CN110345292B - Electric valve - Google Patents
Electric valve Download PDFInfo
- Publication number
- CN110345292B CN110345292B CN201910204636.0A CN201910204636A CN110345292B CN 110345292 B CN110345292 B CN 110345292B CN 201910204636 A CN201910204636 A CN 201910204636A CN 110345292 B CN110345292 B CN 110345292B
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- Prior art keywords
- valve
- male screw
- screw shaft
- spring
- port
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- 230000008878 coupling Effects 0.000 claims description 26
- 238000010168 coupling process Methods 0.000 claims description 26
- 238000005859 coupling reaction Methods 0.000 claims description 26
- 239000012530 fluid Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 description 17
- 239000011347 resin Substances 0.000 description 6
- 229920005989 resin Polymers 0.000 description 6
- 239000011258 core-shell material Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910001369 Brass Inorganic materials 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- -1 for example Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
- F16K1/38—Valve members of conical shape
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/48—Attaching valve members to screw-spindles
- F16K1/487—Attaching valve members to screw-spindles by a fixing element extending in the axial direction of the spindle, e.g. a screw
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Lift Valve (AREA)
Abstract
The invention provides an electrically operated valve, in which when a valve port is moved from an open state to a closed state and from the closed state to the open state by a valve core, an abutting end between an abutting end of a connecting part of a valve rod and a concave part of a spring support is prevented from touching an inclined surface of the concave part, thereby avoiding the obstacle of the action. Between the connection part (14C) of the male screw shaft (14) and the recess (24R) of the extension part (24T) of the spring holder member (24), the value of the angle beta formed by the taper surface of the recess in the recess (24R) of the spring holder member (24) and the central axis is set to be equal to or less than the value of the angle alpha formed by the taper surface of the convex abutment end part (14FE) of the male screw shaft (14) and the central axis.
Description
Technical Field
The present invention relates to an electrically operated valve used in a refrigeration cycle or the like.
Background
In a refrigeration cycle apparatus, an electrically operated valve as an expansion valve is disposed between a condenser and an evaporator and used for flow rate control of refrigerant or the like, and in the electrically operated valve, it is particularly important to ensure the accuracy of the axial center of a valve element and a valve port. Such an electrically operated valve is driven by a stepping motor, converts the rotational motion of a rotor into a linear motion by a feed screw mechanism of a male screw member and a female screw member, and separates and contacts a valve element from and with a valve port, and as shown in patent document 1, for example, the electrically operated valve is configured to include as main components: a valve main body having a valve seat member formed with a valve port communicating with the valve chamber; a valve core for opening and closing the valve port; a cylindrical valve body (referred to as a valve guide in patent document 1) coupled to the valve body; a valve rod connected with the valve core shell and provided with an external thread which enables the valve core and the valve core shell to move up and down; a stepping motor for controlling the rotation of the valve rod; and a female screw member (referred to as a stem holder in patent document 1) screwed to the male screw of the valve stem. A resin spring holder and a valve spring that biases the spring holder toward the coupling portion of the valve rod in a direction away from the valve element are provided between the coupling portion formed at the lower end of the valve rod and the valve element in the valve element case. The upper end of the valve body housing is connected to the connection portion of the valve rod via the through hole and the resin washer. The concave portion formed in the upper portion of the spring holder is formed as a pressure receiving surface that receives a convex abutting end formed in the coupling portion of the valve stem by the biasing force of the valve spring. In this case, the center position of the pressure receiving surface of the spring holder and the center position of the abutment end of the valve rod are arranged on the common central axis. Further, the upper end portion of the valve body housing is movable relative to the coupling portion of the stem in the radial direction of the stem via the gasket.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2017-161052
Disclosure of Invention
In the electrically operated valve disclosed in patent document 1, when the valve body has the valve port closed, the valve body and the valve element are lowered together with the valve stem, the end of the valve element is inserted into the valve port, and the valve element abuts against the valve seat. After the valve element abuts against the valve seat, the valve rod is further rotated and lowered against the urging force of the valve spring via the spring holder, and the valve element is pressed against the valve seat. Thus, the valve body reliably closes the valve port of the valve body. In this case, since the concave portion of the spring holder contracts the valve spring while receiving the rotation of the abutment end of the valve rod, the valve spring is likely to be twisted, and the spring holder is likely to be inclined with respect to the abutment end of the valve rod. Further, due to a radial gap between the valve stem and the valve body case and the gasket, a backlash between the external thread of the valve stem and the internal thread of the internal thread member, and the like, the axis of the valve stem may be displaced from the central axis of the recess of the spring holder.
Further, when the valve element is in the open state with the valve port of the valve body open, and the valve element is separated from the valve seat from the state in which the valve element is seated on the valve seat, the valve element is separated from the valve seat while the recessed portion of the spring holder is pressed against the abutment end of the rotating valve rod by the restoring force of the valve spring when the valve rod is rotated and raised. Thereby, the valve port of the valve body is opened. At this time, when the valve spring is expanded from the compressed state, the spring holder may be inclined with respect to the abutting end of the valve stem due to the twisting of the valve spring, as in the case of the closed state described above. Further, due to a radial gap between the valve stem and the valve body case and the gasket, a backlash between the external thread of the valve stem and the internal thread of the internal thread member, and the like, the axis of the valve stem may be displaced from the central axis of the recess of the spring holder.
When the valve body is closed or opened by the valve element, the contact end of the spring holder is inclined with respect to the contact end of the valve stem, and the valve stem is displaced from the axis of the recess of the spring holder, the convex contact end of the coupling portion of the valve stem may contact the tapered surface of the recess of the spring holder.
This causes the posture of the spring holder to be inclined with respect to the connecting portion of the valve rod, and there is a possibility that the spring load and the thrust force of the valve rod screw cannot be transmitted in the direction of the center axis line with a normal load. Further, the valve element may not be normally seated on the valve seat, and sliding resistance between the stem and the spring holder, between the valve element and the valve seat, between the valve element case and the gasket, and sliding resistance between the outer periphery of the valve element case and the inner periphery of the female screw member may increase, thereby causing an obstacle to the operation of the electric valve.
In order to solve such a problem, for example, it is conceivable to form the convex abutting end of the coupling portion of the valve stem into a hemispherical shape. However, since the hemispherical abutting end is point-contacted with the pressure receiving surface of the spring holder, the amount of wear of the pressure receiving surface of the resin spring holder may be relatively large, which is not a good countermeasure.
In view of the above problems, an object of the present invention is to provide an electrically operated valve capable of avoiding an operational failure by preventing an abutment end from contacting an inclined surface of a recessed portion between an abutment end of a coupling portion of a valve stem and the recessed portion of a spring holder when a valve port is moved from an open state to a closed state and from the closed state to the open state by a valve body.
In order to achieve the above object, an electrically operated valve according to the present invention includes: a valve body portion having a first port connected to the first passage and a second port connected to the second passage, and a housing portion communicating with the first port and the second port and housing a valve element unit in a movable manner, the valve element unit including a valve element that controls opening and closing of the second port; and a spool unit drive mechanism that causes the spool unit to perform an operation of opening and closing control of the second port in a manner of adjusting a flow rate of the fluid passing between the front end portion of the spool and the periphery of the second port, the spool unit drive mechanism being a mechanism that converts the rotational motion of the rotor into a linear motion by means of the male screw shaft and the female screw member, the spool unit further including: a valve body housing which is movably connected to a connection end of the male screw shaft in the valve body unit drive mechanism via a washer and holds the valve body; a spring support member disposed within the valve core housing; and a spring member that biases the spring holder member in a direction away from the valve element, wherein a convex abutment end is formed on one of a connection portion of the male threaded shaft and an abutment portion of the spring holder member facing the connection portion, and a concave portion serving as a pressure receiving surface for receiving the abutment end is formed on the other, and a relationship between a value of an angle α formed by a tapered surface of the convex abutment end and a central axis and a value of an angle β formed by a tapered surface of the concave portion serving as the pressure receiving surface and the central axis is set to α or more than β.
The angle β may be set to 45 ° or less. The convex abutting end may be formed at the coupling portion of the male screw shaft and the concave portion may be formed at the upper portion of the spring bearing member as a pressure receiving surface for receiving the abutting end of the male screw shaft, or the convex abutting end may be formed at the upper portion of the spring bearing member and the concave portion may be formed at the coupling portion of the male screw shaft as a pressure receiving surface for receiving the abutting end of the spring bearing member.
Further, the longitudinal cross-sectional shape of the convex abutting end may be substantially a truncated cone, and the depth of the concave portion as the pressure receiving surface may be set to be larger than the radius of the corner of the smallest diameter portion of the convex abutting end.
The effects of the present invention are as follows.
According to the motor-operated valve of the present invention, since the relationship between the value of the angle α obtained by bisecting the apex angle of the convex abutment end by the central axis and the value of the angle β obtained by bisecting the taper angle of the recess formed as the pressure receiving surface by the central axis is set to α or more, the movement in the radial direction from the central axis between the connection portion of the male screw shaft and the spring bearing member is restricted by the peripheral portion of the tapered surface of the recess forming the pressure receiving surface of the recess being abutted by the tapered surface of the convex abutment end. Thus, when the valve port is moved from the open state to the closed state by the valve element, and when the valve port is moved from the closed state to the open state by the valve element, while the valve element is in contact with the valve seat, the convex contact end, which is caused by the inclination of the spring holder due to the twisting of the valve spring and the relative radial displacement of the center position of the spring holder with respect to the coupling portion of the valve stem due to the clearance between each portion of the valve element unit and the valve stem, can be prevented from coming into contact with the tapered surface forming the concave portion receiving the pressure receiving surface of the convex contact end. Therefore, it is possible to prevent unnecessary sliding resistance from being generated during the operation of the valve stem and the valve element, to ensure normal seating of the valve element and the valve seat, and to avoid the occurrence of an obstacle in the operation of the electric valve.
Drawings
Fig. 1 is a partially enlarged cross-sectional view showing a connection end portion of a male threaded shaft, a spring bearing member, and a washer used in an example of an electric valve according to the present invention.
Fig. 2 is a partially enlarged cross-sectional view showing a part of a coupling end portion of a male threaded shaft, a spring bearing member, and a washer as another example used in one example of the motor-operated valve according to the present invention.
Fig. 3 is a cross-sectional view schematically showing the overall configuration of an example of an electrically operated valve according to the present invention.
Fig. 4 is a partial sectional view illustrating the operation of the coupling end portion of the male screw shaft, the spring bearing member, and the washer used in the example shown in fig. 3.
In the figure:
12-a guide support; 12B — an internal threaded portion; 12 FMS-internal thread; 14-an externally threaded shaft; 14C-connecting end portion; 14F — an extension; 14 FE-abutment end portion; 16-a gasket; 18-a cartridge housing; 22-a helical spring; 24-a spring support member; 24R — concave; 24T — extension; 26-a valve core; 30-a valve body portion; 30V-valve seat; 30 Va-valve port.
Detailed Description
Fig. 3 shows a configuration of an example of an electrically operated valve according to the present invention together with a piping tube.
In fig. 3, the motor-operated valve is disposed as an expansion valve between a condenser and an evaporator in the air-conditioning apparatus, for example. The electric valve includes: a valve driving unit disposed in the cylindrical rotor case 20 and driving a valve element unit described later; a valve body 30 connected to an end of the rotor case 20 and having a valve seat 30V opened and closed by a distal end of the valve element 26; and a valve body unit which is disposed in the valve body 30 and includes a valve body 26 that opens and closes a valve seat 30V.
The valve drive unit is configured to include, as main components: an external screw shaft 14 for moving the valve element unit up and down; a guide support portion (female screw member) 12 having a female screw portion 12B formed with a female screw 12FMS fitted to the male screw shaft 14 and fixed to the valve body portion 30 to guide the valve element unit to be movable up and down; a rotor 10 fixed to a guide shaft portion 14A of the male screw shaft 14, rotatably supported, and magnetized; and a stator coil (not shown) disposed on an outer peripheral portion of the rotor case 20 and configured to rotate the rotor 10.
The guide support portion 12 has a guide surface on an inner peripheral portion thereof, which guides the cylindrical valve body housing 18 of the valve body unit to be movable up and down while rotating.
The externally threaded shaft 14 includes: an external thread portion 14B fitted into the internal thread 12FMS of the internal thread portion 12B; a connection portion 14C formed at the lower end of the male screw portion 14B and engaged with the periphery of the through hole 18a of the valve body 18 via a gasket 16; and a guide shaft portion 14A formed at the upper end of the male screw portion 14B. The guide shaft portion 14A is rotatably supported in a cylindrical portion 20C, and the cylindrical portion 20C protrudes from the top portion in the rotor case 20 toward the guide support portion 12 along the center axis.
A spiral guide portion 11 is formed on the outer peripheral portion of the cylindrical portion 20C, and the spiral guide portion 11 guides the movable stopper piece 13 to move in the central axis direction of the cylindrical portion 20C while rotating. One end of the movable stopper piece 13 is locked to the protrusion of the rotor 10. Further, rotation stoppers 20US and 20LS of the movable stopper piece 13 are provided at the uppermost end portion and the lowermost end portion of the cylindrical portion 20C, respectively. Thus, when the movable stopper piece 13 abuts against the rotation stoppers 20US and 20LS, the movable stopper piece 13 is stopped at a predetermined rotation angle corresponding to a predetermined valve closing position and a predetermined valve opening (full opening) position of the valve body 26, which will be described later.
The valve driving unit is controlled based on a drive pulse signal supplied to the stator coil by a drive control unit, not shown.
The valve body unit is configured to include, as main components: a needle-like valve element 26 that opens and closes a valve port 30Va of a valve seat 30V described later; a cylindrical resin spring holder member 24 that engages the extension 14F of the coupling portion 14C of the male screw shaft 14 with the inner periphery of the opening end 18T of the valve body case 18 in cooperation with the resin washer 16; a coil spring 22 disposed between the extension portion 24T of the spring bearing member 24 and the annular flat portion for spring bearing of the one end 26EA of the valve body 26 and biasing the two directions away from each other; and a cylindrical valve body case 18 that houses the spring holder member 24, the coil spring 22, and one end 26EA of the valve body 26.
One end of the cylindrical valve body case 18 close to the valve seat 30V is closed by an outer peripheral portion of one end 26EA of the fixed valve body 26. As partially enlarged in fig. 4, the other side of the cylindrical valve body housing 18 is an opening end portion 18T having a hole 18a through which the reduced diameter portion 14Cd of the positioning washer 16 in the coupling portion 14C of the threaded shaft 14 passes. Therefore, the gasket 16 is disposed between the inner periphery of the opening end portion 18T of the valve body case 18 and one end surface of the extension portion 14F.
The reduced diameter portion 14Cd of the coupling portion 14C of the male screw shaft 14 is formed integrally with one end surface of the projecting portion 14F. The diameter of the reduced diameter portion 14Cd is set smaller than the inner diameter of the hole 18 a. A predetermined gap is formed between the inner peripheral surface of the hole 16a of the washer 16 and the outer peripheral surface of the reduced diameter portion 14 Cd. As partially enlarged in fig. 1, an abutment end portion 14FE having a substantially truncated conical longitudinal cross-sectional shape is integrally formed on the other end surface of the extension portion 14F. The abutment end portion 14FE abuts on a pressure receiving surface formed by the substantially inverted truncated conical recess 24R of the extension portion 24T of the spring bearing member 24.
The minimum diameter φ DE of the abutment end portion 14FE is set to, for example, about 1.8 mm. An angle α (1/2 at the apex angle of the abutment end portion) formed by the tapered surface of the abutment end portion 14FE and the central axis C is set to a value equal to or larger than an angle β (1/2 at the taper angle of the pressure receiving surface) formed by the tapered surface of the pressure receiving surface in the recess 24R of the extension portion 24T of the spring bearing member 24 and the central axis C and equal to or smaller than 75 °, for example. The diameter φ BE of the pressure receiving surface forming the bottom of the concave portion 24R is set to, for example, about 2.0 mm. The angle β is set to a predetermined value of 45 ° or less, for example. The depth Dp of the recess 24R is preferably set to be larger than the radius of the arc Ra of the corner of the smallest diameter portion of the contact end portion 14FE, for example.
The outer peripheral portion of the cylindrical valve body case 18 is supported so as to be movable up and down while being in sliding contact with the guide surface of the guide support portion 12. Thus, after the tip (needle portion) of the other end 26EB of the valve element 26 is inserted into the valve port 30Va of the valve seat 30V and the outer peripheral surface of the needle portion of the valve element 26 abuts on the periphery of the opening portion of the valve port 30Va, the coil spring 22 is compressed by a predetermined amount when the male screw shaft 14 continues to descend. As a result, as shown in fig. 3, the outer peripheral surface of the needle portion of the valve body 26 is pressed against the periphery of the opening portion of the valve port 30Va by the spring force of the coil spring 22. Thereby, the valve port 30Va of the valve seat 30V is closed.
The valve body 30 is made of a metal material, for example, brass, stainless steel, aluminum alloy, or a resin material, and has a lower end of the guide support portion 12 below the receiving female screw portion 12B, the other end 26EB of the valve element 26, and a valve element receiving portion 30A of the cylindrical valve element housing 18 on the inner side. In the valve body housing portion 30A, the other end 26EB of the valve body 26 protrudes toward the valve port 30 Va. Further, the valve body housing portion 30A includes: a first port 32P to which one end of a connection pipe 32 as a first passage is connected on an axis substantially orthogonal to the center axis of the valve body 26; and a valve seat 30V adjacent to the second port 34P as one end of a connecting pipe 34 of the second passage is connected to an axis common to the center axis of the valve body 26.
In such a configuration, the stator coil of the valve driving unit is controlled by a drive pulse signal from the drive control unit, and the valve element 26 moves up and down, so that the refrigerant as the fluid supplied through the connection pipe 32 or the connection pipe 34 passes through the slit flow channel formed between the inner peripheral surface of the valve seat 30V where the valve port 30Va is formed and the needle portion of the other end 26EB of the valve element 26 at a predetermined flow rate in the direction indicated by the arrow F or the arrow R.
When the above-described valve port 30Va is moved from the open state to the closed state by the needle portion of the other end 26EB of the valve element 26, the washer 16, the valve element case 18, and the valve element 26 descend while rotating in synchronization with the rotation of the male screw shaft 14 until the outer peripheral surface of the needle portion abuts against the opening edge of the valve port 30 Va. Thereafter, since the outer peripheral surface of the needle portion abuts against the periphery of the opening portion of the valve port 30Va, when the male screw shaft 14 continues to further lower, the rotation of the valve element 26 and the valve element housing 18 is suppressed, and as shown in fig. 4 in a partially enlarged manner, the coupling portion 14C of the rotating male screw shaft 14 lowers by a predetermined amount together with the spring bearing member 24 against the biasing force of the coil spring 22. At this time, the recess 24R of the spring bearing member 24 receives the rotational force of the abutment end 14FE of the male screw.
When the valve port 30Va is shifted from the closed state to the open state, the rotation of the valve element 26 and the valve element case 18 is suppressed while the outer peripheral surface of the needle portion of the other end 26EB of the valve element 26 abuts on the periphery of the opening portion of the valve port 30 Va. When the male screw shaft 14 is rotated and raised, the coil spring 22 is extended by the restoring force of the coil spring 22 while the recess 24R of the spring receiving member 24 receives the rotational force of the abutment end 14FE of the male screw shaft 14. Thereafter, when the outer peripheral surface of the needle portion is separated from the periphery of the opening portion of the valve port 30Va, the gasket 16, the valve body case 18, and the valve body 26 rise while rotating in synchronization with the rotation of the male screw shaft 14, and thereby the valve port 30Va is opened.
In this way, when the valve port 30Va is moved from the open state to the closed state and from the closed state to the separated state, while the outer peripheral surface of the needle portion is in contact with the periphery of the opening portion of the valve port 30Va, the concave portion 24R of the spring support member 24 receives the rotational force of the contact end 14F of the male screw 14 while receiving the restoring force of the coil spring 22 when the male screw shaft 14 is operated, and therefore, when the coil spring 22 contracts and expands, twisting is likely to occur. Accordingly, the contact end 14F of the male screw 14 is inclined in the recess 24R of the spring bearing member 24, and further, due to a radial gap between the respective portions of the valve body unit (between the male screw shaft 14 and the valve body housing 18, between the male screw shaft 14 and the washer 16, or between the washer 16 and the valve body housing 18), the central axis C of the coupling portion 14C of the rotating male screw shaft 14 may be radially offset from the central axis of the spring bearing member 24.
Even in such a case, by setting the angle β of the recess 24R of the spring bearing member 24 to be equal to or smaller than the angle α of the convex abutment end of the male screw shaft 14, as shown in fig. 1 and 4, the tapered surface of the outer periphery of the abutment end 14FE of the male screw shaft 14 abuts against the periphery of the tapered surface of the recess 24R of the spring bearing member 24, and further, even if a force that is biased radially outward acts on the male screw shaft 14, as shown in fig. 1 and 4, the truncated cone-shaped abutment end portion 14FE of the coupling portion 14C abuts against the abutment portion TP of the recess 24R formed on the pressure receiving surface of the projecting portion 24T of the spring bearing member 24, and a radial reaction force indicated by an arrow F acts on the abutment end portion 14 FE.
This prevents the truncated cone shaped abutment end portion 14FE from touching the inclined surface (tapered surface) of the recess 24R of the spring bearing member 24. Thus, the following situation is avoided: when the valve port 30Va of the valve seat 30V is shifted from the closed state to the open state, the contact end portion 14FE of the coupling portion 14C of the male screw shaft 14 contacts the tapered surface of the recessed portion 24R, and thus, an unnecessary increase in frictional resistance and an increase in the amount of wear are caused by interference between the contact end portion 14FE and the tapered surface of the recessed portion 24R, interference between the outer periphery of the reduced diameter portion 14Cd of the coupling portion 14C of the male screw shaft 14 and the inner periphery of the washer 16, interference between the outer periphery of the washer 16 and the inner periphery of the valve body housing 18, interference between the outer periphery of the valve body housing 18 and the inner periphery of the guide support portion 12, and the like. Further, it is possible to avoid the deterioration of the flow rate accuracy due to the deviation of the center axis of the valve element 26 coupled to the valve element case 18 from the center axis of the valve port 30Va of the valve seat 30V, and the wear of the needle portion of the other end 26EB of the valve element 26 due to the deviation of the needle portion of the other end 26EB of the valve element 26 into contact with the inner peripheral portion of the valve port 30 Va.
Fig. 2 is an enlarged view of a part of the male screw shaft 15 as another example of the male screw shaft for moving the valve body unit up and down, the spring holder member 25 as another example of the spring holder member, and the washer 16, which are used in one example of the motor-operated valve shown in fig. 3. In the example shown in fig. 1 and 3, the male screw shaft 14 has an abutment end portion 14FE having a substantially truncated cone-shaped longitudinal cross-sectional shape integrally formed on the other end surface of the extension portion 14F, and the extension portion 24T of the spring bearing member 24 has a recess portion 24R having a pressure receiving surface against which the abutment end portion 14FE abuts, but instead, in fig. 2, the extension portion 15F of the coupling portion 15C of the male screw shaft 15 has a recess portion 15R having a pressure receiving surface against which a truncated cone-shaped abutment end portion 25C formed on the extension portion 25T of the spring bearing member 25 abuts. Further, as in the example shown in fig. 3, the male screw shaft 15 is supported by a guide support portion 12 (not shown) having a female screw portion 12B, and the female screw portion 12B is formed with a female screw 12FMS fitted to the male screw shaft 15. The washer 16 positioned at the reduced diameter portion 15Cd of the male screw shaft 15 is disposed between the inner periphery of the opening end portion 18T of the valve body case 18, not shown, and one end surface of the extension portion 15F. The truncated cone shaped contact end portion 25C formed in the extension portion 25T of the spring bearing member 25 is biased toward the recess 15R by the coil spring 22 (not shown).
The minimum diameter Φ DE of the abutment end portion 25C of the spring bearing member 25 is set to, for example, about 1.8 mm. The angle α (1/2 at the apex angle of the contact end) formed by the tapered surface of the contact end 25C of the spring bearing member 25 and the central axis C is set to a value equal to or greater than an angle β (1/2 at the taper angle of the pressure receiving surface) formed by the tapered surface of the pressure receiving surface and the central axis C in the recess 15R of the extension 15F of the connection portion 15C of the male screw shaft 15 and equal to or less than 75 °, for example. The diameter φ BE of the pressure receiving surface of the bottom of the recess 15R forming the projecting portion 15F is set to, for example, about 2.0 mm. The angle β is set to a predetermined value of 45 ° or less, for example. The depth Dp of the recess 15R of the protruding portion 15F is preferably set to be larger than the radius of the arc Ra of the corner of the smallest diameter portion of the contact end 25C, for example.
In the example shown in fig. 2, the same operational effects as those of the example shown in fig. 1 described above are obtained by setting the angles α and β in this manner.
Claims (8)
1. An electrically operated valve, comprising:
a valve body portion having a first port connected to a first passage and a second port connected to a second passage, and a housing portion communicating with the first port and the second port and housing a valve element unit in a movable manner, the valve element unit including a valve element that controls opening and closing of the second port;
a valve element unit drive mechanism that causes the valve element unit to perform an operation of opening and closing the second port so as to adjust a flow rate of the fluid passing between a tip portion of the valve element and a periphery of the second port,
the above-mentioned valve core unit driving mechanism is a mechanism for converting the rotational motion of the rotor into a linear motion by means of the male screw shaft and the female screw member,
the above-mentioned spool unit further includes: a valve body case movably coupled to a coupling end of the male screw shaft in the valve body unit drive mechanism via a washer to hold the valve body; a spring support member disposed within the valve core housing; and a spring member for urging the spring holder member in a direction away from the valve element,
a convex abutment end is formed on one of the connection portion of the male screw shaft and the abutment portion of the spring bearing member opposed thereto, and a concave portion as a pressure receiving surface for receiving the abutment end is formed on the other, and a relationship between a value of an angle α formed by a tapered surface of the convex abutment end and a central axis and a value of an angle β formed by a tapered surface of the concave portion formed as the pressure receiving surface and the central axis is set as follows:
α≥β。
2. electrically operated valve according to claim 1,
the angle β is set to 45 ° or less.
3. Electrically operated valve according to claim 1,
the convex contact end is formed at the coupling portion of the male screw shaft, and the concave portion is formed at the upper portion of the spring receiver member as a pressure receiving surface for receiving the contact end of the male screw shaft.
4. Electrically operated valve according to claim 2,
the convex contact end is formed at the coupling portion of the male screw shaft, and the concave portion is formed at the upper portion of the spring receiver member as a pressure receiving surface for receiving the contact end of the male screw shaft.
5. Electrically operated valve according to claim 1,
the convex contact end is formed at an upper portion of the spring holder member, and the concave portion is formed at the coupling portion of the male screw shaft as a pressure receiving surface for receiving the contact end of the spring holder member.
6. Electrically operated valve according to claim 2,
the convex contact end is formed at an upper portion of the spring holder member, and the concave portion is formed at the coupling portion of the male screw shaft as a pressure receiving surface for receiving the contact end of the spring holder member.
7. Electrically operated valve according to one of the claims 1 to 6,
the convex abutting end has a substantially truncated cone longitudinal cross-sectional shape.
8. Electrically operated valve according to one of the claims 1 to 6,
the depth of the concave portion as the pressure receiving surface is set to be larger than the value of the radius of the corner of the minimum diameter portion of the convex contact end.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-072564 | 2018-04-04 | ||
| JP2018072564A JP6790012B2 (en) | 2018-04-04 | 2018-04-04 | Solenoid valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110345292A CN110345292A (en) | 2019-10-18 |
| CN110345292B true CN110345292B (en) | 2021-04-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910204636.0A Active CN110345292B (en) | 2018-04-04 | 2019-03-18 | Electric valve |
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| Country | Link |
|---|---|
| JP (1) | JP6790012B2 (en) |
| CN (1) | CN110345292B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7254678B2 (en) * | 2019-10-28 | 2023-04-10 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2929225Y (en) * | 2006-06-30 | 2007-08-01 | 柳州华威电控燃油喷射***技术有限公司 | Electromagnetic electric control diesel oil injector |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5833874U (en) * | 1981-08-28 | 1983-03-05 | 株式会社横河電機製作所 | servo valve |
| JP4220178B2 (en) * | 2001-09-03 | 2009-02-04 | 株式会社鷺宮製作所 | Motorized valve |
| CN100487290C (en) * | 2006-06-26 | 2009-05-13 | 上海康源电气有限公司 | Multi-path output controlling valve |
| JP5778902B2 (en) * | 2010-09-15 | 2015-09-16 | 株式会社不二工機 | Female thread member, motor-operated valve using the same, and method for manufacturing female thread member for motor-operated valve |
| DE102012011962B4 (en) * | 2012-06-18 | 2016-10-06 | Robert Bosch Gmbh | Valve attachment for a radiator control valve with electronic motor and spring and with or without expansion body |
| CN203430633U (en) * | 2013-07-31 | 2014-02-12 | 瑞立集团瑞安汽车零部件有限公司 | Pressure regulation solenoid valve |
| CN104482276B (en) * | 2014-12-03 | 2016-11-23 | 吉林东光奥威汽车制动***有限公司 | A kind of brake system of car bidirectional electromagnetic valve |
| JP2017161052A (en) * | 2016-03-11 | 2017-09-14 | 株式会社鷺宮製作所 | Electric operated valve |
-
2018
- 2018-04-04 JP JP2018072564A patent/JP6790012B2/en active Active
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2019
- 2019-03-18 CN CN201910204636.0A patent/CN110345292B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2929225Y (en) * | 2006-06-30 | 2007-08-01 | 柳州华威电控燃油喷射***技术有限公司 | Electromagnetic electric control diesel oil injector |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110345292A (en) | 2019-10-18 |
| JP6790012B2 (en) | 2020-11-25 |
| JP2019183892A (en) | 2019-10-24 |
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