JP2008139003A - Ejector type decompression device - Google Patents

Abstract

An ejector-type decompression device capable of improving a deviation between a flow path shaft of a nozzle and a shaft of a valve stem is provided.
An ejector 10 is used in a vapor compression refrigeration cycle, and is a nozzle 23 that decompresses and expands high-pressure refrigerant flowing out of a radiator in an isentropic manner; a valve rod 22 that adjusts the passage opening of the nozzle 23; A magnet rotor 15 that provides a driving force for displacing the valve stem 22 in the axial direction, and a valve stem support member that supports the valve stem 22 and is moved in the axial direction by the magnet rotor 15 to displace the valve stem 22 in the axial direction. 20 and a diffuser portion 26 that increases the pressure of the refrigerant by converting the velocity energy into pressure energy while mixing the refrigerant injected from the nozzle 23 and the refrigerant sucked from the evaporator. The valve stem support member 20 supports the valve stem 22 so as to be movable in the radial direction.
[Selection] Figure 2

Description

  The present invention is used in a vapor compression refrigeration cycle having a radiator that dissipates high-pressure refrigerant compressed by a compressor and an evaporator that absorbs heat by evaporating low-pressure refrigerant and moves low-temperature heat to a high-temperature side. The present invention relates to an ejector type pressure reducing device.

  As a conventional ejector-type decompression device, a nozzle that takes in the refrigerant flowing out of the radiator and converts the pressure energy into velocity energy to decompress and expand the refrigerant, a valve rod that adjusts the throttle opening of the nozzle, A device including a drive unit that displaces the valve stem in the axial direction is known (for example, see Patent Document 1). Further, the valve rod of the pressure reducing device is held by a magnet rotor as a drive unit via a washer, and the valve rod and the washer are joined by electric welding.

Moreover, as a decompression device provided with a valve stem (needle valve), an electronic expansion valve of a system in which a needle valve is driven by a solenoid is known (for example, see Patent Document 2). The electronic expansion valve includes a first refrigerant passage through which refrigerant flows from a side into a body provided with a refrigerant inflow chamber, and a second refrigerant passage extending in the axial direction of the needle valve. The first refrigerant passage is arranged in a state of being deviated in the radial direction with respect to the valve stem portion of the needle valve arranged at the axial center of the refrigerant inflow chamber.
JP 2005-69599 A JP-A-8-159617

  However, in the decompression device described in Patent Documents 1 and 2, if the passage axis of the nozzle and the axis of the valve stem are misaligned, the nozzle and the stem are contacted and rubbed, Since the rod cannot move to a predetermined downstream position in the axial direction, the sealing performance cannot be ensured. Moreover, the resistance at the time of moving a valve stem may become large, and malfunction may occur. When such a thing happened, there existed a problem that a decompression device cannot demonstrate performance.

  The present invention has been made in view of the above points, and an object of the present invention is to provide an ejector-type pressure reducing device in which a problem caused by a deviation between a nozzle passage shaft and a valve shaft is reduced.

  Still another object of the present invention is to provide an ejector-type decompression device that can improve the deviation between the passage shaft of the nozzle and the shaft of the valve stem.

In order to achieve the above object, the following technical means are adopted. That is, the first invention has a radiator (3) that dissipates high-pressure refrigerant compressed by the compressor (2) and an evaporator (7) that absorbs heat by evaporating the low-pressure refrigerant, so Is an ejector-type decompression device used in a vapor compression refrigeration cycle that moves the gas to the high temperature side,
A nozzle (23) that decompresses and expands the high-pressure refrigerant, a valve rod (22) that is displaced in the axial direction to adjust the passage opening of the nozzle (23), and a driving force that displaces the valve rod (22) in the axial direction. And a valve stem support member (20) that supports the valve stem (22) and is displaced in the axial direction by the drive portion (15) to displace the valve stem (22) in the axial direction. ) And a pressure increasing section (24, 26) for increasing the pressure while mixing the refrigerant injected from the nozzle (23) and the refrigerant sucked from the evaporator (7), and the valve stem (22) is a valve stem It is characterized by being supported so as to be displaceable with respect to the support member (20).

  According to this invention, even if the axis of the valve stem defined by the valve stem support member is deviated from the passage axis of the nozzle, it is possible to suppress problems caused by the deviation.

  The displacement provided by the present invention is, for example, that the valve stem rotates about its axis with respect to the valve stem support member, that the shaft of the valve stem swings in the radial direction with respect to the valve stem support member, Including one or a combination of a plurality of radial translation of the shaft of the valve stem relative to the support member, and advancing and retreating of the valve stem along the axial direction of the valve stem support member. Yes. The displacement given by the present invention includes one or a combination of a displacement given when the valve stem is separated from the nozzle and a displacement given when the valve stem is in contact with the nozzle.

  The valve stem (22) can be supported by the valve stem support member (20) so as to be movable in the radial direction. According to the present invention, the relative position of the valve stem with respect to the nozzle is adjusted to absorb the misalignment, and an automatic centering function can be provided to the valve stem itself. Can be improved, and problems due to the misalignment of the axis can be suppressed.

  Further, the valve stem (22) is swingably connected to the valve stem support member (20) so that the valve stem (22) is aligned with the passage axis of the nozzle (23) by the flow of the high-pressure refrigerant. It is preferable to provide a coupling mechanism (27, 28, 29). According to the present invention, when the axis of the valve stem support member is deviated from the axis of the nozzle passage, the valve stem can be tilted to adjust the relative position of the valve stem with respect to the nozzle passage. .

  The drive unit includes a magnet rotor (15), and the valve stem support member (20) rotates as the magnet rotor (15) rotates, and the valve stem support member (20) rotates in the axial direction. It is preferable to provide a guide portion (18) for holding the valve stem support member (20) in the radial direction so as to move. According to the present invention, the movement of the valve stem support member in the radial direction can be regulated and stably moved in the axial direction.

  The drive unit includes a magnet rotor (15), and the valve stem support member (20) moves to the nozzle side in the axial direction while rotating with the rotation of the magnet rotor (15). 20) When the valve stem (22) displaced to the nozzle side in the axial direction by 20) is in a position to close the passage of the nozzle (23), the inner diameter dimension of the nozzle (23) in the passage portion closed by the valve stem (22) (X) is preferably larger than the radial dimension (Y) of the portion where the valve stem support member (20) and the valve stem (22) are in contact.

  When the valve stem closes the passage of the nozzle, the rotational force of the magnet rotor acts on the valve stem via the valve stem support member, and the valve stem itself rotates to bite the nozzle. According to the present invention, even in such a situation, the distance from the center of rotation to the surface of the valve stem on which the impulse works is larger in the nozzle passage portion closed by the valve stem. The torque (moment of force) acting on the valve rod does not lose to the torque (moment of force) acting on the valve stem from the valve stem support member. As a result, the valve stem does not rotate after coming into contact with the inner wall of the passage of the nozzle, and the valve stem support member idles with respect to the valve stem, and there is an effect that biting of the valve stem against the nozzle is alleviated.

  Further, the drive unit is provided with a magnet rotor (15), and the valve stem support members (34, 43, 60, 80) move to the axial nozzle side while rotating with the rotation of the magnet rotor (15). When the valve stem (32, 42, 66, 84) displaced to the nozzle side in the axial direction by the valve stem support member is in a position for closing the passage of the nozzle (23), the valve stem of the magnet rotor (15) It is preferable that the member (35, 43, 61, 88) rotated by the rotation is in contact with a point at the end on the side opposite to the nozzle.

  According to this invention, even when the valve stem closes the nozzle passage, the valve stem receives the rotational force by the magnet rotor at a point at the end on the non-nozzle side. Can hardly be transmitted to the valve stem, and the biting of the valve stem against the nozzle can be reduced.

  In addition, it is preferable to provide storage portions (29, 55) in which one of the valve rod support members (20, 50) and the valve rods (22, 53) is housed so that the other part can be displaced. According to the present invention, the valve stem can be easily arranged in the radial direction or the shaft with respect to the valve stem support member by carrying out a design for adjusting the clearance formed between the storage portion and the portion stored in the storage portion. It can be displaceable in the direction or can be configured to be swingable.

  Moreover, it is preferable that the part of the said valve stem (22) supported by contact | abutting with a valve stem support member (20) is formed in the curved surface. According to this invention, the valve stem can be moved smoothly with respect to the valve stem support member.

  Moreover, it is preferable to provide a spherical body (35) separate from the valve stem (40) between the end (41) of the valve stem (40) and the valve stem support member (20). According to this invention, since the sphere for smooth movement of the valve stem is configured separately from the valve stem, it is not necessary to form the sphere on the valve stem, so that the processing of the valve stem can be simplified.

  Moreover, it is preferable to provide an elastic member (21, 33, 90) that is elastically deformed between the valve stem (22, 32, 84) and the valve stem support member (20, 34, 80). According to the present invention, the axial movement of the valve stem when affected by the pressure in the nozzle can be made smoother.

  Moreover, it is preferable to provide an elastic member (33, 119) that biases the valve stem (46, 110) in the anti-nozzle direction. According to this invention, since the force is always acting in the direction of separating the valve stem from the nozzle, it is possible to prevent the valve stem from biting into the nozzle when the valve rod contacts the inner wall of the nozzle.

  Further, it is preferable that an elastic member (33, 119) for urging the valve stem (46, 110) in the anti-nozzle direction is provided, and an isolation member (117) separating the elastic member from the flow path through which the refrigerant flows. According to the present invention, it is possible to provide an elastic member that prevents the valve stem from biting against the nozzle when the valve stem contacts the inner wall of the nozzle and does not affect the refrigerant flow.

  Moreover, it is preferable to provide the elastic member (33) elastically deformed between the valve stem (46) and the nozzle (23). According to the present invention, the elastic force of the elastic member acts directly on both the valve stem and the nozzle, and the force acts in the direction of separating the valve stem from the nozzle, so that the biting of the valve stem against the nozzle can be reduced. .

  In addition, a refrigerant passage (11) for introducing the high-pressure refrigerant from the radiator (3) to the periphery of the valve rod (22) is provided, and the refrigerant passage (11) has the introduction direction of the high-pressure refrigerant as the axis of the valve rod (22). It is preferable that it is provided so as to be shifted with respect to.

  According to the present invention, since the fluid flowing into the upstream portion of the ejector can be swirled, the flow rate of the liquid refrigerant is increased, the boiling is promoted, and the nozzle efficiency is improved. Also, the swirling flow acts to align the valve stem.

  In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment will be described with reference to FIGS. FIG. 1 shows an example of a vapor compression refrigeration cycle provided with an ejector-type decompression device (ejector 10). The vapor compression refrigeration cycle 1 includes a compressor 2, a radiator 3 that radiates heat of the high-pressure refrigerant discharged from the compressor 2, and a decompression device that decompresses and expands the high-pressure refrigerant downstream of the radiator 3. And an evaporator 7 for exchanging heat between the outdoor air and the liquid phase refrigerant, and a gas-liquid separator 5 for separating the refrigerant into a gas phase refrigerant and a liquid phase refrigerant. In the present embodiment, carbon dioxide is used as the refrigerant, and the high-pressure refrigerant discharged from the compressor 2 has a critical pressure or higher. The arrows in FIG. 1 indicate the flow of the refrigerant in the cycle.

  The compressor 2 is driven by an electric motor to suck, compress, and discharge the refrigerant, and can variably control the discharge refrigerant temperature or the discharge refrigerant pressure to be a predetermined value. The compressor 2 is driven by a vehicle running engine via an electromagnetic clutch and a belt, for example, a swash plate type variable displacement compressor capable of continuously variably controlling the discharge capacity by an external control signal. It may be configured.

  The radiator 3 is a heat exchanger that cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 2 and outside air that is forcibly blown by a blower (not shown). When the radiator 3 is used in a hot water heater, the radiator 3 is a water / refrigerant heat exchanger, and the hot water is heated by exchanging heat between the high-pressure refrigerant discharged from the compressor 2 and the hot water. The refrigerant will be cooled.

  The ejector 10 sucks the gas-phase refrigerant evaporated in the evaporator 7 by decompressing and expanding the refrigerant that has flowed through the refrigerant passage 11 connected to the radiator 3, and converts the expansion energy into pressure energy. The suction pressure of the compressor 2 is increased.

  The gas-liquid separator 5 is a separating unit that separates the refrigerant flowing out from the ejector 10 into a gas-phase refrigerant and a liquid-phase refrigerant and stores the refrigerant, and the gas-phase separator portion of the gas-liquid separator 5 is the suction of the compressor 2. The liquid phase refrigerant part of the gas-liquid separator 5 is connected to the evaporator 7. A throttle unit 6 is provided between the liquid phase refrigerant unit and the evaporator 7, and the liquid phase refrigerant flowing out from the gas-liquid separator 5 is decompressed.

  Next, as an example of the ejector according to the present invention, an ejector 10 installed with its axial direction aligned with the vertical direction will be described with reference to FIGS. FIG. 2 is a cross-sectional view showing the internal configuration of the ejector 10. As shown in FIG. 2, the body 25 of the ejector 10 has a high-pressure side refrigerant pipe that forms a refrigerant passage 11 for taking in the refrigerant that has flowed out of the radiator 3 and a refrigerant for taking in the refrigerant that has flowed out of the evaporator 7. A low-pressure refrigerant pipe that forms the passage 12 is connected.

  Inside the body 25, there are mainly a nozzle 23, a valve rod 22 for adjusting the passage opening of the nozzle 23, a magnet rotor 15 for providing a driving force for displacing the valve rod 22 in the axial direction, and a valve rod 22. A valve stem support member 20 to be supported and a mixing unit 24 are provided. The ejector 10 is installed so that the axial direction of the valve rod 22 is substantially vertical.

  On one side (upper side) of the body 25, an actuator 13 having an exciting coil 14 and configured by a stepping motor is provided, and the actuator 13 provides a rotational force to a magnet rotor 15 that is a drive unit. On the other side (lower side) of the body 25, a diffuser portion 26 that forms a pressure increasing portion downstream from the mixing portion 24 is provided.

  One end (upper end) 17 of the valve stem support member 20 is rotatably held by a plate 16 that transmits the rotational force of the magnet rotor 15 to the valve stem support member 20. The valve stem support member 20 is a magnet rotor. It is rotated with 15 rotations. A male screw portion 19 is provided on the outer peripheral portion of the valve stem support member 20. Around the valve stem support member 20, a guide portion 18 having a female screw portion screwed with the male screw portion 19 is fixed. The valve stem support member 20 is rotatably held in the radial direction by the guide portion 18 when the male screw portion 19 is rotatably engaged with the female screw portion, and is smoothly displaced in the axial direction while rotating. become.

  At the other end (lower end) of the valve stem support member 20, the valve stem 22 is aligned with the passage axis of the nozzle 23 by the flow of high-pressure refrigerant. A connecting mechanism that connects the valve stem 22 to the valve stem support member 20 is provided so that at least one of swinging and radial movement with respect to 20 can be performed. That is, the valve stem support member 22 supports the valve stem 20 at least one of being swingable and movable in the radial direction. Thus, the valve stem support member 22 has a holding portion to which the rotational force of the magnet rotor 15 is transmitted to the one end portion 17 (the upper portion in the axial direction), the male screw portion 19 in the middle in the axial direction, and the other side. A connecting mechanism is provided at the end (the lower portion in the axial direction). In other words, the coupling mechanism is a loose coupling means that couples the valve stem 22 to the valve stem support member 20 so as to be displaceable, for example, to be movable in the radial direction. Moreover, it is preferable that a connection mechanism connects so that the valve stem 22 can rotate with respect to the valve stem support member 20 in the circumferential direction.

  By providing such a coupling mechanism, at least one of the following effects can be achieved. That is, when the valve stem 22 is lifted in the axial direction and separated from the valve seat, the valve stem 22 is aligned so as to improve misalignment in the passage of the nozzle 23, The valve rod 22 is free to move in the circumferential direction with respect to the valve stem support member 20 (the valve stem 22 is the valve stem support member 20). Can rotate freely with respect to).

  The valve stem 22 is a tapered valve body (needle-like valve body) supported so as to hang down by the valve stem support member 20, and the inner passage of the nozzle 23 is connected to the wall surface of the inner passage. In a state where a predetermined interval is provided, the axis of the nozzle 23 and the axis of the valve stem 22 are arranged so as to substantially coincide with each other. The throttle opening degree of the nozzle 23 is adjusted by changing the axial position of the valve rod 22 by the operation of the actuator 13, and the pressure of the high-pressure side refrigerant detected by the pressure sensor is detected by the temperature sensor. Control is performed so that the target pressure is determined from the temperature. The target pressure is a refrigerant pressure on the high pressure side that gives the highest coefficient of performance of the ejector cycle with respect to the refrigerant temperature on the high pressure side.

  The nozzle 23 is formed such that the large-diameter passage, the small-diameter passage formed by the large-diameter passage being squeezed by the throat 30 on the downstream side, and the passage cross-sectional area gradually increase from the small-diameter passage toward the downstream. An expansion passage and a refrigerant outlet at the most downstream end of the nozzle 23 are provided. The high-pressure refrigerant that has flowed through the refrigerant passage 11 is decompressed and expanded in an isentropic manner through a small-diameter passage having a small passage area. A large-diameter shaft portion having a large shaft diameter near the valve rod support member 20 of the valve rod 22 is disposed in the large-diameter passage, and a part of the tapered portion on the distal end side of the valve rod 22 is disposed in the small-diameter passage. The throat 30 is formed over the entire circumference of the boundary portion where the large-diameter passage changes to the small-diameter passage.

  The high-pressure refrigerant flowing in through the refrigerant passage 11 is jetted to the periphery of the upper portion of the valve rod 22 and flows through a passage formed between the outer peripheral surface of the valve rod 22 and the inner peripheral surface on the upstream side of the nozzle 23. , Flows into the small diameter passage. The suction part for sucking the gas-phase refrigerant from the evaporator 7 is connected to the refrigerant passage 12 and is disposed so as to communicate with the refrigerant outlet.

  The mixing unit 24 is a flow path provided on the downstream side of the nozzle 23 and the suction unit. The high-speed refrigerant flow from the nozzle 23 and the suction refrigerant from the suction unit are mixed, and the diffuser unit 26 is further downstream. Connected with. The diffuser portion 26 is formed in a shape in which the refrigerant passage area gradually increases, and has a function of decelerating the refrigerant flow to increase the refrigerant pressure, that is, a function of converting the velocity energy of the refrigerant into pressure energy. Further, the mixing unit 24 and the diffuser unit 26 may be collectively referred to as a boosting unit. A gas-liquid separator 5 is connected to the downstream side of the diffuser portion 26 in the refrigerant flow direction.

  FIG. 3 is a partial cross-sectional view illustrating the relationship between the valve stem 22 and the valve stem support member 20. As shown in FIG. 3, the valve stem 22 is arranged so that the axial direction of the valve stem support member 20 coincides with that of the valve stem support member 20. An end portion 27 located at the uppermost portion on the valve stem support member 20 side of the valve stem 22 is housed in a housing portion 29 formed at the lower end portion on the valve stem 22 side of the valve stem support member 20 so as to be in the axial direction. It is supported. With this configuration, the valve stem 22 is held so that the movement in the axial direction is restricted and does not fall off in the axial direction.

  The distance between the inner surfaces in the radial direction of the storage portion 29 is longer than the outer dimension in the radial direction of the end portion 27. Accordingly, the end portion 27 can be displaced in the storage portion 29, and can move in the radial direction until the surface of the end portion 27 collides with the radially inner surface of the storage portion 29 in a state of being disposed in the storage portion 29. Further, the end portion 27 can move in the axial direction until the end portion 27 in the state of being disposed in the storage portion 29 collides with the bottom surface of the storage portion 29 located on the side opposite to the nozzle. The inner surface formed in the radial direction of the storage portion 29 is formed with a curved surface or a flat surface, and the space forming the storage portion 29 is, for example, cylindrical or prismatic.

  The end portion 27 is integrated with the large-diameter shaft portion of the valve stem 22 through a neck portion having a smaller outer dimension than the end portion 27, and is formed by subjecting the valve stem 22 to machining. For example, the end 27 can be formed of a sphere (ball), and the neck can be formed of a shaft having a smaller axial diameter than the diameter of the sphere.

  At the lowermost end of the valve stem support member 20, an arm that abuts against the surface of the end 27 in a state where the valve stem 22 is suspended and supports the end 27 upward against the gravity of the valve stem 22. A portion 28 is provided. The portion of the end portion 27 that is supported by being in contact with the arm portion 28 is preferably formed in a curved surface. For example, the end portion 27 has a substantially cylindrical shape in the axial direction, and the arm portion 28 is further provided. The lower portion in the axial direction that is supported by being in contact with the surface is formed of a curved surface, and the upper portion in the axial direction that is in contact with the elastic member 21 described later is formed of a spherical dome.

  The arm portion 28 has a shape that protrudes in a substantially horizontal direction (radial direction of the valve stem support member 22) so that the cross section thereof faces inward from both outer sides of the lower end portion of the valve stem support member 20. A predetermined gap is formed between the end surfaces of the arm portions 28 to be engaged. This gap is located below the storage portion 29 and is smaller than the outer dimension of the end portion 27 of the valve rod 22. For this reason, the end portion 27 is held so that it does not fall off from the storage portion 29 by the lower portion being supported by the arm portion 28 with the neck portion positioned in the gap. Furthermore, the end portion 27 can move within a range in which the neck portion can move in the radial direction between the opposing end surfaces (gap) of the arm portion 28.

  The end portion 27, the arm portion 28, and the storage portion 29 constitute a coupling mechanism that is coupled so that the valve stem 22 can swing at least one of the valve stem support member 20 and move in the radial direction. is doing. When the valve stem 22 swings with respect to the valve stem support member 20, the valve stem 22 swings in the nozzle 23 with the end portion 27 as a fulcrum while the end portion 27 abuts on the arm portion 28.

  When the valve stem 22 moves in the radial direction with respect to the valve stem support member 20, the end portion 27 is within a range in which the neck portion can move between the opposite end surfaces of the arm portion 28 or between the radial inner surfaces of the storage portion 29. Can move within the nozzle 23 as much as possible. When the lower portion in the axial direction of the end portion 27 that is supported by being in contact with the arm portion 28 is formed in a curved surface, the end portion 27 moves while tilting upward while being in contact with the arm portion 28, 22 translates in the radial direction.

  The valve stem support member 20 includes an opening that communicates with the gap and the storage portion 29 on at least one of the depth side and the near side in FIG. Grooves having a predetermined width extending in the axial direction are formed on the opposite end surfaces of the arm portion 28. This groove extends from the lower end in the axial direction of the opposing end face of the arm portion 28 to the storage portion 29. The circumferential shape of the groove on the storage portion 29 side is preferably a shape that follows the outer shape of the end portion 27. The end portion 27 is held in the storage portion 29 by being placed in the groove. The storage portion 29 is formed by processing the valve stem support member 20 with a T slow cutter. When installing the end portion 27 of the valve stem 22 in the storage portion 29, the neck portion and the end portion 27 are inserted into this opening portion, and the end portion 27 is placed in a state where the neck portion is positioned between the opposing end surfaces of the arm portion 28. Place in the groove. By placing the end portion 27 in the groove, the groove is positioned so as to sandwich the outer periphery of the end portion 27 from both sides, and the end portion 27 is restricted from moving in the radial direction.

  Inside the valve stem support member 20, a recess having a smaller radial dimension than the storage portion 29 is provided above the storage portion 29. In this recess, the elastic member 21 is provided in a stable state. The depth of the recess is formed smaller than the natural length of the elastic member 21. The elastic member 21 is installed in a state where it abuts both the end portion 27 of the valve stem 22 and the bottom surface of the concave portion and its axial dimension is smaller than the natural length. The elastic member 21 is elastically deformed in the axial direction between the end portion 27 and the valve rod support member 20 according to the displacement of the valve rod 22 in the axial direction, and an elastic force is applied to the valve rod 22 in the axial direction. With this configuration, the driving force that causes the magnet rotor 15 to move the valve stem support member 20 in the axial direction can be transmitted to the valve stem 22 as it is. The elastic member 21 can be constituted by a member formed of a metal such as a spring spring or a plate spring, or a member formed of an elastic material such as an elastomer.

  When the valve stem support member 20 rotates while being held by the guide portion 18 by the driving force provided by the magnet rotor 15 and moves downward in the axial direction (axial nozzle 23 side), the valve stem 22 is displaced downward in the axial direction. And when the displacement amount of the valve stem 22 is large, or when the axis of the valve stem 22 and the flow axis of the nozzle 23 are shifted, the valve stem 22 bites against the inner wall surface of the flow path of the nozzle 23, The valve stem 22 may be worn out.

  At this time, an axially upward force repelling the force pushed downward in the axial direction by the elastic member 21 acts on the valve rod 22, and the end portion 27 of the valve rod 22 moves upward in the axial direction. It will contact | abut to the bottom face of 29, and the opening edge part of a recessed part.

  Since the end portion 27 is formed of a spherical dome at the upper portion in the axial direction as described above, the end portion 27 does not come into contact with the bottom surface of the storage portion 29 but comes into line contact with the opening end portion of the recess. Thus, the contact area of the end 27 is small, and the valve stem 22 is supported so as to be freely rotatable in the circumferential direction with respect to the valve stem support member 20. The movement of the valve stem support member 20 can be prevented from being transmitted to the valve stem 22 and the bite and wear of the valve stem 22 can be prevented from being promoted.

  The coupling mechanism of this embodiment supports the valve stem 22 so as to be displaceable with respect to the valve stem support member 20. The valve stem 22 is separated from the nozzle, and the valve stem 22 is seated on the nozzle. In both cases, the shaft of the valve stem 22 is allowed to swing in the radial direction with respect to the valve stem support member 20. The coupling mechanism allows the shaft of the valve stem 22 to swing with respect to the valve stem support member 20 around the spherical end portion 27. The coupling mechanism allows the valve stem 22 to slightly move back and forth along the axial direction with respect to the valve stem support member 20 when the valve stem 22 is in contact with the nozzle. Further, the coupling mechanism allows the valve stem 22 to rotate around its axis with respect to the valve stem support member 20 when the valve stem 22 is in contact with the nozzle.

  In this way, the valve stem 22 is further swung so that the portion for adjusting the passage opening degree of the nozzle 23 is movable in the radial direction (radial direction) while its movement is restricted in the axial direction by the valve stem support member 20. Supported as possible. Further, the valve stem 22 may be configured to freely move in a direction other than the axial direction with respect to the valve stem support member 20 provided with a driving force for displacing the valve stem 22 in the axial direction. The valve stem 22 is freely movable so that its tapered portion is displaced in the radial direction (direction perpendicular to the axial direction) with the portion supported by the valve stem support member 20 being supported as a substantial fulcrum. Further, the valve stem 22 can be swung in such a posture that its axial direction is inclined with respect to the vertical direction. For example, a portion supported by the valve stem support member 20 in contact with the valve stem 22 is supported as a pendulum. Can exercise.

  For example, when the accuracy of each component of the ejector 10 is not appropriate or due to an incomplete assembly process, the shaft of the nozzle 23 or the passage shaft of the nozzle 23 and the shaft of the valve stem support member 20 (the valve stem support member 20 The shaft of the male screw portion 19 may be misaligned, or the axial direction of the valve stem support member 20 or the valve stem 22 may be inclined. In this case, as shown in FIG. 4, the valve stem 22 comes into contact with the nozzle 23, and the valve stem 22 is arranged with the throat 30 of the nozzle 23 as a fulcrum. FIG. 4 is a cross-sectional view showing a state in which the axis of the valve stem support member 20 is displaced in the ejector 10 and the valve stem 22 is in contact with the nozzle 23 (throat part 30).

  Even when the valve stem 22 is in the state shown in FIG. 4, the valve stem 22 is supported by the valve stem support member 20 that is displaced up and down so that the valve stem 22 can move in the radial direction and can be swung. It can move in the flow path space of the nozzle 23 with 30 as a fulcrum. In this manner, the valve stem 22 moves away from the passage wall surface when it contacts the passage wall surface of the nozzle 23 and is aligned.

  The end 27 of the valve stem 22 is formed in a particularly spherical shape, so that the valve stem 22 can move smoothly in the radial direction or in the circumferential direction around the end 27. A valve transmitted by the magnet rotor 15 in a state where the valve rod 22 abuts against the inner wall surface forming the flow path of the nozzle 23 and closes the flow path by smooth movement of the valve rod 22. The driving torque of the rod support member 20 is transmitted as the rotational torque of the valve rod 22 with respect to the nozzle 23, so that it can be prevented from being twisted, biting and wearing, and the sealing performance of the flow path being lowered.

  When the magnet rotor 15 continues to rotate in one direction, the valve stem support member 20 is displaced in the axial direction while rotating, and thereby the valve stem 20 is also displaced toward the nozzle side to close the passage of the nozzle 23. Move to position. When the valve stem 22 is in this position and the passage of the nozzle 23 is closed, as shown in FIG. 5, the inner diameter dimension X of the nozzle 23 in the passage portion closed by the valve stem 22 is the same as that of the valve stem support member 20. It is a dimension larger than the radial dimension Y of the part where the valve stem 22 contacts.

  The inner diameter dimension X of the nozzle 23 is the diameter of a circle drawn by the throat 30 of the nozzle 23, and is also the diameter of the tapered portion on the distal end side of the valve rod 22 inserted into the throat 30. The radial dimension Y is a radial dimension of a portion where the opposite nozzle side of the end 27 of the valve rod 22 contacts the storage chamber 29.

  By forming the nozzle 23 so that the inner diameter dimension X of the nozzle 23 is larger than the radial dimension Y of the portion where the valve stem support member 20 and the valve stem 22 are in contact with each other, the valve stem 22 is Even when the passage of the nozzle 23 is closed, the distance from the center of rotation to the surface of the valve rod 22 on which the impulse works is greater in the passage portion having the inner diameter dimension X than in the portion having the radial dimension Y. growing. For this reason, due to the action of torque, the torque (moment of force) acting on the tapered portion of the valve stem 22 does not lose to the torque (moment of force) acting on the valve stem 22 from the valve stem support member 20. Does not rotate any more after the passage of the nozzle 23 is closed, and the valve stem support member 20 is idled with respect to the valve stem 22 and the bite of the valve stem 22 is stopped.

  Next, the structure of the valve stem 50 and the valve stem support member 53 which are modifications of the valve stem 22 and the valve stem support member 20 will be described with reference to FIG. The modification shown in FIG. 6 has a configuration in which the end portion 52 of the valve stem 50 is slidably accommodated and supported in a storage portion 55 provided on the valve stem support member 53. The valve stem support member 53 includes an elastic member 54 that cushions the movement of the valve stem 50 in the axial direction, and an arm portion 56 that abuts the end surface 52 of the valve stem 50 opposite to the nozzle side with the neck portion 51 interposed therebetween. Yes. The elastic member 54 is a component similar to the elastic member 21 described above, and the arm portion 56 has the same configuration as the arm portion 28.

  Next, the automatic centering action of the valve stem 22 utilizing the pressure balance in the flow path of the nozzle 23 will be described with reference to FIG. 7 showing the relationship between the pressure of the flow path of the nozzle 23 and the valve stem 22. FIG. 7 shows only the relationship between the flow path portion of the nozzle 23 and the valve rod 22 where the refrigerant passage area changes for convenience of explanation.

  As shown in FIG. 7, the outer peripheral surface of the valve stem 22 is formed with the inner wall surface of the flow path of the nozzle 23 in the Mach portion 31 where the Mach region of the refrigerant flow is formed in the downstream region from the throat portion 30 due to some cause. The distance may be uneven in the circumferential direction. In this case, the pressure of the refrigerant flowing through the shorter distance (upper side in FIG. 4) becomes higher than the pressure of the refrigerant flowing through the longer side (lower side in FIG. 4).

  At this time, since the refrigerant flowing through the Mach portion 31 tends to balance the pressure, the valve rod 22 is subjected to an external force from the higher pressure refrigerant toward the axial center of the valve rod 22, and the tapered portion of the valve rod 22 The portion where the rod 22 is supported by being in contact with the valve stem support member 20 is moved so that the distance is evenly approximated in the circumferential direction (in the automatic alignment direction). With this action, the performance of the ejector 10 as a single unit, particularly the boosting performance is enhanced. Further, since the Mach portion 31 has a long influence length, the moment effect for returning the valve rod 22 toward the flow path axis of the nozzle 23 is large.

  As described above, the valve rod 22 is acted on the valve rod 22 by an action force that always balances the refrigerant pressure in the Mach portion 31 at the radial position of the valve rod 22. Therefore, in combination with the configuration in which the valve stem 22 is supported by the valve stem support member 20 so as to be movable in the radial direction and swingable, the passage of the nozzle 23 when the valve stem 22 is moved up and down (lifted) in the axial direction. The alignment (automatic alignment performance) to improve misalignment is promoted. The applicant has confirmed this effect by a visualization experiment.

  In the present embodiment, the valve stem support member 20 employs a coupling mechanism that supports the valve stem 22 so that the valve stem 22 can move in the radial direction or swingably, so that the relative position of the valve stem 22 with respect to the nozzle 23 is increased. The misalignment is absorbed and the misalignment of the shaft center of the valve stem 22 with respect to the nozzle 23 can be improved, and a problem due to the misalignment of the shaft center can be suppressed. With this configuration, when the valve stem 22 is moved up and down (lifted) in the axial direction, it is aligned so as to improve misalignment in the passage of the nozzle 23, and the valve stem 22 contacts the passage wall surface of the nozzle 23. At least one of the effects of moving and aligning sometimes away from the wall surface of the passage and being able to freely rotate the valve stem 22 with respect to the valve stem support member 20 is achieved.

  Further, the end portion 27 of the valve stem 22 is formed in a spherical shape, and the end portion 27 is disposed in the storage portion 29 and supported by the arm portion 28, whereby the valve stem 22 is caused to flow through the nozzle 23 by the flow of high-pressure refrigerant. A coupling mechanism that couples the valve stem 22 to the valve stem support member 20 in a swingable manner is configured so as to be aligned with the center.

  When this configuration is adopted, when the shaft center of the valve stem support member 20 is deviated from the passage shaft center of the nozzle 23, the refrigerant flowing around the valve stem 22 tries to balance the pressure in the valve stem 22. The relative position of the valve stem 22 with respect to the passage of the nozzle 23 can be adjusted by swinging the valve stem 22 and inclining it with respect to the valve stem support member 20 by utilizing the action. In particular, since the valve stem 22 is swingably supported by the valve stem support member 22, the deviation between the passage shaft of the nozzle 23 and the shaft of the valve stem 20 can be improved by tilting the valve stem 20 very small.

  Further, the ejector 10 includes a magnet rotor 15 as a drive component, and rotates the valve stem support member 20 as the magnet rotor 15 rotates, so that the valve stem support member 20 moves in the axial direction while rotating. The guide portion 18 for holding the valve stem support member 20 in the radial direction is provided. When this configuration is adopted, the movement of the valve stem support member 20 in the radial direction can be restricted and stably moved in the axial direction.

  In addition, the valve stem support member 20 includes a storage portion 29 in which the end portion 27 of the valve stem 22 is stored so that the valve stem 22 does not fall off in the axial direction. When this configuration is employed, the valve stem 22 can be stably held in the axial direction.

  The portion of the valve stem 22 that is supported in contact with the valve stem support member 20 is formed by a curved surface such as a spherical surface. When this configuration is adopted, the contact area of the valve stem 22 can be reduced, or the sliding of the contact portion can be made smooth, and the valve stem 22 can be moved smoothly with respect to the valve stem support member 20. Can do.

(Second Embodiment)
In the second embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 8 is a partial cross-sectional view showing the configuration of the valve stem 32 and the valve stem support member 34 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The valve stem 32 and the valve stem support member 34 are different from the first embodiment in that a sphere 35 is provided between the end portion 38 of the valve stem 32 and the valve stem support member 34. The point which caulked the lower end part, and the arrangement | positioning location of an elastic member mainly differ. This embodiment is the same as the first embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 8, the valve stem 32 is arranged so that the axial direction of the valve stem support member 34 coincides with that of the valve stem support member 34. An end portion 38 positioned at the uppermost portion on the valve rod support member 34 side of the valve rod 32 is housed in a housing portion formed at a lower end portion on the valve rod 32 side of the valve rod support member 34 so as to be in the axial direction. It is supported. With this configuration, the valve stem 32 is held so that the movement in the axial direction is restricted and does not fall off in the axial direction.

  The end portion 38 is integrated with the large-diameter shaft portion of the valve stem 32 through a neck portion having a smaller outer dimension than the end portion 38. The valve stem support member 34 is a substantially cylindrical body having an axial end face opened, and a lowermost end portion thereof includes an annular spacer 39 that supports an end portion 38 of the valve stem 32 from below. The spacer 39 has an inner ring whose diameter is larger than the outer diameter of the end portion 38, and its outer peripheral portion is pressed and fixed by a caulking portion 37. The caulking portion 37 is caulked so that the cross-sectional shape of the caulking portion 37 protrudes inward from both outer sides of the lowermost end portion of the valve stem support member 34. The valve stem 32 is held so that it does not fall off from the storage portion by the lower portion of the end portion 38 being supported by the spacer 39 in a state where the neck portion of the valve stem 32 is positioned inside the annular spacer 39.

  A sphere 35 placed on the upper end surface 36 of the end portion 38 is provided between the end portion 38 and the bottom surface of the storage portion. In a state where the end portion 38 is supported by being in contact with the spacer 39, a predetermined gap is formed between the surface of the sphere 35 and the bottom surface of the storage portion. The spherical body 35 is a member that is rotated together with the valve stem support member 34 by the rotation of the magnet rotor 15.

  An elastic member 33 is provided in a stable state around the neck of the valve stem support member 32. The elastic member 33 is installed in contact with both the spacer 39 and the top surface of the large-diameter shaft portion of the valve stem 32, and the large-diameter shaft end of the spacer 39 and the valve stem 32 according to the axial displacement of the valve stem 32. It is elastically deformed between the parts in the axial direction, and an elastic force is applied to the valve stem 32 in the axial direction. The distance between the spacer 39 and the top surface of the large-diameter shaft portion of the valve stem 32 is smaller than the natural length of the elastic member 33. With this configuration, the driving force that causes the magnet rotor 15 to move the valve stem support member 34 in the axial direction can be transmitted to the valve stem 32 as it is.

  The elastic member 33 is made of, for example, a member formed of a metal such as a spring spring or a plate spring arranged in a form in which a neck portion is arranged at an axial center position, or a member formed of an elastic material such as an elastomer. Can do. In this way, the valve rod 32 is supported by the valve rod support member 34 so as to be movable in the radial direction while the movement of the valve rod 32 is regulated in the axial direction while the passage opening degree of the nozzle 23 is adjusted.

  When the valve stem support member 34 is moved in the axial direction by the driving force provided by the magnet rotor 15, the displacement amount of the valve stem 32 is large, or the shaft of the valve stem 32 and the flow axis of the nozzle 23 are shifted. In some cases, the valve stem 32 may bite or wear against the inner wall surface of the nozzle 23.

  At this time, the valve rod 32 is subjected to an axially upward force that repels the force pushed axially downward (on the axial nozzle 23 side) by the elastic member 33, and the end 38 of the valve rod 32 is axially upward. Finally, the upper end 36 comes into contact with the sphere 35. Since the contact between the end portion 38 and the sphere 35 is a point contact, the contact area of the end portion 38 is small, so that the rotational torque of the valve stem support member 34 can be suppressed from being transmitted to the valve stem 32, and the valve stem 32 bites. And the promotion of wear can be prevented.

  The distance between the inner surfaces in the radial direction of the storage portion is longer than the outer dimension in the radial direction of the end portion 38. Thereby, the end portion 38 can be translated in the radial direction until the surface of the end portion 38 collides with the inner surface in the radial direction of the storage portion. Further, the end portion 38 can be translated within a range in which the neck portion of the valve stem 32 can move radially between the inner ring wall surfaces of the spacer 39. In this way, the valve stem 32 can be translated in the nozzle 23 as much as possible.

  When the end portion 38 of the valve stem 32 is installed in the storage portion, the elastic member 33 is disposed in advance between the spacer 39 and the end portion of the large-diameter shaft portion of the valve stem 32, and between the end portion 38 and the elastic member 33. The spacer 39 is arranged. Then, the end portion 38 is inserted into the storage portion in the axial direction in a state where the sphere 35 is disposed in the storage portion, and after the spacer 39 is provided at a predetermined position, the caulking process for forming the caulking portion 37 is performed.

  As described above, in this embodiment, the sphere 35 that is configured separately is provided between the end portion 38 of the valve stem 32 and the valve stem support member 34, so that the sphere that makes the movement of the valve stem 32 smooth is provided as the valve stem 32. Therefore, the processing of the valve stem 32 can be simplified.

(Third embodiment)
In the third embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 9 is a partial cross-sectional view showing the configuration of the valve stem 40 and the valve stem support member 20 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The valve stem 40 and the valve stem support member 20 are different from the first embodiment in that a sphere 35 (similar to the second embodiment) is provided between the end 41 of the valve stem 40 and the valve stem support member 20. The main difference is that the portion of the end portion 41 supported by the arm portion 28 is not a spherical surface but a plane. This embodiment is the same as the first embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 9, the valve stem 40 is disposed so that the axial directions of the valve stem support member 20 and the valve stem coincide with each other. An end portion 41 positioned at the uppermost portion on the valve stem support member 20 side of the valve stem 40 is housed in a housing portion formed at a lower end portion on the valve stem 40 side of the valve stem support member 20 so as to be in the axial direction. It is supported. With this configuration, the valve stem 40 is held so that movement in the axial direction is restricted and does not fall off in the axial direction.

  The end portion 41 is integrated with a large-diameter shaft portion of the valve stem 40 via a neck portion having a smaller outer dimension than the end portion 41, and is formed by cutting and processing the valve stem 40. The end portion 41 is held so that the lower portion thereof is supported from below by the arm portion 28 so as not to drop out of the storage portion. The end portion 41 is supported by the arm portion 28 so as to be movable in the radial direction.

  The distance between the radially inner surfaces of the storage portion is longer than the radial dimension of the end portion 41. As a result, the end 41 can be translated in the radial direction until the surface of the end 41 collides with the inner surface in the radial direction of the storage unit. In this way, the valve stem 40 can be translated in the nozzle 23 as much as possible.

  A sphere 35 is provided between the end portion 41 and the bottom surface of the storage portion of the valve stem support member 20 so as to be placed on the upper end surface of the end portion 41. As in the first embodiment, the elastic member 21 is provided in a stable state in the recess or groove formed above the storage portion inside the valve stem support member 20. When the end portion 41 of the valve stem 40 is installed in the storage portion, it is performed in the same manner as in the first embodiment.

  Similar to the above embodiment, when the valve stem 40 bites or contacts the flow path of the nozzle 23, the valve stem 40 moves upward in the axial direction and contacts the sphere 35. At this time, the contact between the end portion 41 and the sphere 35 is a point contact, and the contact between the sphere 35 and the opening end portion of the recess is a line contact (similar to the first embodiment), and therefore both of these contact areas are small. Therefore, transmission of the rotational torque of the valve stem support member 20 to the valve stem 40 can be suppressed, and biting of the valve stem 40 and promotion of wear can be prevented.

(Fourth embodiment)
In the fourth embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 10 is a partial cross-sectional view showing the configuration of the valve stem 42 and the valve stem support member 43 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The valve stem 42 and the valve stem support member 43 are mainly different from the second embodiment in that a sphere is not provided between the end portion 38 of the valve stem 42 and the valve stem support member 43. This embodiment is the same as the second embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 10, the valve stem 42 is disposed so that the axial direction of the valve stem support member 43 coincides with that of the valve stem support member 43. A spherical body is not provided between the end portion 38 of the valve stem 42 and the bottom surface of the storage portion of the valve stem support member 43, and instead, a spherical portion is formed on a part of the top surface of the end portion 38. Other configurations and operational effects are the same as in the second embodiment.

  Similar to the above embodiment, when the valve stem 42 bites or contacts the flow path of the nozzle 23, the end portion 38 of the valve stem 42 moves upward in the axial direction and contacts the bottom surface of the storage portion. At this time, since the contact between the spherical portion of the end portion 38 and the bottom surface of the storage portion is a point contact, since the contact area is small, it is possible to suppress transmission of the rotational torque of the valve stem support member 43 to the valve stem 42, It is possible to prevent biting and wear of the valve stem 42 from being promoted.

(Fifth embodiment)
In the fifth embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 11 is a partial cross-sectional view showing the configuration of the valve stem 66 and the valve stem support member 60 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The valve stem 66 and the valve stem support member 60 have a cylindrical portion that is integral with the valve stem support member 60 and protrudes toward the head 67 of the valve stem 66 with respect to the first embodiment. The main difference is that a spherical portion 61 is provided at the tip. This embodiment is the same as the first embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 11, the valve stem 66 is arranged so that the axial direction of the valve stem support member 60 coincides with each other. At the lowermost end of the valve stem support member 60, the valve stem 66 is in contact with the surface of the head 67 close to the neck 69, and the head 67 is moved upward against the gravity of the valve stem 66. An arm portion 64 is provided to be supported. A portion 68 of the head 67 that is supported in contact with the arm portion 64 is formed of a curved surface. The head 67 has a substantially cylindrical shape in the axial direction, and the end surface on the side opposite to the nozzle is formed by a plane orthogonal to the axis of the valve stem 66.

  The valve stem support member 60 includes a storage portion 63 that stores the head 67 in a displaceable manner. The storage unit 63 has the same configuration as the storage unit 29 of the first embodiment, and performs the same function.

  The valve stem support member 60 includes a recess 62 that is formed to be recessed from the bottom surface 65 located on the side opposite to the nozzle of the storage portion 63 to the side opposite to the nozzle. The cylindrical portion of the valve stem support member 60 that protrudes toward the head 67 of the valve stem 66 is located in the recess 62, and the tip thereof is a spherical portion 61 that protrudes from the recess 62 into the space formed by the storage portion 63. The spherical portion 61 is a member that is rotated together with the valve stem support member 60 by the rotation of the magnet rotor 15.

  The cylindrical portion is provided with an elastic member 71 so as to surround the periphery thereof. The elastic member 71 is disposed so as to be elastically deformed between the bottom surface of the recess 62 on the side opposite to the nozzle and the end surface of the head 67 on the side opposite to the nozzle.

  The distance between the inner surfaces in the radial direction of the storage portion 63 is longer than the outer dimension in the radial direction of the head 67. As a result, the head 67 can be displaced in the storage portion 63 and can move in the radial direction until the surface of the head 67 collides with the radially inner surface of the storage portion 63 in a state of being disposed in the storage portion 63. The inner surface formed in the radial direction of the storage unit 63 is formed with a curved surface or a flat surface, and the space forming the storage unit 63 is, for example, a cylindrical shape or a prismatic shape. Further, the head 67 can move within a range in which the neck 69 can move in the radial direction between the opposing end surfaces (gap) of the arm 64.

  The valve stem 66 moves to the anti-nozzle side while resisting the elastic force of the elastic member 71 until the end face on the anti-nozzle side collides with the spherical surface portion 61 of the cylindrical part in the state where it is arranged in the storage part 63. Can do. In a normal state where the valve stem 66 does not close the passage of the nozzle 23, the axial distance between the end surface of the valve stem 66 on the side opposite to the nozzle and the spherical portion 61 of the cylindrical portion is the large diameter of the valve stem 66. This is shorter than the axial distance between the shoulder portion 70 formed between the neck portion 69 and the neck portion 69 and the nozzle side end surface of the valve stem support member 60.

  Due to this distance relationship, when the valve stem 66 contacts the flow path of the nozzle 23, the head 67 of the valve stem 66 moves upward in the axial direction and comes into contact with the spherical surface portion 61 of the cylindrical portion. At this time, the contact between the head portion 67 and the arm portion 64 is released, and the contact between the head portion 67 and the spherical surface portion 61 is a point contact. Therefore, since the contact area is small, the rotational torque of the valve stem support member 60 is controlled by the valve. Transmission to the rod 66 can be suppressed, and biting of the valve rod 66 and the promotion of wear can be suppressed.

(Sixth embodiment)
In the sixth embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 12 is a partial cross-sectional view showing the configuration of the valve stem 84 and the valve stem support member 80 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The valve stem 84 and the valve stem support member 80 are different from the fifth embodiment in that the shape of the head 85 of the valve stem 84 is a sphere, and the head 85 instead of the cylindrical portion of the valve stem support member 80. The difference is that a plate 88 is provided between the elastic member 90 and the elastic member 90. This embodiment is the same as the fifth embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 12, the valve stem 84 is disposed so that the axial direction of the valve stem support member 80 coincides with that of the valve stem support member 80. At the lowermost end of the valve stem support member 80, the valve stem 84 is in contact with the surface near the neck 86 of the head 85 in a suspended state, and the head 85 is moved upward against the gravity of the valve stem 84. An arm portion 83 is provided to be supported. A portion of the head 85 that is supported by being in contact with the arm 83 is formed by a curved surface.

  The valve stem support member 80 includes a storage portion 82 that stores the head 85 in a displaceable manner. The storage unit 82 has the same configuration as the storage unit 29 of the first embodiment, and performs the same function.

  The valve stem support member 80 includes a recess formed by denting the bottom surface 81 located on the side opposite to the nozzle of the storage portion 82 to the side opposite to the nozzle. The elastic member 90 is disposed so as to be elastically deformed between the bottom surface of the recess opposite to the nozzle and the end surface 89 of the plate 88 opposite to the nozzle.

  The distance between the inner surfaces in the radial direction of the storage portion 82 is longer than the outer dimension in the radial direction of the head 85. Accordingly, the head 85 can be displaced in the storage portion 82 and can move in the radial direction until the surface of the head 85 collides with the radial inner surface of the storage portion 82 in a state of being disposed in the storage portion 82. The inner surface formed in the radial direction of the storage part 82 is formed by a curved surface or a flat surface, and the space forming the storage part 82 is, for example, cylindrical or prismatic. Further, the head 85 can move within a range in which the neck 86 can move in the radial direction between the opposing end surfaces (gap) of the arm 83.

  While the valve stem 84 is disposed in the storage portion 82, it resists the elastic force of 90 of the elastic member until the end surface 89 on the side opposite to the nozzle of the plate 88 collides with the bottom surface 81 on the side opposite to the nozzle of the storage portion 82. It can move to the non-nozzle side. In a normal state where the valve stem 66 does not close the passage of the nozzle 23, the axial distance between the end surface 89 on the side opposite to the nozzle of the plate 88 and the bottom surface 81 is the large diameter portion of the valve stem 84 and the neck portion 86. The axial distance between the shoulder portion 87 formed between the nozzle portion and the nozzle side end surface of the valve stem support member 80 is shorter. The plate 88 is a member that is rotated together with the valve stem support member 80 by the rotation of the magnet rotor 15.

  Due to this distance relationship, when the valve stem 84 comes into contact with the flow path of the nozzle 23, the plate 88 in contact with the head 85 of the valve stem 84 moves upward in the axial direction and comes into contact with the bottom surface 81. . At this time, the contact between the head 85 and the arm 83 is released, and the contact between the head 85 and the plate 88 integrated with the valve stem support member 80 is a point contact. Even if the rod support member 80 and the plate 88 rotate as one body, transmission of the rotational torque of the valve rod support member 80 to the valve rod 84 can be suppressed, and the biting of the valve rod 84 and the promotion of wear can be suppressed. Can do.

(Seventh embodiment)
In the seventh embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 13 is a partial cross-sectional view showing the configuration of the valve stem 107 and the valve stem support member 100 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  Compared to the fifth embodiment, the valve stem 107 and the valve stem support member 100 are not provided with the cylindrical portion of the valve stem support member 60, and the curvature of the surface of the neck portion 106 of the valve stem 107 is recessed toward the axis. The main difference is that the surface is formed. This embodiment is the same as the first embodiment in the other configurations and has the same functions and effects.

  As shown in FIG. 13, the valve stem 107 is disposed so that the axial direction of the valve stem support member 100 coincides with that of the valve stem support member 100. At the lowermost end of the valve stem support member 100, the valve stem 107 is in a suspended state and abuts against a portion 105 near the neck portion 106 of the head 104, and the head 104 is held against the gravity of the valve stem 107. An arm portion 103 that is supported upward is provided. A portion 105 of the head 104 that is supported in contact with the arm 103 is formed of a curved surface. The valve stem support member 100 includes a storage portion 102 that stores the head 104 in a displaceable manner. The storage unit 102 has the same configuration as the storage unit 29 of the first embodiment, and performs the same function.

  The valve stem support member 100 is provided with a concave portion that is recessed from the bottom surface 101 located on the side opposite to the nozzle of the storage portion 102 to the side opposite to the nozzle. The elastic member 109 is disposed so as to be elastically deformed between the bottom surface of the recess opposite to the nozzle and the end surface 101 of the head 104 opposite to the nozzle.

  The distance between the inner surfaces in the radial direction of the storage portion 102 is longer than the outer dimension in the radial direction of the head 104. Accordingly, the head 104 can be displaced in the storage portion 102 and can move in the radial direction until the surface of the head 104 collides with the radially inner surface of the storage portion 102 in a state where the head 104 is disposed. The inner surface formed in the radial direction of the storage unit 102 is formed with a curved surface or a flat surface, and the space forming the storage unit 102 is, for example, cylindrical or prismatic. Furthermore, the head 104 can move within a range in which the neck 106 can move in the radial direction between the opposing end faces (gap) of the arm 103.

  The neck portion 106 is formed so that the head portion 104 side and the large diameter portion side are thicker than the intermediate portion therebetween. From the intermediate part to the head 104 side and from the intermediate part to the base part on the large diameter part side, the diameter is gradually increased so that the surface exhibits a curved surface that spreads toward the end.

  The valve stem 107 is placed on the anti-nozzle side while resisting the elastic force of the elastic member 109 until the base portion of the neck portion 106 collides with the bottom surface of the anti-nozzle side of the storage portion 102 in a state where the valve stem 107 is arranged. Can move. In a normal state where the valve rod 107 does not close the passage of the nozzle 23, the axial distance C1 between the base portion of the neck portion 106 and the bottom surface of the storage portion 102 on the side opposite to the nozzle is the nozzle side of the head portion 104. The axial distance C2 between the end surface 108 and the bottom surface 101 of the storage portion 102 is shorter.

  Due to this distance relationship, when the valve stem 107 comes into contact with the flow path of the nozzle 23, the root portion of the neck portion 106 comes into contact with the bottom surface of the storage portion 102 on the side opposite to the nozzle. At this time, the contact between the head portion 104 and the arm portion 103 is released, and the valve stem 107 comes into contact with the nozzle side end portion of the arm portion 103 at the base portion of the neck portion 106 formed by a curved surface. For this reason, the valve stem 107 is supported so as to be movable or swingable in the radial direction.

  Further, the contact between the base portion of the neck portion 106 and the nozzle side end portion of the arm portion 103 is a line contact, and since the contact area is small, the transmission of the rotational torque of the valve stem support member 100 to the valve stem 107 is suppressed. This can suppress the biting of the valve stem 107 and the promotion of wear.

(Eighth embodiment)
In the eighth embodiment, an ejector including a swirling flow forming means for forming a swirling flow of refrigerant in a flow path formed inside the body 44 will be described with reference to FIGS. 14 and 15. FIG. 14 is a partially cutaway schematic sectional view showing the configuration of the swirl flow forming means. FIG. 15 is a schematic cross-sectional view of the cut surface in FIG. 14 viewed from the XV direction.

  The swirl flow forming means is configured by the positional relationship between the valve rod 22 and the refrigerant passage 11 for introducing the high-pressure refrigerant from the radiator 3 into the vicinity of the valve rod 22. The refrigerant passage 11 is provided so as to shift the introduction direction of the high-pressure refrigerant with respect to the axial center of the valve rod 22, and the high-pressure refrigerant passes through the nozzle 23 that forms a flow path with the outer peripheral surface of the valve rod 22. It is introduced around the valve stem 22 along the inner peripheral surface. Further, the refrigerant passage 11 may be arranged so that the introduction direction of the high-pressure refrigerant is obliquely downward with respect to the axial direction of the valve rod 22.

  More specifically, the refrigerant passage 11 is a flow path through which the refrigerant flows in a direction substantially orthogonal to the axial direction of the valve stem 22 as shown in FIGS. 14 and 15. The valve rod 22 is provided at a position shifted in the radial direction.

  The refrigerant that has flowed into the body 44 from the refrigerant passage 11 approaches the axis of the valve stem 22 while flowing in an arc along the inner wall surface of the body 44. Then, it turns around the valve stem 22 and further descends in the nozzle 23 toward the mixing portion 24 while forming a spiral flow in the flow path between the valve stem 22 and the inner peripheral surface of the nozzle 23. .

  FIG. 16 is a perspective view schematically showing the velocity vector of the swirling flow (broken line in FIG. 16) formed by the swirling flow forming means of this embodiment. As shown in FIG. 16, the gas-liquid two-phase refrigerant that has flowed into the vicinity of the valve rod 22 in the ejector 10 through the refrigerant flow channel 11 receives the centrifugal force that acts outward in the radial direction of the valve rod 22. The refrigerant flow having the actual velocity vector V is formed by turning the valve shaft 22 obliquely downward so as to turn around the valve rod 22. At this time, the liquid refrigerant mainly turns. This is because liquid refrigerant is easily affected by inertial force.

  Here, the velocity vector V is a resultant force of the velocity vector component V1 in the flow channel axis direction and the velocity vector component V2 in the radial direction of the flow channel. Further, since the flow rate of the refrigerant flowing through the flow path is the same regardless of whether or not the swirl flow is generated, the speed vector component V1 is equal to the speed vector component in the flow path axis direction of the flow that does not swirl. That is, the absolute value V of the actual refrigerant speed when the swirl flow is generated is larger than the absolute value of the refrigerant speed in the flow path axis direction when the swirl flow is not generated.

  Therefore, when the swirl flow is generated, the relative refrigerant flow velocity in the flow path is increased, and it is easy to receive disturbance from the inner wall surface of the flow path (the inner peripheral surface of the nozzle 23). Boiling will be promoted. As a result, the expansion loss energy that can be recovered by the nozzle 23 is increased, and the nozzle efficiency is improved. Furthermore, since the swirl flow formed by the swirl flow generating means is a swirl flow that spirally travels around the valve rod 22, the relative position of the valve rod 22 with respect to the passage in the nozzle 23, in other words, It is possible to appropriately correct the position of the shaft center of the valve stem 22 with respect to the axis of the passage in the nozzle 23 so as to be close to the same axis, thereby assisting the automatic centering operation of the valve stem 22.

  The ejector of the present embodiment includes a refrigerant passage 11 that introduces high-pressure refrigerant from the radiator 3 to the periphery of the valve rod 22, and the refrigerant passage 11 has an introduction direction of the high-pressure refrigerant with respect to the axis of the valve rod 22. It is provided to stagger. By adopting this configuration, the high-pressure refrigerant flowing into the upstream portion of the ejector can be swirled, and the swirling flow acts to align the valve rod 22, and the liquid refrigerant increases in flow velocity and boils. The nozzle efficiency and the ejector efficiency can be improved.

(Ninth embodiment)
In the ninth embodiment, another configuration of the valve stem and the valve stem support member will be described with reference to FIG. FIG. 17 is a partial cross-sectional view showing the configuration of the valve stem 46 and the valve stem support member 20 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The valve stem 46 and the valve stem support member 20 are mainly different from the first embodiment in that an elastic member 33 that elastically deforms between the valve stem 46 and the nozzle 23 is provided. This embodiment is the same as the first embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 17, the valve stem 46 is disposed so that the axial direction of the valve stem support member 20 coincides with that of the valve stem support member 20. The valve stem 46 includes a flange portion 47 closer to the nozzle 23 than the end portion 27. The flange portion 47 has a larger outer diameter than that of the large-diameter shaft portion. Between the lower surface of the flange portion 47 and the top surface portion of the nozzle 23, there is an elastic member 33 in a state of being elastically deformed with a dimension shorter than the natural length. Is provided.

  The elastic member 33 is elastically deformed in the axial direction between the flange portion 47 and the nozzle 23 in accordance with the axial displacement of the valve stem 46 and directly exerts an elastic force on the valve stem 46 in the axial direction.

  Since the ejector of the present embodiment includes the elastic member 33 that elastically deforms between the valve stem 46 and the nozzle 23, the elastic force of the elastic member 33 directly acts on both the valve stem 46 and the nozzle 23. Even if the valve rod 46 bites against the inner wall surface of the flow path of the nozzle 23, it is possible to suppress the occurrence of biting by an elastic force acting in a direction to eliminate this (vertically upward in FIG. 17).

(10th Embodiment)
In the tenth embodiment, another configuration of the ejector will be described with reference to FIG. FIG. 18 is a partial cross-sectional view showing the configuration around the valve stem 110 in the present embodiment. The vapor compression refrigeration cycle to which the ejector of the present embodiment is applied is the same as the cycle described in the first embodiment.

  The ejector according to the present embodiment is mainly different from the ninth embodiment in that it includes an isolation member 117 that separates the elastic member 119 that biases the valve rod 110 in the anti-nozzle direction from the refrigerant flow path. This embodiment is the same as the ninth embodiment in other configurations, and has the same functions and effects.

  As shown in FIG. 18, the valve stem 110 includes a head portion 111 that is displaceably housed in the housing portion 116 of the valve stem support member 114, a neck portion 112 that connects the head portion 111 and the large diameter portion, and a large diameter portion. And a flange portion 113 protruding outward in the radial direction near the neck portion 112. An elastic member 119 that urges the valve rod 110 in the anti-nozzle direction is disposed between the nozzle side end surface of the flange portion 113 and the nozzle side inner wall of the isolation member 117. Further, the axial distance between the nozzle side end surface 115 of the valve stem support member 114 and the flange portion 113 is set to such a dimension that the valve stem 110 can sufficiently move in the anti-nozzle direction by the elastic force of the elastic member 119. ing.

  In the first to seventh embodiments described above, when the arm portion or the like of the valve stem support member is damaged for some reason, the valve stem receives a force in the direction of closing the passage of the nozzle 23 due to the pressure difference of the refrigerant. . In the present embodiment, even if such a breakage occurs, an ejector capable of avoiding the valve closing state by the valve stem 110 is provided by providing the elastic member 119 having an elastic force larger than this by predicting this force. Can be provided.

  The isolation member 117 is a cylindrical body disposed so as to surround a part of the valve rod 110, the flange portion 113, and the elastic member 119, and is a member that resists the flow of the refrigerant from the radiator 3. Can be removed from the flow path. An annular gap is provided between the axial inner wall 118 located on the nozzle side of the separating member 117 and the valve stem 110. The valve stem 110 can be displaced in the radial direction by using the annular gap, and is supported so as to be swingable.

  The ejector according to the present embodiment includes the isolation member 117 that separates the elastic member 119 that urges the valve rod 110 in the anti-nozzle direction from the flow path through which the refrigerant flows, so that the valve rod 110 contacts the inner wall of the nozzle 23. The elastic member 119 that can prevent the valve stem 110 from biting against the nozzle 23 and does not affect the refrigerant flow is obtained.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  The ejector-type decompression device in the above-described embodiment can be applied to a vehicle air conditioner, a heat pump cycle for a water heater or an indoor air conditioner. The installation location may be a moving body such as a vehicle, or a fixed body placed at a fixed position.

  In the above embodiment, the type of refrigerant is carbon dioxide, but the refrigerant can be applied to any of vapor compression type supercritical cycle and subcritical cycle such as chlorofluorocarbon refrigerant, HC refrigerant, and carbon dioxide. .

  Further, the ejector in the above embodiment includes a valve stem having an axial direction arranged in a substantially vertical direction. However, the ejector is not limited to this. For example, the axial direction of the valve stem is arranged in a substantially horizontal direction. Or a configuration in which the axial direction of the valve stem is inclined.

It is the schematic diagram which showed an example of the vapor compression refrigeration cycle applicable to the ejector of all the embodiments. It is sectional drawing which showed the internal structure of the ejector of 1st Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 1st Embodiment. It is sectional drawing which showed the state which the valve stem contacted the nozzle in the ejector of 1st Embodiment. It is sectional drawing which showed the state which a valve rod contacts the inner wall of a nozzle and closes a nozzle channel | path in the ejector of 1st Embodiment. It is the fragmentary sectional view which showed the structure of the modification of the valve stem and valve stem support member in the ejector of 1st Embodiment. It is the conceptual diagram which showed the relationship between the pressure of the flow path of a nozzle, and a valve stem in the ejector of 1st Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 2nd Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 3rd Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 4th Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 5th Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 6th Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 7th Embodiment. It is the typical sectional view fractured | ruptured which showed the structure of the rotational flow formation means in the ejector of 8th Embodiment. It is typical sectional drawing which looked at the cut surface in FIG. 14 from the XV direction. It is explanatory drawing which showed the velocity vector of the swirl flow formed by the swirl flow formation means of 8th Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem and valve stem support member in the ejector of 9th Embodiment. It is the fragmentary sectional view which showed the structure of the valve stem periphery in the ejector of 10th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 2 ... Compressor 3 ... Radiator 7 ... Evaporator 11 ... Refrigerant passage 15 ... Magnet rotor (drive part)
18 ... Guide portion 20, 34, 43, 50, 60, 80 ... Valve rod support member 21, 33, 90, 119 ... Elastic member 22, 32, 40, 42, 46, 53, 66, 84, 110 ... Valve rod 23 ... Nozzle 24 ... Mixing unit (pressure unit)
26 ... Diffuser section (boost section)
27 ... End (coupling mechanism)
28 ... Arm (coupling mechanism)
38, 41 ... end 29, 55 ... storage part (coupling mechanism)
35 ... sphere 117 ... isolation member

Claims (14)

Vapor compression that has a radiator (3) that dissipates the high-pressure refrigerant compressed by the compressor (2) and an evaporator (7) that absorbs heat by evaporating the low-pressure refrigerant and moves the heat on the low temperature side to the high temperature side An ejector-type decompression device used in a refrigeration cycle,
A nozzle (23) for decompressing and expanding the high-pressure refrigerant;
A valve stem (22) for adjusting the passage opening of the nozzle (23) by being displaced in the axial direction;
A drive unit (15) for providing a driving force for axially displacing the valve stem (22);
A valve stem support member (20) that supports the valve stem (22) and is moved in the axial direction by the drive unit (15) to displace the valve stem (22) in the axial direction;
A pressure increasing section (24, 26) for increasing the pressure while mixing the refrigerant injected from the nozzle (23) and the refrigerant sucked from the evaporator (7);
The ejector-type decompression device, wherein the valve stem (22) is supported so as to be displaceable with respect to the valve stem support member (20).   The ejector-type decompression device according to claim 1, wherein the valve stem (22) is supported by the valve stem support member (20) so as to be movable in a radial direction.   The valve stem (22) is swingably attached to the valve stem support member (20) so that the valve stem (22) is aligned with the passage axial center of the nozzle (23) by the flow of the high-pressure refrigerant. The ejector-type decompression device according to claim 1 or 2, further comprising a coupling mechanism (27, 28, 29) for coupling. The drive unit includes a magnet rotor (15),
The valve stem support member (20) rotates with the rotation of the magnet rotor (15),
The valve stem support member (20) further includes a guide portion (18) for holding the valve stem support member (20) in a radial direction so that the valve stem support member (20) moves in an axial direction while rotating. 4. The ejector-type decompression device according to claim 1. The drive unit includes a magnet rotor (15),
The valve stem support member (20) moves to the nozzle side in the axial direction while rotating as the magnet rotor (15) rotates,
A passage closed by the valve stem (22) when the valve stem (22) displaced to the nozzle side in the axial direction by the valve stem support member (20) is in a position to close the passage of the nozzle (23). The inner diameter dimension (X) of the nozzle (23) in the part is larger than the radial dimension (Y) of the part where the valve stem support member (20) and the valve stem (22) are in contact with each other. The ejector-type decompression device according to any one of claims 1 to 4. The drive unit includes a magnet rotor (15),
The valve stem support member (34, 43, 60, 80) moves to the axial nozzle side while rotating with the rotation of the magnet rotor (15),
When the valve stem (32, 42, 66, 84) displaced to the nozzle side in the axial direction by the valve stem support member is in a position to close the passage of the nozzle (23), the valve stem is the magnet rotor. 5. The member (35, 43, 61, 88) rotated by the rotation of (15) is in contact with a point at the end on the side opposite to the nozzle, 5. Ejector type decompression device.   One of the valve stem support member (20, 50) and the valve stem (22, 53) is provided with a storage portion (29, 55) in which a part of the other is stored in a displaceable manner. The ejector-type decompression device according to any one of claims 1 to 6.   The ejector system according to any one of claims 1 to 7, wherein a portion of the valve stem (22) supported in contact with the valve stem support member (20) is formed in a curved surface. Pressure reducing device.   The sphere (35) separate from the valve stem (40) is provided between an end (41) of the valve stem (40) and the valve stem support member (20). The ejector-type decompression device according to claim 7.   2. An elastic member (21, 33, 90) that elastically deforms between the valve stem (22, 32, 84) and the valve stem support member (20, 34, 80). The ejector-type decompression device according to claim 8.   The ejector-type pressure reducing device according to any one of claims 1 to 10, further comprising an elastic member (33, 119) for urging the valve stem (46, 110) in a direction opposite to the nozzle.   The ejector-type decompression device according to claim 11, further comprising an isolation member (117) separating the elastic member (33, 119) from a flow path through which a refrigerant flows.   12. The ejector-type pressure reducing device according to claim 11, further comprising an elastic member (33) elastically deformed between the valve stem (46) and the nozzle (23). A refrigerant passage (11) for introducing the high-pressure refrigerant around the valve rod (22);
The said refrigerant path (11) is provided so that the introduction direction of the said high voltage | pressure refrigerant | coolant may be shifted with respect to the axial center of the said valve rod (22), The Claim 1 characterized by the above-mentioned. The ejector-type decompression device as described.

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