space 221 is formed in the nozzle body 220 has been described. However, the present invention is not limited thereto, and for example, the swirl space 221 may be formed in the housing body 210.

  In order to improve the energy conversion efficiency in the nozzle passage 224 as in the above-described embodiment, it is desirable to form the swirl space 221 inside the body 200, but the present invention is not limited to this. The space 221 may not be formed.

  In the above-described embodiment, the example in which most of the elements constituting the body 200, the valve member 240, the drive mechanism 250, and the like are made of metal has been described, but the present invention is not limited to this. Each component may be made of a material other than metal (for example, resin) as long as pressure resistance, heat resistance, and the like are not problematic.

  In the above-mentioned embodiment, although the example which employ | adopts a subcool type condenser as the heat radiator 12 was demonstrated, it is not limited to this, For example, the heat radiator in which the receiver 122 and the supercooling part 123 are not provided is employ | adopted. Also good.

  In the above-mentioned embodiment, although the example which applies the ejector 100 of this indication to the refrigerating cycle 10 of a vehicle air conditioner was demonstrated, it is not limited to this. For example, the ejector 100 of the present disclosure may be applied to a heat pump cycle used for a stationary air conditioner or the like, or a refrigeration cycle applied to a thermal apparatus other than the air conditioner.

  In the above-described embodiment, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where it is considered that it is clearly essential in principle.

  In the above-described embodiment, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is particularly limited to a specific number when clearly indicated as essential and in principle. Except in some cases, the number is not limited.

  In the above embodiment, when referring to the shape, positional relationship, etc. of the component, etc., the shape, positional relationship, etc. unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to etc.

Claims (8)

An ejector applied to a vapor compression refrigeration cycle (10),
From the decompression space (222) for depressurizing the refrigerant flowing in from the refrigerant inlet (211), the suction passage (231) for sucking the refrigerant from the outside, the injection refrigerant injected from the decompression space, and the suction passage A body (200) in which a pressurizing space (232) for mixing and sucking the sucked refrigerant is formed;
An annular nozzle passage (224) that is disposed at least partially within the decompression space and the pressurization space, and injects the refrigerant by depressurizing the refrigerant with a portion that forms the decompression space in the body; A valve member (240) that forms an annular diffuser passage (232a) for mixing and boosting the injected refrigerant and the suction refrigerant between a portion of the body forming the pressurizing space;
A drive mechanism (250) for displacing the valve member in the axial direction of the nozzle passage and the diffuser passage;
A base member (270) having a valve support portion (272) for slidably supporting the valve member,
The body includes a gas-liquid separation space (261) for separating the gas-liquid refrigerant flowing out of the diffuser passage, and a gas-phase refrigerant outflow passage (263) for discharging the gas-phase refrigerant separated in the gas-liquid separation space. Is formed,
The gas-phase refrigerant outflow passage has a gas-phase refrigerant inlet (263a) that opens at a position away from the valve member in the gas-liquid separation space,
At least the valve support portion in the base member is an ejector disposed between the gas-phase refrigerant inlet portion and the valve member. The base member has a substrate part (271) for fixing the valve support part to the body,
The substrate portion extends in a direction intersecting with the central axis of the valve member, and against a side wall portion located in a direction intersecting the central axis of the valve member in the body so as not to reach the gas-phase refrigerant outflow passage. The ejector according to claim 1, wherein the ejector is fixed.   The ejector according to claim 2, wherein the valve support portion is fixed to the substrate portion so as to protrude from the substrate portion toward the valve member side. The valve member includes a passage forming portion (241) that forms the nozzle passage and the diffuser passage, and a sliding shaft portion (242) that is slidably supported by the valve support portion. Has been
The gas-phase refrigerant inlet portion is open at a position away from the passage forming portion,
The ejector according to any one of claims 1 to 3, wherein the valve support portion is disposed between the gas-phase refrigerant inlet portion and the passage forming portion. The gas-liquid separation space is a space having a shape of a rotating body around the central axis of the valve member,
The base member is formed with an outlet side communication passage (274) for guiding the refrigerant flowing out of the diffuser passage to the gas-liquid separation space at a portion close to the refrigerant outlet side of the diffuser passage,
5. The swivel portion (275) that swirls the refrigerant that has flowed out of the diffuser passage around the axis of the gas-liquid separation space is provided in the outlet-side communication passage. Ejector. The swivel portion has a plurality of rectifying plates (275a) having a shape extending in a direction intersecting with the radial direction of the diffuser passage,
The ejector according to claim 5, wherein the plurality of rectifying plates are arranged around the axis of the valve member so as to surround a refrigerant outlet side of the diffuser passage.   The ejector according to claim 6, wherein the plurality of rectifying plates have a blade shape that curves from the upstream side to the downstream side of the refrigerant flow in the outlet side communication passage. A first biasing member (254) for applying a load to the valve member in a direction to reduce a refrigerant passage area in the nozzle passage and the diffuser passage;
A second urging member (255) for applying a load to the valve member in a direction opposite to the first urging member;
The ejector according to any one of claims 1 to 7, wherein the base member is provided with a support portion (273) that supports both the first urging member and the second urging member.

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