JP2006125751A - Electric control valve and refrigeration cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To perform valve operation as an opening and closing valve in two positions, that is, a completely closed position and a fully opened position, and function as an electromagnetic opening and closing valve in the two positions of the completely closed position and the fully opened position in addition to a proportional flow rate control valve for conducting quantitative flow rate control in an electric control valve. <P>SOLUTION: A flow rate control valve element 17 exceeds a valve lift position (fully opened position) setting a maximum flow rate from a flow rate control region, and is moved to a valve lift direction, and thereby a ball valve 42 is seated in a valve seat 29, and the completely closed state is achieved. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an electric control valve and a refrigeration cycle apparatus, and more particularly to an electric control valve and a refrigeration cycle apparatus used as an expansion valve of the refrigeration cycle apparatus.

  As an electric control valve used as an expansion valve of a refrigeration cycle device, etc., it includes a feed screw mechanism by screw engagement between a male screw member and a female screw member. The feed screw mechanism is rotationally driven by an electric motor, and is rotated by the feed screw mechanism. There is known an electric control valve that converts the flow into a linear motion in the valve lift direction and moves the valve body in the valve lift direction by the linear motion to control the flow rate (for example, Patent Documents 1, 2, and 3).

  The expansion valve of the refrigeration cycle device is a throttle valve that depressurizes the refrigerant by adiabatic expansion, so the electric control valve used as the expansion valve is designed not to take a fully closed state that completely shuts off the refrigerant flow rate. Even if there is a fully closed position that takes a fully closed state, it is set on the valve lift position side that sets the minimum flow rate.

  For this reason, even though the conventional electric control valve can perform proportional flow control, special control is required when the fully closed state and fully open state are turned on and off. In addition, it is not easy to perform self-cleaning in which the valve body is positioned at the fully open position and foreign matters in the valve portion are removed by a large flow rate.

  In addition, for example, some indoor units are operated in a multi-type air conditioner or a refrigeration / refrigeration showcase in which multiple indoor units are connected in parallel to one common outdoor unit. In order to stop the operation, it is necessary to connect an electromagnetic on-off valve in series to the high pressure side of the expansion valve in order to completely stop the refrigerant flow in the indoor unit.

  This electromagnetic on-off valve is of course required when the expansion valve is a mechanical type, but is used when an electric control valve that includes the fully closed position to the fully open position within the variable range of the valve lift is used as the expansion valve. However, since the electric control valve does not have the same valve closing capability as an electromagnetic on-off valve, in the refrigeration and refrigeration showcases where the operation of some indoor units may be suspended, the expansion valve of the electric control valve It is necessary to provide an electromagnetic on-off valve on the high pressure side.

However, if a new electromagnetic on-off valve is installed on the high-pressure side of the expansion valve, it will require installation space for the electromagnetic on-off valve and power for operation, so it goes against the recent trends in space-saving and energy-saving. In addition, the opening / closing operation of the electromagnetic opening / closing valve may cause a water hammer phenomenon in the expansion valve on the downstream side thereof, which may cause noise and failure.
Japanese Patent No. 2615021 JP 2001-271156 A Japanese Patent Laid-Open No. 2003-148643

  The problem to be solved by the present invention is that in an electric control valve that performs quantitative flow rate control, in addition to proportional flow rate control, two-way valve operation of a fully closed position and a fully open position can be performed. It is to diversify the valve operation.

  The electric control valve according to the present invention includes a feed screw mechanism by screw engagement between a male screw member and a female screw member, and the feed screw mechanism is rotationally driven by an electric motor, and the rotary motion is linearly moved in the valve lift direction by the feed screw mechanism. In the electric control valve that converts the motion into the valve lift direction by the linear motion, the valve lift position that sets the minimum flow rate and the valve that sets the maximum flow rate by the movement of the valve body in the valve lift direction A lift position is set, and a flow rate control area for quantitative flow control is set between both valve lift positions, and the valve body exceeds the valve lift position for setting the maximum flow rate from the flow rate control area. A fully closed position is set in which a fully closed state is achieved by moving in the opening direction.

  In the electric control valve according to the present invention, preferably, the valve body performs quantitative flow control by increasing or decreasing the effective opening area of the valve port formed in the valve housing by movement in the valve lift direction. And a fully closed portion for closing the valve port by sitting on a fully closed valve seat defined around the valve port.

  An electric control valve according to the present invention includes an electric motor, a feed screw mechanism that is rotationally driven by the electric motor and converts rotational motion into linear motion, a valve housing having a valve port, and the feed screw mechanism. It is driven in the valve lift direction by linear motion, and quantitative flow control is performed between the valve lift position for setting the minimum flow rate and the valve lift position for setting the maximum flow rate by increasing or decreasing the effective opening area of the valve port. A flow control valve body, and an open / close valve body that closes the valve port by sitting on a fully-closed valve seat portion defined around the valve port, and the open / close valve body includes the flow control valve In a state where the body is in a flow control range between the valve lift position for setting the minimum flow rate and the valve lift position for setting the maximum flow rate, the position separated from the valve seat by the flow control valve body The valve seat portion is prevented from being seated on the valve seat portion and is moved in the valve opening direction beyond the valve lift position where the flow rate control valve body sets a maximum flow rate from the flow rate control region. Ready to sit on.

  In the electric control valve according to the present invention, the flow control valve body further moves around the valve port by moving in a valve lift direction beyond the valve lift position that sets a minimum flow rate from the flow control region. A fully closed state is established by sitting on the other fully closed valve seat portion defined.

  The electric control valve according to the present invention defines an electric motor, a feed screw mechanism that is rotationally driven by the electric motor and converts rotational motion into linear motion, a flow control valve port, and a fully-closed valve seat portion. A valve housing having a fully closed valve port that is connected in series, and driven in the valve lift direction by the linear motion of the feed screw mechanism, and by increasing or decreasing the effective opening area of the flow control valve port, the minimum flow rate A flow control valve body that performs quantitative flow control between a valve lift position that sets a maximum flow rate and a valve lift position that sets a maximum flow rate, and a seat on the valve seat portion defined by the valve port for full closure The on-off valve body closes the valve port for full closure by the valve lift position at which the flow control valve body sets the minimum flow rate and the valve lift position at which the maximum flow rate is set. In a state where the flow rate is in the flow control range between the valve seat and the valve seat is prohibited from being seated on the fully closed valve seat by the flow control valve, and the flow control valve is By moving in the valve opening direction beyond the valve lift position where the maximum flow rate is set from the flow rate control region, the valve seat portion can be seated.

  In the electric control valve according to the present invention, preferably, the on-off valve body exerts a differential pressure across the valve port in a direction in which the valve seat is seated on the valve seat portion.

  The electric control valve according to the present invention preferably further includes a spring for biasing the on-off valve body in a valve closing direction seated on the valve seat portion.

  The refrigeration cycle apparatus according to the present invention is a multi-type refrigeration cycle apparatus in which a plurality of indoor units are connected in parallel to one common outdoor unit, and the electric control valve according to the above-described invention is used as an expansion valve. In the refrigerant circuit.

  The electric control valve according to the present invention is fully closed when the valve body moves in the valve opening direction beyond the valve lift position (fully opened position) that sets the maximum flow rate from the flow rate control region. As a result, the electric control valve according to the present invention performs not only a proportional flow rate control valve that performs quantitative flow rate control, but also an on-off valve operation of two positions, a fully closed position and a fully open position, And also functions as a two-position electromagnetic on-off valve in the fully open position.

  One embodiment of an electric control valve according to the present invention will be described with reference to FIG.

  The electric control valve according to this embodiment has a cup-shaped valve housing 10. The valve housing 10 includes a valve chamber 11, a valve port 12 formed in the lower bottom of the valve chamber 11, a first input / output port 14 connected to the lower joint 13 and communicating with the valve chamber 11 via the valve port 12. And a second inlet / outlet port 16 connected to the horizontal joint 15 and directly communicating with the valve chamber 11.

  A flow control valve element 17 is disposed in the valve chamber 11. The flow rate control valve body 17 has a flow rate metering portion (needle valve portion) 18 having a truncated cone shape with a small diameter on the lower side. A cylindrical valve support cylinder 19 is fixedly connected to the flow control valve body 17 by an upper flange portion 17A.

  A fixed support member (female screw member) 21 is fixed to the upper portion of the valve housing 10 by a mounting plate 20. The valve support cylinder 19 is fitted in a guide hole 22 formed in the fixed support member 21 so as to be slidable in the axial direction (vertical direction), that is, in the valve lift direction, and the flow control valve body 17 is fitted to the valve housing 10 side. It plays the role of supporting the movably in the valve lift direction from the fixed support member 21.

  With this support structure, the flow rate control valve body 17 moves in the valve lift direction so that the flow rate metering unit 18 enters the valve port 12 so that it can enter and exit, so that the effective opening area of the valve port 12 is increased by movement in the valve lift direction. The flow rate is quantitatively controlled between the valve lift position (lowering position) that sets the minimum flow rate and the valve lift position (upward position) that sets the maximum flow rate.

  The illustrated valve lift position is a valve lift position for setting a minimum flow rate (minimum flow rate setting position), and the large diameter portion 18A of the flow rate measuring portion 18 enters the valve port 12, and the outer peripheral surface of the large diameter portion 18A. The minimum flow rate is set by the gap between the valve port 12 and the inner peripheral surface of the valve port 12.

  From this minimum flow rate setting position, the flow rate control valve body 17 moves upward in the valve lift direction, the large diameter portion 18A of the flow rate measuring portion 18 comes out of the valve port 12, and only the small diameter portion 18B of the flow rate measuring portion 18 is inside the valve port 12. The maximum flow rate is set by the gap between the outer peripheral surface of the small-diameter portion 18B and the inner peripheral surface of the valve port 12 at the valve lift position located at. This valve lift position is a valve lift position (maximum flow rate setting position) at which the maximum flow rate (fully open flow rate) is set.

  The valve support cylinder 19 is disposed in the lower flange portion 23A of the male screw shaft 23 within the upper annular lip 19A of the valve support cylinder 19 and the valve support cylinder 19 and is urged by the compression coil spring 25. The pressing member 26 is sandwiched in the thrust direction (valve lift direction) via the high-sliding washer 24, is connected to the male screw shaft 23 so as to be relatively rotatable, and moves together with the male screw shaft 23 in the valve lift direction.

  The male screw shaft 23 has a male screw part 27, and the male screw part 27 is engaged with a female screw part 28 formed on the fixed support member 21. By this screw engagement, the male screw shaft 23 moves in the axial direction, that is, in the valve lift direction with rotation.

  The feed screw mechanism is configured by the screw engagement between the male screw portion 27 and the female screw portion 28, and the feed screw mechanism converts the rotational motion of the male screw shaft 23 into linear motion in the valve lift direction of the member.

  A can-shaped rotor case 31 of a stepping motor 30 is airtightly fixed to the upper portion of the valve housing 10 by welding or the like. In the rotor case 31, a rotor 32 having a multi-pole magnetized outer peripheral surface portion 32A is rotatably provided. An upper end 23B of the male screw shaft 23 is fixedly connected to the rotor 32.

  A stator coil unit 33 is inserted and attached to the outside of the sealed rotor case 31. Although not shown in detail, the stator coil unit 33 has a well-known airtight mold structure having a magnetic pole tooth, a winding part, and an electric wiring part therein for a stepping motor.

  In the rotor case 31, a guide support shaft 34 that is suspended and fixed from the ceiling portion of the rotor case 31, a spiral guide wire 35 that is attached to the outer periphery of the guide support shaft 34, and an upper end portion of the guide support shaft 34 are formed. There are a fixed stopper portion 36, a movable stopper member 37 screwed into the spiral guide wire 35, and a protrusion 38 of the rotor 32 that engages and kicks the movable stopper member 37, thereby opening or closing the valve. The stopper is configured.

  The stepping motor 30 rotationally drives the male screw shaft 23 by the rotor 32, and moves the flow control valve body 17 together with the valve support cylinder 19 in the valve lift direction by the axial movement of the male screw shaft 23 accompanying the rotation.

  A valve holder 41 is fixedly attached to the lower joint 13 outside the valve port 12. A ball valve 42 serving as an on-off valve body is provided in the valve holder 41. The ball valve 42 closes the valve port 12 by sitting on a fully-closed valve seat 29 defined around the lower joint 13 side of the valve port 12.

  A compression coil spring 43 is provided between the spring receiving portion 41 </ b> B around the lower communication hole 41 </ b> A of the valve holder 41 and the ball valve 42. The compression coil spring 43 urges the ball valve 42 in the valve closing direction in which the compression coil spring 43 is seated on the valve seat portion 29.

  The ball valve 42 is in contact with the tip 17B of the flow control valve body 17 and is in a flow control region between the valve lift position where the flow control valve body 17 sets the minimum flow rate and the valve lift position where the maximum flow rate is set. In the state, as shown in the figure, the flow control valve body 17 is pushed down against the spring force of the compression coil spring 43 and is held at a position away from the valve seat portion 29 and is seated on the valve seat portion 29. Is prohibited and the valve is kept open.

  On the other hand, the ball valve 42 is seated on the valve seat 29 by moving (upward movement) in the valve opening direction beyond the valve lift position where the flow rate control valve body 17 sets the maximum flow rate from the flow rate control region. In this state, the valve is seated on the valve seat 29 by the spring force of the compression coil spring 43, and the valve is closed, that is, the valve port 12 is fully closed.

  The flow control characteristic of the electric control valve according to this embodiment is as shown in FIG. In the flow rate control characteristics shown in FIG. 2, the minimum flow rate range is set within a predetermined pulse number range on the 0 pulse side of the stepping motor 30 depending on the shape of the flow control valve body 17, and the stepping motor 30 responds to an increase in the pulse number. As the flow control valve element 17 moves upward, the flow rate increases proportionally, and reaches a fully open flow rate (maximum flow rate) with a certain number of pulses. Between the valve lift position (lowering position) for setting the minimum flow rate and the valve lift position (upward position) for setting the maximum flow rate is a flow rate control region in which quantitative flow rate control is performed. The fully open flow rate (maximum flow rate) state is also maintained over a predetermined pulse number range depending on the shape of the flow control valve element 17. This is a fully open area.

  The pulse number of the stepping motor 30 increases beyond this fully open region, and the ball valve 42 is seated on the valve seat portion 29 by the spring force of the compression coil spring 43 at the maximum pulse, and the valve port 12 is shielded. .

  In this fully closed state, the tip 17B of the flow control valve body 17 may be separated from the ball valve 42 by upward movement, and the ball valve 42 is seated on the valve seat 29 by the spring force of the compression coil spring 43. The valve port 12 is shielded like a check valve. Therefore, in the fully closed state, the valve closing thrust force does not act on the screw engagement between the male screw portion 27 and the female screw portion 28, and a large load does not act on the screw engaging portion. This contributes to reducing wear of the screw engaging portion and preventing biting (locking).

  When fluid flows from the lower joint 13 to the horizontal joint 15, the differential pressure across the valve port 12 acts in the direction of seating on the valve seat 29 with respect to the ball valve 42, and the ball valve 42 is also affected by this differential pressure. A fully closed state in which the valve seat 29 is seated is obtained. In this case, the compression coil spring 43 can be omitted.

  As described above, according to the electric control valve according to this embodiment, the flow rate control valve element 17 is driven by the stepping motor 30 so that the valve opening direction exceeds the valve lift position (full open range) where the maximum flow rate is set from the flow rate control range. Since the ball valve 42 is seated on the valve seat 29 and moved to the fully closed state by moving to (up), in addition to functioning as a proportional flow rate control valve that performs quantitative flow rate control, the ball valve 42 is fully opened. On the other hand, it also performs an on-off valve operation that takes two positions, the fully open position and the fully closed position, and also functions as an electromagnetic open / close valve in two positions, the fully closed position and the fully open position.

  In addition, the rotation of the rotor 32 by the stepping motor 30 is converted into linear movement by the feed screw mechanism of the male screw shaft 23 and the fixed support member 21, and the flow control valve element 17 is moved between the fully open position and the fully closed position. The operation of the electric control valve according to this embodiment is slower than that of the electromagnetic valve that moves the valve element between the fully open position and the fully closed position by linear movement of the plunger by the electromagnetic solenoid. The valve works like a slow-acting electromagnetic on-off valve.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  The complete shielding of the valve port 12 is advantageous in that the on-off valve body is a ball valve 42, but the on-off valve body is a plate-like flat valve instead of the ball valve 42 as shown in FIG. It is also possible to configure with 44.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. 4, parts corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1, and description thereof is omitted.

  The electric control valve according to this embodiment has a valve housing 50. The valve housing 50 includes a valve chamber 51, a valve port 52 formed in the upper portion of the valve chamber 51, a first input / output port 54 connected to the lower horizontal joint 53 and directly communicating with the valve chamber 51, and an upper horizontal joint. And a second inlet / outlet port 56 communicating with the valve chamber 51 via the valve port 52.

  The flow control valve body 17 is fitted in a guide hole 57 formed in the valve housing 50 so as to be slidable in the axial direction (vertical direction), that is, in the valve lift direction, and supported so as to be movable in the valve lift direction from the valve housing 10. Has been.

  The flow control valve body 17 abuts on the tip 23C of the male screw shaft 23 at the upper end 17C, and is directly driven in the axial direction (valve lift direction) by the axial movement of the male screw shaft 23.

  A female screw member 58 is fixedly mounted on the upper portion of the valve housing 10, and the male screw portion 27 of the male screw shaft 23 is screw-engaged with the female screw portion 28 formed on the female screw member 58 to constitute a feed screw mechanism. This feed screw mechanism also converts the rotational motion of the male screw shaft 23 into linear motion in the valve lift direction of the member.

  Also in this embodiment, the flow rate control valve body 17 moves in the valve lift direction so that the flow rate measuring unit 18 enters the valve port 52 so as to be able to enter and exit. The effective opening area of the port 52 is increased or decreased, and quantitative flow rate control is performed between the valve lift position (lowering position) for setting the minimum flow rate and the valve lift position (upward position) for setting the maximum flow rate.

  A ball valve 42 serving as an on-off valve body is provided in the valve chamber 51. The ball valve 42 is held by a slide guide holder 63 that is in sliding contact with the inner peripheral surface of the valve chamber 51 and guided in the opening / closing direction (vertical direction) in the valve chamber 51, and is defined around the valve chamber 51 side of the valve port 52. The valve port 52 is closed by seating on the fully closed valve seat 59.

  A compression coil spring 43 is provided between a ball retainer-shaped spring retainer 60 engaged with the ball valve 42 and a spring retainer 61 fixed to the valve housing 50. The compression coil spring 43 is the same as that described above. Similarly to the embodiment, the ball valve 42 is biased in the valve closing direction in which the ball valve 42 is seated on the valve seat portion 59.

  Also in this embodiment, the ball valve 42 is in contact with the tip 17B of the flow control valve body 17, and the flow control valve body 17 is between the valve lift position where the minimum flow rate is set and the valve lift position where the maximum flow rate is set. In the state in the flow rate control region, as shown in the figure, the flow rate control valve body 17 is pushed down against the spring force of the compression coil spring 43 and held at a position away from the valve seat portion 59. It is prohibited to sit on 59 and keep the valve open.

  On the other hand, the ball valve 42 is seated on the valve seat 59 by moving (upward movement) in the valve opening direction beyond the valve lift position where the flow rate control valve body 17 sets the maximum flow rate from the flow rate control region. In this state, the valve is seated on the valve seat 59 by the spring force of the compression coil spring 43, and the valve is closed, that is, the valve port 52 is fully closed.

  Also in this embodiment, in the fully closed state, the distal end portion 17B of the flow control valve element 17 may be separated from the ball valve 42 by the upward movement, and the ball valve 42 is separated from the valve seat portion 59 by the spring force of the compression coil spring 43. The valve port 52 is shielded in a check valve manner. Therefore, in the fully closed state, the valve closing thrust force does not act on the screw engagement between the male screw portion 27 and the female screw portion 28, and a large load does not act on the screw engaging portion. This contributes to reducing wear of the screw engaging portion and preventing biting (locking).

  Even in the electric control valve according to this embodiment, the flow control valve element 17 moves in the valve opening direction (upward movement) beyond the valve lift position (full open range) where the maximum flow rate is set from the flow rate control region by driving by the stepping motor 30. As a result, the ball valve 42 is seated on the valve seat portion 59 and is fully closed, so that in addition to functioning as a proportional flow control valve that performs quantitative flow control, on the fully open side, It also operates as an open / close valve that takes two positions of the fully closed position, and functions as a two-position electromagnetic open / close valve that is a fully closed position and a fully open position.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. 5, parts corresponding to those in FIGS. 1 and 4 are denoted by the same reference numerals as those in FIGS. 1 and 4, and description thereof is omitted.

  In this embodiment, both shaft ends 23D and 23E of the male screw shaft 23 integral with the rotor 32 of the stepping motor 30 are axially moved by the bearing member 62 attached to the valve housing 50 and the bearing member 39 attached to the rotor case 31. In a state where movement is constrained, it is rotatably supported. A female screw portion 28 of a female screw member 58 is engaged with the male screw portion 27 of the male screw shaft 23.

  An upper end portion 64 </ b> A of a drive rod 64 that is movably fitted in an axial direction (valve lift direction) is fixedly connected to a through hole 69 formed in the valve housing 50. As a result, the female screw member 58 can move in the axial direction (valve lift direction) and is prevented from rotating. Although only one drive rod 64 is shown in the figure, three drive rods 64 are actually provided at a rotation angle pitch of 120 degrees. Incidentally, the number of drive rods 64 and the rotation angle pitch may be other than three and 120 degrees depending on the design.

  The drive rod 64 contacts the slide guide holder 63 at the lower end portion 64B, and transmits the movement of the female screw member 58 in the valve lift direction to the slide guide holder 63 and the ball valve.

  As a result, the movement of the female screw member 58 in the valve lift direction is transmitted to the flow control valve body 17 via the drive rod 64, the slide guide holder 63, and the ball valve.

  Also in this embodiment, the ball valve 42 is shown in a state where the flow control valve element 17 is in a flow rate control region between a valve lift position that sets a minimum flow rate and a valve lift position that sets a maximum flow rate. In addition, it is pushed down against the spring force of the compression coil spring 43 and is held at a position away from the valve seat portion 59, so that it is prohibited from being seated on the valve seat portion 59, the valve open state is maintained, and the flow control valve body When 17 moves beyond the valve lift position that sets the maximum flow rate from the flow rate control region and moves in the valve opening direction (upward movement), it is seated on the valve seat portion 59 by the spring force of the compression coil spring 43, and the valve is closed, that is, The valve port 52 is fully closed.

  Also in this embodiment, in the fully closed state, the distal end portion 17B of the flow control valve element 17 may be separated from the ball valve 42 by the upward movement, and the ball valve 42 is separated from the valve seat portion 59 by the spring force of the compression coil spring 43. The valve port 52 is shielded in a check valve manner. Therefore, in the fully closed state, the valve closing thrust force does not act on the screw engagement between the male screw portion 27 and the female screw portion 28, and a large load does not act on the screw engaging portion. This contributes to reducing wear of the screw engaging portion and preventing biting (locking).

  Even in the electric control valve according to this embodiment, the flow control valve element 17 moves in the valve opening direction (upward movement) beyond the valve lift position (full open range) where the maximum flow rate is set from the flow rate control region by driving by the stepping motor 30. As a result, the ball valve 42 is seated on the valve seat portion 59 and is fully closed, so that in addition to functioning as a proportional flow control valve that performs quantitative flow control, on the fully open side, It also operates as an open / close valve that takes two positions of the fully closed position, and functions as a two-position electromagnetic open / close valve that is a fully closed position and a fully open position.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIGS. In FIGS. 6 and 7, parts corresponding to those in FIGS. 1 and 4 are denoted by the same reference numerals as those in FIGS. 1 and 4, and description thereof is omitted.

  As shown in FIG. 6, in this embodiment, the flow control valve body 17 and the male screw shaft 23 are configured as an integral part. A spline joint member 65 having a spline shaft portion 65A is fixedly connected to the upper end portion 23B of the male screw shaft 23.

  A hub member 66 is fixedly attached to the rotor 32 of the stepping motor 30. The hub member 66 is rotatably supported by the guide support shaft 34 in a suspended manner.

  As shown in FIG. 7, a spline hole 67 is formed in the hub member 66, and the spline shaft portion 65A of the spline joint member 65 is slidably engaged with the spline hole 67 in the axial direction. Yes. As shown in FIG. 6, a conical coil spring 68 is attached between the hub member 66 and the spline joint member 65. The conical coil spring 68 is provided to attenuate the damping of the rotor 32, but may be omitted depending on the damping state of the rotor 32.

  In this structure, the rotation of the rotor 32 of the stepping motor 30 is transmitted to the male screw shaft 23 via the spline engaging portion between the spline hole 67 of the hub member 66 and the spline shaft-like portion 65A of the spline joint member 65, and the male screw shaft. 23 is rotationally driven.

  As shown in FIG. 7, a clearance C in the rotor rotation direction is provided at a spline engaging portion between the spline hole 67 of the hub member 66 and the spline shaft-like portion 65A of the spline joint member 65.

  As a result, even if the rotor 32 vibrates in the rotational direction during the transition of the excitation phase of the stepping motor 30, that is, even if the rotor 32 repeats reciprocating rotation by a small angle, only the rotor 32 rotates within the clearance C range. (Idling), and the reciprocating rotation (damping) by the small angle of the rotor 32 is not transmitted to the male screw shaft 23.

  As a result, regardless of the type, size, weight, and phase excitation speed of the multipolar magnetization of the rotor 32, noise is generated using the sliding sound of the screw engaging portion between the male screw portion 27 and the female screw portion 28 as a sound source. (Operation noise) is reduced.

  As shown in FIG. 8, the clearance C is set by sliding key engagement between the key portion 92 of the one-character member 91 attached to the male screw shaft 23 and the key groove 93 formed in the hub member 66. It can be set similarly.

  In this embodiment, when a fluid flows from the lower joint 13 to the horizontal joint 15, the differential pressure across the valve port 12 acts in the direction in which the ball valve 42 is seated on the valve seat portion 29, so that the ball valve 42 In the state where the flow control valve element 17 is in contact with the tip 17B of the flow control valve element 17 and is in the flow control region between the valve lift position where the minimum flow rate is set and the valve lift position where the maximum flow rate is set. As shown in the figure, it is pushed down by the flow control valve body 17 and held at a position away from the valve seat portion 29, so that it is prohibited from sitting on the valve seat portion 29, and the valve is kept open.

  On the other hand, the ball valve 42 is seated on the valve seat 29 by moving (upward movement) in the valve opening direction beyond the valve lift position where the flow rate control valve body 17 sets the maximum flow rate from the flow rate control region. In this state, the valve seat 12 is seated by the differential pressure across the valve port 12 acting on the ball valve 42, and the valve is closed, that is, the valve port 12 is fully closed.

  In this embodiment, in the fully closed state, the distal end portion 17B of the flow control valve element 17 may be separated from the ball valve 42 by upward movement, and the ball valve 42 is separated from the valve seat 29 by the differential pressure across the valve port 12. The valve port 12 is shielded in a check valve manner. Therefore, in the fully closed state, the valve closing thrust force does not act on the screw engagement between the male screw portion 27 and the female screw portion 28, and a large load does not act on the screw engaging portion. This contributes to reducing wear of the screw engaging portion and preventing biting (locking).

  Even in the electric control valve according to this embodiment, the flow control valve element 17 moves in the valve opening direction (upward movement) beyond the valve lift position (full open range) where the maximum flow rate is set from the flow rate control region by driving by the stepping motor 30. As a result, the ball valve 42 is seated on the valve seat 29 and is fully closed, so that in addition to functioning as a proportional flow control valve that performs quantitative flow control, on the fully open side, It also operates as an open / close valve that takes two positions of the fully closed position, and functions as a two-position electromagnetic open / close valve that is a fully closed position and a fully open position.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  In this embodiment, the periphery of the valve seat portion 29 has a tapered hole shape for receiving the ball valve 42, but the periphery of the valve seat portion 29 may be a flat shape as shown in FIG. Good. Further, the position of the valve seat portion 29 in FIG. 6 may be set not on the periphery of the valve port 12 but on the flat shape portion 29a around it and further on the tapered surface portion 29b around it.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. 10, parts corresponding to those in FIGS. 1 and 6 are denoted by the same reference numerals as those in FIGS. 1 and 6, and description thereof is omitted.

  In this embodiment, a planetary gear reduction device 70 is incorporated between the stepping motor 30 and the male screw shaft 23. The planetary gear reduction device 70 is supported by a ring gear 71 having a fixed arrangement, a sun gear 72 fixed to a rotor shaft 94 integrally formed with the rotor 32, and a shaft 73 so as to be rotatable from a carrier 73. And planetary pinion 75 that meshes with 72.

  A spline hole 67 is formed in the carrier 73, and a spline shaft portion 65 </ b> A of the spline joint member 65 is engaged with the spline hole 67 so as to be slidable in the axial direction.

  In this embodiment, the rotation of the stepping motor 30 is decelerated by the planetary gear type reduction device 70 and transmitted to the male screw shaft 23.

  Further, the planetary gear type speed reduction device 70 incorporates a stopper mechanism that is fully closed or fully opened by a fixed stopper member 77 and a movable stopper portion 78 formed on the planetary pinion 75.

  If a detailed description of the stopper mechanism is necessary, refer to the specification and drawings of Japanese Patent Application No. 2004-269280 filed by the same applicant as the present applicant.

  Moreover, in this embodiment, the block-shaped on-off valve body 81 is provided. The on-off valve body 81 is guided by guide vanes 82 projecting in the radial direction from the outer peripheral surface thereof and slidably contacting the inner peripheral surface of the lower joint 13, moves in the lower joint 13 in the valve lift direction, and the valve seat portion Sitting on 29 closes valve port 12.

  In this embodiment, when a fluid flows from the lower joint 13 to the horizontal joint 15, the differential pressure across the valve port 12 acts in a direction in which the valve seat 81 is seated on the valve seat portion 29, thereby opening and closing the valve body. 81 is in contact with the tip 17B of the flow control valve body 17, and the flow control valve body 17 is in a flow control region between the valve lift position for setting the minimum flow rate and the valve lift position for setting the maximum flow rate. As shown in the drawing, it is pushed down by the flow control valve body 17 and is held at a position away from the valve seat portion 29, so that it is prohibited from being seated on the valve seat portion 29, and the valve is kept open.

  On the other hand, the on-off valve body 81 is seated on the valve seat portion 29 by moving (upward movement) in the valve opening direction beyond the valve lift position where the flow rate control valve body 17 sets the maximum flow rate from the flow rate control region. Then, the valve seat 12 is seated by the differential pressure across the valve port 12 acting on the on-off valve body 81, and the valve is closed, that is, the valve port 12 is fully closed.

  In this embodiment, in the fully closed state, the distal end portion 17B of the flow control valve body 17 may be separated from the on-off valve body 81 by upward movement, and the on-off valve body 81 is separated from the valve seat by the differential pressure across the valve port 12. It seats on the part 29 and shields the valve port 12 like a check valve. Therefore, in the fully closed state, the valve closing thrust force does not act on the screw engagement between the male screw portion 27 and the female screw portion 28, and a large load does not act on the screw engaging portion. This contributes to reducing wear of the screw engaging portion and preventing biting (locking).

  Even in the electric control valve according to this embodiment, the flow control valve element 17 moves in the valve opening direction (upward movement) beyond the valve lift position (full open range) where the maximum flow rate is set from the flow rate control region by driving by the stepping motor 30. As a result, the on-off valve body 81 is seated on the valve seat portion 29 and is fully closed, so that in addition to functioning as a proportional flow rate control valve that performs quantitative flow rate control, on the fully open side, The valve operates as an on-off valve that takes two positions, the fully closed position, and also functions as an electromagnetic on-off valve in two positions, a fully closed position and a fully open position.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. 11, parts corresponding to those in FIGS. 1 and 10 are denoted by the same reference numerals as those in FIGS. 1 and 10, and description thereof is omitted.

  In this embodiment, a fully-closed valve port member 83 that defines a fully-closed valve seat portion 84 is fixedly mounted in the lower joint 13 in a series relationship with the valve port 12 that is a flow control valve port.

  The on-off valve body 81 is between the valve port 12 and the fully-closing valve seat portion 84 and is engaged with the distal neck portion 17 </ b> D of the flow control valve body 17. Contrary to the embodiment shown in FIG. 1 and the like, the flow rate measuring portion (needle valve portion) 18 of the flow control valve body 17 has a truncated conical shape with a small diameter on the upper side.

  In a state where the flow control valve body 17 is in a flow control region between the valve lift position for setting the minimum flow rate and the valve lift position for setting the maximum flow rate, the on-off valve body 81 is configured to perform flow control as shown in the figure. It is lifted by the valve body 17 and is held at a position away from the fully-closed valve seat portion 84, and is prevented from being seated on the fully-closed valve seat portion 84, and the valve is kept open.

  On the other hand, the on-off valve body 81 moves in the valve opening direction (downward movement) beyond the valve lift position where the flow rate control valve body 17 sets the maximum flow rate from the flow rate control region, and thereby the fully closed valve seat portion. The fully-closed valve seat can be seated on the open / close valve body 81 by the differential pressure across the fully-closed valve port member 83 acting on the on-off valve body 81 (the differential pressure when fluid flows from the horizontal joint 15 to the lower joint 13). It sits on the portion 84 and enters a valve closed state, that is, a fully closed state that shields the valve port member 83 for full closure.

  Therefore, even in the electric control valve according to this embodiment, the flow control valve element 17 is moved in the valve opening direction (lowered) beyond the valve lift position (full open region) where the maximum flow rate is set from the flow control region by driving by the stepping motor 30. Movement), the on-off valve body 81 is seated on the fully-closed valve seat 84 and becomes fully closed, so that in addition to functioning as a proportional flow control valve that performs quantitative flow control, On the other hand, it also performs an on-off valve operation that takes two positions, the fully open position and the fully closed position, and also functions as an electromagnetic open / close valve in two positions, the fully closed position and the fully open position.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. 12, parts corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1, and description thereof is omitted.

  In this embodiment, the flow rate control valve body 17 includes a flow rate measuring unit 18 that performs quantitative flow rate control by increasing or decreasing the effective opening area of the valve port 12 by movement in the valve lift direction, and the valve chamber 11 of the valve port 12. It has a packing member 85 as a fully closed portion for closing the valve port 12 by sitting on a fully closed valve seat 29 defined around the side.

  In a state where the flow rate metering portion 18 of the flow rate control valve body 17 is in the flow rate control region between the valve lift position where the minimum flow rate is set and the valve lift position where the maximum flow rate is set, the packing member 85 is from the valve seat portion 29. Keep the valve open at a distance.

  On the other hand, when the flow control valve element 17 moves in the valve lift direction (downward movement) beyond the valve lift position where the maximum flow rate is set from the flow control region, the packing member 85 is seated on the valve seat portion 29, and the valve port 12 is fully closed.

  Therefore, even in the electric control valve according to this embodiment, the flow control valve element 17 is moved in the valve opening direction (lowered) beyond the valve lift position (full open region) where the maximum flow rate is set from the flow control region by driving by the stepping motor 30. Since the packing member 85 is seated on the valve seat 29 and is fully closed by moving, the function as a proportional flow rate control valve that performs quantitative flow rate control, in addition to the fully open side, It also operates as an on-off valve that takes two positions, the position and the fully closed position, and functions as a two-position electromagnetic on-off valve that is a fully closed position and a fully open position.

  Also in this embodiment, since the valve is fully opened immediately before it is fully closed, it is possible to easily perform self-cleaning control that removes foreign matter from the valve portion by a large flow rate.

  Another embodiment of the electric control valve according to the present invention will be described with reference to FIG. In FIG. 13, parts corresponding to those in FIG. 1 are denoted by the same reference numerals as those in FIG. 1, and description thereof is omitted.

  In this embodiment, the large-diameter portion 18A of the flow rate measuring portion 18 of the flow control valve element 17 is seated on another fully-closed valve seat portion 86 formed in the valve port 12 in the lowest lowered position. ing.

  Thus, in this embodiment, the large diameter of the flow metering portion 18 of the flow control valve body 17 can also be obtained by moving in the valve closing direction (lowering movement) beyond the valve lift position that sets the minimum flow rate from the flow control region. When the portion 18A is seated on the valve seat portion 86, the valve seat portion 86 is fully closed. The control characteristics in this case are as shown in FIG.

  Next, one embodiment of the refrigeration cycle apparatus according to the present invention will be described with reference to FIG.

  The refrigeration cycle apparatus according to this embodiment is of a multi-type system, and includes one common outdoor unit 100 and a plurality of indoor units 110 connected in parallel to the common outdoor unit 100.

  The common outdoor unit 100 is provided with a compressor 101, a four-way valve 102, an outdoor heat exchanger 103, and an outdoor unit expansion valve 104.

  The indoor unit 110 is provided with an indoor heat exchanger 111 and an indoor unit expansion valve 112 for each indoor heat exchanger 111.

  This refrigeration cycle apparatus is used in an air conditioner, a refrigeration / refrigerator or the like. When used in an air conditioner, the solid arrow indicates the refrigerant flow during cooling, and the broken arrow indicates the refrigerant flow during heating.

  As the outdoor unit expansion valve 104 and the indoor unit expansion valve 112, the above-described electric control valve according to the present invention is used.

  In the multi-type system, for the indoor unit 110 that is thermo-off (operation stop) during cooling operation, the fan is stopped by thermo-off (operation stop) by fully closing the indoor unit expansion valve 112 of the indoor unit 110. The refrigerant is completely prohibited from flowing through the indoor unit 110.

  Thereby, the refrigerant leaks and flows through the indoor unit 110 with the fan stopped, so that the indoor heat exchanger 111 and the piping are not supercooled, and condensation and freezing of condensed water are avoided. Furthermore, the valve closing operation is slow, and is different from the rapid valve closing and valve opening operations such as an electromagnetic on-off valve, and is effective in preventing the occurrence of water hammer.

It is sectional drawing which shows one Embodiment of the electrically driven control valve by this invention. It is a graph which shows the control characteristic of the electric control valve by this embodiment. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing along line AA of FIG. FIG. 7 is a cross-sectional view showing another embodiment along line AA in FIG. 6. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is sectional drawing which shows other embodiment of the electrically driven control valve by this invention. It is a graph which shows the control characteristic of the electrically driven control valve by other embodiment. It is a refrigerant circuit figure showing one embodiment of the refrigerating cycle device by this invention.

Explanation of symbols

10, 50 Valve housing 11, 51 Valve chamber 12, 52 Valve port 13 Lower joint 14, 54 First inlet / outlet port 15 Horizontal joint 16, 56 Second inlet / outlet port 17 Flow control valve element (valve element)
18 Flow meter 19 Valve support cylinder 20 Mounting plate 21 Fixed support member (female screw member)
22, 57 Guide hole 23 Male screw shaft 24 High slip washer 25 Compression coil spring 26 Press member 27 Male screw portion 28 Female screw portion 29, 59 Valve seat portion 30 Stepping motor 31 Rotor case 32 Rotor 33 Stator coil unit 34 Guide support shaft 35 Spiral Guide wire body 36 Fixed stopper portion 37 Movable stopper member 38 Protruding portion 39, 62 Bearing member 41 Valve holder 42 Ball valve 43 Compression coil spring 44 Flat valve 53 Lower lateral joint 55 Upper lateral joint 58 Female thread member 60, 61 Spring retainer 63 Slide Guide holder 64 Drive rod 65 Spline joint member 66 Hub member 67 Spline hole 68 Conical coil spring 69 Through hole 70 Planetary gear type reduction gear 71 Ring gear 72 Sun gear 73 Carrier 74 Shaft 75 Planetary pinion 77 S Topper member 78 Stopper part 81 Open / close valve body 82 Guide vane 83 Fully closed valve port member 84 Fully closed valve seat part 85 Packing member 86 Valve seat part 91 Single letter member 92 Key part 93 Key groove 94 Rotor shaft 100 Common outdoor unit 101 Compressor 102 Four-way valve 103 Outdoor heat exchanger 104 Outdoor unit expansion valve 110 Indoor unit 111 Indoor heat exchanger 112 Indoor unit expansion valve

Claims (9)

A feed screw mechanism by screw engagement between a male screw member and a female screw member, wherein the feed screw mechanism is driven to rotate by an electric motor, and the rotary motion is converted into a linear motion in the valve lift direction by the feed screw mechanism; In the electric control valve that moves the valve body in the valve lift direction,
A flow rate control region in which a valve lift position for setting a minimum flow rate and a valve lift position for setting a maximum flow rate are set by movement of the valve body in the valve lift direction, and quantitative flow control is performed between the valve lift positions. The electric control valve is set to a fully closed position in which the valve body is fully closed by moving in the valve opening direction beyond the valve lift position for setting the maximum flow rate from the flow rate control region .   The valve body is defined around the valve port and a flow rate control unit that performs quantitative flow rate control by increasing or decreasing the effective opening area of the valve port formed in the valve housing by movement in the valve lift direction. The electric control valve according to claim 1, further comprising: a fully closed portion that closes the valve port by being seated on a fully closed valve seat portion. An electric motor;
A feed screw mechanism that is rotationally driven by the electric motor and converts rotational motion into linear motion;
A valve housing with a valve port;
It is driven in the valve lift direction by the linear motion of the feed screw mechanism, and quantitatively between the valve lift position that sets the minimum flow rate and the valve lift position that sets the maximum flow rate by increasing or decreasing the effective opening area of the valve port. A flow control valve body that performs proper flow control,
An open / close valve body that closes the valve port by sitting on a fully-closed valve seat portion defined around the valve port;
In the state where the flow control valve body is in a flow control region between the valve lift position for setting the minimum flow rate and the valve lift position for setting the maximum flow rate, the valve seat portion is opened by the flow control valve body. It is prohibited to be seated on the valve seat portion while being held at a further distance, and the flow rate control valve element moves in the valve opening direction beyond the valve lift position that sets the maximum flow rate from the flow rate control range. An electric control valve that can be seated on the valve seat by   The flow control valve body moves in the valve lift direction beyond the valve lift position that sets a minimum flow rate from the flow control region, thereby another valve for full closure defined around the valve port. The electric control valve according to claim 3, wherein the electric control valve is seated on the seat and is fully closed. An electric motor;
A feed screw mechanism that is rotationally driven by the electric motor and converts rotational motion into linear motion;
A valve housing comprising a flow control valve port and a fully closed valve port defining a fully closed valve seat portion in a series relationship;
Driven in the valve lift direction by the linear movement of the feed screw mechanism, and between the valve lift position that sets the minimum flow rate and the valve lift position that sets the maximum flow rate by increasing or decreasing the effective opening area of the flow control valve port A flow control valve that performs quantitative flow control at
An open / close valve body that closes the full-close valve port by sitting on the valve seat portion defined by the full-close valve port;
In the state where the flow control valve body is in a flow control region between the valve lift position for setting the minimum flow rate and the valve lift position for setting the maximum flow rate, the valve seat portion is opened by the flow control valve body. It is prohibited to be seated on the valve seat for full closure while being held at a further distance, and the flow rate control valve element exceeds the valve lift position at which the maximum flow rate is set from the flow rate control region in the valve opening direction. An electric control valve that can be seated on the valve seat by moving.   The electric control valve according to any one of claims 3 to 5, wherein the on-off valve body exerts differential pressure across the valve port in a direction in which the valve seat is seated on the valve seat portion.   The electric control valve according to any one of claims 3 to 6, further comprising a spring that biases the on-off valve body in a valve closing direction that is seated on the valve seat portion.   A refrigeration cycle apparatus having the electric control valve according to any one of claims 1 to 7 as an expansion valve in a refrigerant circuit.   The refrigeration cycle apparatus according to claim 8, wherein the refrigeration cycle apparatus is a multi-type refrigeration cycle apparatus in which a plurality of indoor units are connected in parallel to one common outdoor unit.

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