WO2002018828A1 - Vanne electromagnetique - Google Patents

Vanne electromagnetique Download PDF

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Publication number
WO2002018828A1
WO2002018828A1 PCT/JP2001/007282 JP0107282W WO0218828A1 WO 2002018828 A1 WO2002018828 A1 WO 2002018828A1 JP 0107282 W JP0107282 W JP 0107282W WO 0218828 A1 WO0218828 A1 WO 0218828A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
solenoid valve
inner peripheral
sleeve
peripheral wall
Prior art date
Application number
PCT/JP2001/007282
Other languages
English (en)
Japanese (ja)
Inventor
Ichiro Hirata
Norio Uemura
Yoshinari Kasagi
Original Assignee
Nok Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nok Corporation filed Critical Nok Corporation
Priority to AU2001280160A priority Critical patent/AU2001280160A1/en
Priority to DE10196576T priority patent/DE10196576B4/de
Priority to JP2002523515A priority patent/JP4210775B2/ja
Priority to US10/362,372 priority patent/US6971627B2/en
Publication of WO2002018828A1 publication Critical patent/WO2002018828A1/fr

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Classifications

    • 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
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • 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
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0668—Sliding valves

Definitions

  • the present invention relates to a solenoid suitably used for various fluid pressure controls and the like.
  • FIG. 8 is a schematic configuration sectional view of a solenoid valve according to the related art.
  • the solenoid valve 200 includes a solenoid part 200 A, a valve part 200 B, and a cap.
  • the knob portion 200B is a spool valve, and since the opening area of the valve changes in accordance with the stroke of the spool, the amount of fluid inflow and the amount of fluid can be controlled by controlling the stroke amount of the spool with a solenoid. It is configured to control the amount of outflow.
  • the solenoid part 200 A is generally driven by a coil 203, a plunger 201 magnetically attracted to the center post 202 by energizing the coil 203, and a drive of the plunger 201. And a rod 204 connected to the plunger 201 for transmitting the pressure to the valve portion 200B (specifically, the spool).
  • the plunger 201 is configured to be located away from the center post 202 in a normal state, that is, in a state in which the coil 203 is not energized.
  • the plunger 201 is configured to be biased in a direction away from the center post 202 by a biasing member such as a spring.
  • the plunger is configured to be separated from the center post 202 via the spool by providing a spring that biases the spool in the direction of the solenoid portion 20OA.
  • the magnetic force can be controlled by the magnitude of the current flowing through the coil 203, whereby the amount of movement of the plunger 201 is controlled by controlling the balance with the biasing member such as a spring.
  • the stroke amount can be controlled, thereby controlling the flow rate of the fluid, and performing various fluid pressure controls such as hydraulic control.
  • the basic performance required of a solenoid valve generally includes coaxiality. This is because if the coaxiality is insufficient, the plunger rod tilts with respect to the axis and repeats reciprocating motion, resulting in uneven wear in which only a part is worn, and the characteristics in the forward and return paths are reduced. This is because it leads to deterioration of control characteristics such as changing hysteresis and bias of magnetic flux toward the plunger.
  • This coaxiality is determined by the dimensioning of each member, but as the number of members involved in axis alignment increases, the error propagation increases due to the dimensional tolerance of each member. You.
  • the members involved in centering directly or indirectly contact the plunger 201, the center-to-bottom 202 and the opening 204. It is a supporting member.
  • the plate 207, the lower plate 209, and the case 209 are nine members.
  • the members involved in the centering are five members: a plunger, a rod, a center post, a sleeve, and a rod bearing. It is possible to improve the degree.
  • the plunger performs smoothly and stably in a reciprocating motion, so that it has excellent slidability with respect to the inner circumference of the sleeve serving as the bearing, and has both ends in the axial direction.
  • Pressure at It is required to provide a flow path (oil path etc.) on the outer peripheral surface of the plunger in order to eliminate the force load and enhance the slidability.
  • FIG. Fig. 7 is a schematic cross-sectional view of a plunger according to the prior art.
  • (A) is a cross-sectional view cut through the shaft center
  • (B) is a cross-sectional view cut along the axis ⁇ vertical direction (AA in (A)).
  • (It is a cross section and corresponds to the whole part.)
  • the plunger 301 As shown in the figure, the plunger 301 according to the prior art has a substantially cylindrical shape, is provided with a large-diameter portion 301 a that slides on the inner periphery of the sleeve, and has a groove 310 serving as a flow path. 1b is formed by cutting.
  • the inner circumference of the sleeve and the plunger 301 slide while contacting curved surfaces having substantially the same diameter, and the liquid (oil) force S flows through the flow path, so that no pressure load is applied. Since the liquid slides while obtaining lubricity, the reciprocating operation can be suitably performed.
  • the plunger slides against the sleeve while making contact at one point in the cross section perpendicular to the axis.
  • the sliding wear was poor.
  • the gap near the sliding part is very narrow, and when foreign matter (impurity) enters, the foreign matter remains trapped. There was a problem that slidability deteriorated.
  • An object of the present invention is to provide a solenoid pulp having improved controllability and improved slidability of a plunger. Disclosure of the invention
  • a solenoid pulp comprising: a plunger that reciprocates by a magnetic force generated by an exciting unit; and a sleeve that slidably supports the outer periphery of the plunger to perform a bearing.
  • the sleeve has an inner peripheral wall surface for carrying a bearing, and has a circular cross-sectional shape of the inner peripheral wall surface perpendicular to the shaft,
  • a plurality of convex portions extending in the axial direction, having a curved shape having a radius of curvature smaller than a distance from the axis to the outer peripheral surface, and sliding on the inner peripheral wall surface;
  • the curved surface has a radius of curvature smaller than the distance from the axis to the outer peripheral surface, that is, the inner peripheral surface of the sleep also slides on a small curved surface, sliding with only one convex portion is difficult. As it becomes unstable, it slides on two adjacent convex surfaces. In other words, sliding at two points instead of one point in the section perpendicular to the axis as in the past become. As a result, sliding wear is reduced in the case of two-point contact as compared with the case of one-point contact because the load is dispersed.
  • the gap near the sliding portion can be made relatively large, and fluid can easily enter, so that lubricity is improved, and Even if foreign matter enters, it can easily escape to the flow path.
  • the convex portions are provided in the same orientation with respect to the circumferential direction, and are provided at odd positions.
  • the convex portion and the groove have a positional relationship symmetrical with respect to the axis, and in a state where two adjacent convex portions move, the axial center of the intermediate position (groove) between the two convex portions is shifted.
  • the outer peripheral surface on the opposite side across the is most distant from the inner periphery of the sleeve, but since this portion is a convex portion, rattling can be suppressed.
  • the cross section perpendicular to the axial direction of the flow path formed by the groove and the inner peripheral wall has a structure in which impurities contained in the fluid flowing into the solenoid pulp body are removed outside the solenoid valve body before flowing.
  • the size and shape may be set to include the size and shape of the eye of the filter.
  • the size of impurities contained in the fluid flowing into the solenoid valve body by the filter is limited to a size that can pass through the eyes of the filter. Therefore, no impurities are trapped in the flow path.
  • the convex portion and the groove provided on the outer periphery of the plunger are obtained by forging, and
  • a concave portion recessed inside On the end face of the plunger on the side opposite to the pressing direction at the time of forging molding, a concave portion recessed inside is provided, The bottom surface of the concave portion may be a pressed portion which is pressed against the ejector pin to remove the plunger body from the forging die after forging.
  • a solenoid valve comprising: a plunger that reciprocates by a magnetic force of an exciting unit; and a sleeve that slidably supports the outer periphery of the plunger to perform a bearing.
  • the sleeve has an inner peripheral wall surface for carrying a bearing, and has a circular cross-sectional shape of the inner peripheral wall surface perpendicular to the shaft,
  • the outer peripheral shape of a cross section perpendicular to the axial direction, which is a sliding portion with respect to the inner peripheral wall surface of the plunger, is a polygon.
  • polygon means that each corner is R This shall include cases where the shape is used.
  • the plunger having a polygonal cross-sectional outer shape is slidably supported by the inner peripheral wall surface of the sleep having a circular cross-sectional shape. Therefore, the plunger slides at only one corner, so that the plunger slides at two adjacent corners.
  • sliding occurs at two points instead of one point in a cross section perpendicular to the axis.
  • the sliding wear is reduced in the two-point contact as compared with the one-point contact because the load is dispersed.
  • sliding at the corners makes it possible to make the gap near the sliding part relatively large, facilitates fluid entry, and improves lubricity, and even when foreign matter enters. However, the air will escape into the flow path.
  • the outer peripheral shape may be an odd polygon.
  • the outer peripheral shape is preferably a substantially regular octagon.
  • the angular portion and the flat portion of the outer periphery of the plunger have a symmetrical positional relationship with respect to the axis center, and rattling can be reduced.
  • the cross-sectional area of the flow path formed by the outer flat surface portion of the plunger and the inner peripheral wall surface of the sleeve can be set to an appropriate size in consideration of the balance between the supply of the magnetic path and the discharge of foreign matter. .
  • the chuck be a three-point chuck.
  • the outer peripheral shape is a multiple polygon of 3 (regular polygon). It is necessary that the regular octagon satisfies the condition suitably.
  • the cross section perpendicular to the axial direction of the flow path formed by the flat surface portion of the outer periphery of the plunger and the inner peripheral wall surface of the sleeve is provided with impurities contained in the fluid flowing into the solenoid valve main body before the flow. It is recommended that the filter be set to a shape including the size of the mesh of the filter to be removed outside the body of the solenoid valve.
  • the size of the impurities contained in the fluid flowing into the solenoid valve body by the filter is limited to such a size as to pass through the eyes of the filter, and the cross section of the flow path is the size of the eyes of the filter. Since the dimensions include the shape, the impurities do not get caught in the flow path.
  • FIG. 1 is a schematic configuration sectional view of a solenoid valve according to an embodiment of the present invention.
  • FIG. 2 is a schematic configuration sectional view of a plunger according to the first embodiment of the present invention
  • Fig. 3 is a schematic diagram showing the sliding part between the plunger and the inner periphery of the sleeve.
  • FIG. 4 is a schematic diagram showing an example of the shape of a groove provided in the plunger
  • FIG. 5 is a schematic configuration sectional view of the plunger according to the second embodiment of the present invention.
  • FIG. 6 is a schematic view showing a part of the manufacturing process of the plunger according to the embodiment of the present invention.
  • FIG. 7 is a schematic configuration cross-sectional view of a plunger according to the related art
  • FIG. 8 is a schematic configuration cross-sectional view of a solenoid valve according to the related art.
  • FIG. 1 is a schematic configuration of a solenoid valve according to an embodiment of the present invention.
  • FIG. FIG. 2 is a schematic cross-sectional view of a plunger according to a first embodiment of the present invention ((A) is a cross-sectional view cut through an axis, and (B) is a cross-sectional view cut in a direction perpendicular to an axis). (This is the BB cross section in (A) and corresponds to the whole part.)
  • Fig. 3 is a schematic diagram showing the sliding portion between the plunger and the inner periphery of the sleeve.
  • Fig. 5 is a schematic view showing a part of a manufacturing process of a plunger according to an embodiment of the present invention.
  • the solenoid pulp 100 is composed of a solenoid 100 A, a valve 100 B, and a force.
  • valve portion 100B is a spoon lever, and a spool 15 is provided inside the valve sleeve 16 so as to be able to reciprocate, and according to the stroke of the spoon lever 15. Since the opening area of the valve formed in the vanoleb sleeve 16 changes, the amount of fluid inflow and outflow can be controlled by controlling the stroke amount of the spool 15 by the solenoid.
  • the solenoid section 100 A generally includes a coil 3, a plunger 1 magnetically attracted to the center boss 2 by conduction to the coil 3, a sleeve 4 serving as a bearing for the plunger 1, and a plunger 1. And a rod 7 connected to the plunger 1 for transmitting the drive of the motor to the spool 15.
  • It includes a packing 10 for preventing the magnetic field, an upper plate 11 for forming a magnetic path, and a bracket plate 12 for forming a magnetic path and fixing the solenoid valve body at a predetermined position.
  • the spring 14 includes a spring 14 that urges the coil 3 away from the connector 2, and a connector 17 that includes a terminal 17 a for energizing the coil 3.
  • the coil 3 bobbin 6 is molded into an Assy (assemb1y) by a mold, and constitutes a mono-red coil sub-Asy5.
  • the plunger 1 is configured to be located away from the center boss 2 in a normal state, that is, in a state where the coil 3 is not energized, that is, in the present embodiment, as described above, By biasing the spool 15 in the direction of the solenoid 100 A through the E-ring 18 by the spring 14, the plunger 1 is separated from the center post 2.
  • a magnetic path (a magnetic path formed by the case 9, the upper plate 11, the plunger 1, the center post 2, and the bracket plate 12) is formed. Is magnetically attracted to the center post 2.
  • the magnetic force can be controlled by the magnitude of the current flowing through the coil 3, whereby the amount of movement of the plunger 1 is controlled by controlling the amount of movement of the plunger 1 by controlling the balance with the biasing force of the spring 14.
  • the stroke amount of 5 can be controlled, whereby the flow rate of the fluid can be controlled, and various fluid pressure controls such as hydraulic control can be performed.
  • the members involved in the centering are There are five members: the lancer 1, rod 7, center post 2, sleeve 4, and rod bearing 13.Therefore, the burden of dimensional control is relatively small, and the coaxiality can be improved. .
  • the plunger 1 has a substantially cylindrical shape, and the rod 7 is fitted into the hole 1 b on the inner peripheral side, and is slidably supported by the sleep 4 on the outer peripheral side as described above, so that it becomes a sliding portion.
  • a large diameter portion 1a is provided.
  • the large-diameter portion 1a is provided with a plurality of convex portions 1d and a plurality of groove portions 1e alternately, and has a cross-sectional shape like a petal. It has become.
  • the convex portion 1 d extends in the axial direction, and the distance from the tip (the farthest position from the axis) of each convex portion 1 d to the axis is set to be equal.
  • the convex portion 1d has a smooth curved shape, and the radius of curvature of the outer peripheral curved surface in a cross section perpendicular to the axis is set to be smaller than the distance from the tip of the convex portion 1d to the axis. I have. As a result, the distance from the tip of the convex portion 1d to the axis becomes smaller by the clearance than the inner peripheral diameter of the sleeve 4, so that the radius of curvature of the outer peripheral curved surface is naturally larger than the inner peripheral diameter of the sleeve 4. Become smaller.
  • the distance from the tip of the convex portion 1d to the axis is 5 mm, and the radius of curvature near the tip of the convex portion 1d is 3 mm.
  • the radius of the inner circumference of the sleeve 4 is 5 mm and is equal to the clearance. The diameter becomes larger.
  • the tip of the convex portion 1 d is disposed so as to be slidable on the inner peripheral surface of the sleeve 4.
  • a groove 1 e extending in the axial direction is provided between each adjacent convex surface 1 d, and a flow path is formed between the groove 1 e and the inner peripheral surface of the sleep 4.
  • the plunger 1 when the plunger 1 slides on the inner periphery of the sleeve 4, the sliding is performed smoothly as described in the above-described related art. Since the clearance is provided in the plunger, the plunger 1 does not reciprocate while keeping the axis completely coaxial with the sleeve 4.
  • the radius of curvature (outer diameter) of the sliding surface is not substantially the same as the radius of curvature (inner diameter) of the inner peripheral surface of the sleeve.
  • the load is dispersed and the load on the sliding portion is reduced as compared with the case where one point contact is made in a cross section perpendicular to the axis as in the prior art, so that the sliding wear property is improved.
  • the gap near the sliding portion is larger than that of the conventional technology. Even if) has entered, foreign matter can easily escape into the flow path, so that a decrease in slidability due to the foreign matter can be prevented.
  • the above-mentioned convex portion 1d is preferably oriented in the circumferential direction, and is preferably provided in an odd number.
  • the plunger 1 slides while contacting the two points by the adjacent convex portions 1 d, so that the outer peripheral surface on the opposite side with respect to the axis of the groove portion 1 e located at an intermediate position between the two points. Since this is the most distant from the inner circumference of the sleeve, making this portion a convex portion Id has the effect of minimizing the gap and suppressing rattling.
  • the groove 1e is a curved surface that smoothly connects the convex surface 1d and the curved surface, and has a radius of curvature R2 equivalent to the radius of curvature R1 of the convex surface 1d.
  • a triangular groove 1 h as shown in (B) may be used.
  • the cross section perpendicular to the axis of the flow path formed between the groove 1 e and the inner periphery of the sleep 4 should be dimensioned so that impurities contained in the fluid flowing through the flow path will not be caught and caught. desirable.
  • the fluid flows into the solenoid pulp 100.
  • the impurities contained in the fluid are smaller than those of the filter.
  • the dimension of the cross section perpendicular to the axis of the flow channel to include the size of the mesh of the filter, the inside of the channel formed by the groove 1 e and the inner periphery of the sleeve 4 is formed. It can be prevented that impurities are caught and clogged.
  • the control of the pulp timing can be performed by shifting the cam shaft in the rotation direction and changing the phase, and a technique of performing this using a solenoid valve is known as a known technique.
  • a function such as a force S for performing hydraulic control by a solenoid valve and an arrangement space are required.
  • a solenoid valve is installed on the path of the engine oil flow path to use the engine oil.
  • the above-described solenoid valve according to the embodiment of the present invention can be suitably used as such a linear control solenoid valve for valve timing control (VTC).
  • VTC valve timing control
  • the plurality of convex portions 1 d and the plurality of grooves 1 e of the large-diameter portion 1 a of the plunger 1 are clamped by forging dies 50 and 51, and are pressed in the direction of arrow P in the figure to form a forging. It can be made by molding.
  • the forging die 51 is shown by a dotted line in the figure for explanation of the subsequent manufacturing process.
  • 1f in the figure is the cutting part that is cut by the cutting process after forging.
  • the forging die 51 is removed to remove the plunger 1 body from the mold. It is necessary to press (hit) the opposite end face in the direction of arrow Q with the ejector pin 52.
  • a concave portion 1c recessed inward from the tip surface is provided on the end surface opposite to the arrow P direction, and the bottom surface of the concave portion 1c is pressed by the ejector pin 52. It is a pressed part.
  • burrs when pressed by the ejector pins 52, burrs generally occur.
  • the bottom surface of the concave portion 1c is the pressed portion, (P) in FIG.
  • the burrs B 1 and B 2 occur only in the concave portion, and do not affect the entire length of the plunger 1.
  • a solenoid valve according to a second embodiment of the present invention will be described with reference to FIG.
  • the solenoid valve according to the second embodiment of the present invention only the configuration of the plunger is different from that of the first embodiment, so only the plunger will be described in detail, and the description of the other components will be omitted. .
  • FIG. 5 is a schematic configuration sectional view of a plunger according to a second embodiment of the present invention cut in a direction perpendicular to an axis.
  • the cross-sectional view taken along the axis of the plunger according to the present embodiment is the same as that of the above embodiment. This is the same as FIG. 2 (A) shown in the embodiment. Therefore, FIG. 5 is a view corresponding to the BB section in FIG. 2 (A).
  • the large-diameter portion 1′a serving as a sliding portion with respect to the sleeve 4 of the plunger according to the present embodiment has a polygonal cross section perpendicular to the axial direction as shown in FIG. In the example, it is approximately a regular octagon.
  • the distance from the axis to the corner 1′d is set to be smaller than the inner diameter of the sleeve 4 by the clearance. Therefore, the corner 1 ′ d is disposed so as to be slidable on the inner peripheral surface of the sleeve 4.
  • the plunger By configuring the plunger as described above, it is very unstable to slide at only one point in the cross section perpendicular to the axis, as in the case of the first embodiment. In reality, this is not the case, and the adjacent corners 1'd slide with two points of contact.
  • the load is dispersed and the load on the sliding portion is reduced as compared with the case where one point contact is made in a cross section perpendicular to the axis as in the prior art, so that the sliding wear property is improved.
  • the corner 1 ′ d slides on the inner peripheral wall surface of the sleeve 4, the corner 1 ′ d is formed between the flat surface 1 ′ e and the inner peripheral surface of the sleeve 4. Since the fluid easily flows into the sliding part from the flow path, the lubricating property is more excellent than that of the conventional technology, so that the sliding property is improved.
  • the corner 1′d slides on the inner peripheral wall surface of the sleeve 4. Therefore, the gap near the sliding part is larger than that of the conventional technology. Therefore, even if foreign matter enters the vicinity of the sliding part, the foreign matter easily escapes to the flow path. Can be prevented.
  • the cross section is a substantially regular polygon and an odd-numbered polygon (in the illustrated example, a substantially regular octagon), so that the corner 1 ′ d and the plane 1 ′ e However, they are arranged in a symmetrical positional relationship with respect to the axis.
  • the plunger 1 slides while being in two contact points by the adjacent corners 1′d, so that the plunger 1 is on the opposite side of the axis of the plane part 1′e which is an intermediate position between these two points. Since the outer peripheral surface of the sleeve is most distant from the inner periphery of the sleeve, making this part a corner 1'd has the effect of minimizing the gap and suppressing rattling.
  • the corners 1 and d have an R shape, and if the R is too small, the wear will increase. Therefore, it is necessary to set the R to an appropriate value.
  • the flow path formed between the peripheral surface and the peripheral surface will be described in detail.
  • the lubrication of the fluid (oil) is sufficient, and the larger the cross-sectional area of the flow path, the better, so that the oil does not stick. It is also desirable that the dimensions be such that impurities contained in the fluid flowing through the flow channel are not caught.
  • the dimension and shape of the flow path are determined mainly by the regular square and the R dimension of the corner.
  • the plunger can be formed by cutting.
  • cutting it is necessary to perform chucking in order to fix the plunger.
  • the flat part 1'e is used to prevent the corner 1'd serving as the sliding part from being scratched.
  • the chuck is a three-point chuck (third in the direction of 120 °) Force S Since it is suitable for machining with high accuracy, to fix the flat part 1'e with a three-point chuck,
  • the outer shape of a simple section must be a multiple of 3 (regular polygon).
  • the outer peripheral shape of the cross section perpendicular to the axis of the plunger is The shape should be a regular polygon and an odd-numbered polygon from the viewpoint of preventing rattling, the size of the cross-sectional area of the flow path should be appropriate from the viewpoint of magnetic flux supply and lubricity, and the shape should be regular from the viewpoint of cutting. It is necessary to consider that it is a square and a multiple of three.
  • the setting range of R at corner 1'd is necessarily determined by the above conditions, but if R is too small, wear will increase. It is desirable to set to.
  • the plunger slides on the inner peripheral surface of the sleeve at two points in a cross section perpendicular to the axis.
  • the load on the sliding portion is reduced, the sliding wear property is improved, and the control characteristics are improved.
  • the inner circumference of the sleeve also slides on a small curved surface, the gap near the sliding portion can be made relatively large, and fluid can easily enter, so that lubricity is improved, and Even when foreign matter enters, the foreign matter can escape into the flow path, so that the sliding property is improved and the control characteristics are improved.
  • the convex portions are provided in the same orientation with respect to the circumferential direction and are provided in an odd number, rattling can be suppressed.
  • the cross-section perpendicular to the axial direction of the flow path formed by the groove and the inner peripheral wall is set to the size and shape including the size and shape of the filter that removes impurities contained in the fluid, impurities will There is no pinching, and stable slidability can be maintained.
  • a concave recess is provided inside, and this bottom face is pressed against the ejector pin to remove the plunger body from the forging die after forging. If the pressing portion is used, even if a paris is generated by the ezieta pin, the overall length of the plunger is not affected, and stable control can be performed without requiring a cutting process.
  • the plunger slides against the inner peripheral surface of the sleeve at two points in the cross section perpendicular to the axis.
  • the load on the moving part is reduced, sliding wear is improved, and control characteristics are improved.
  • sliding at the corners makes it possible to make the gap near the sliding part relatively large, facilitates fluid entry, improves lubricity, and ensures that even if foreign matter enters, In addition, since foreign substances can escape into the flow path, the slidability is improved, and the control characteristics are improved.
  • the corners and the plane part have a symmetrical positional relationship with respect to the axis center, which can reduce rattling and set the cross-sectional area of the flow passage to an appropriate size. And a three-point check can be performed when cutting.
  • the cross-section perpendicular to the axial direction of the flow path formed by the flat surface portion of the outer periphery of the plunger and the inner peripheral wall surface of the sleeve is set to the size and shape including the size and shape of the filter for removing impurities contained in the fluid, No impurities are trapped in the flow path, and stable slidability can be maintained.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une vanne électromagnétique, destinée à différents types de commandes à pression hydraulique, apte à augmenter l'aptitude au glissement d'un plongeur et présentant d'excellentes caractéristiques de régulation. Selon l'invention, le plongeur (1) est en règle générale de forme cylindrique, une partie à diamètre augmenté (1a), constituant une section de glissement, se trouve sur la périphérie extérieure du plongeur pour soutenir le plongeur de manière coulissante sur un manchon, une pluralité de parties de surface projetée (1d) et une pluralité de parties en creux (1e) sont disposées alternativement sur la partie à diamètre augmenté (1a), dont la section transversale est de forme pétaloïde.
PCT/JP2001/007282 2000-08-28 2001-08-24 Vanne electromagnetique WO2002018828A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU2001280160A AU2001280160A1 (en) 2000-08-28 2001-08-24 Solenoid valve
DE10196576T DE10196576B4 (de) 2000-08-28 2001-08-24 Solenoidventil
JP2002523515A JP4210775B2 (ja) 2000-08-28 2001-08-24 ソレノイドバルブ
US10/362,372 US6971627B2 (en) 2000-08-28 2001-08-24 Solenoid valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000257804 2000-08-28
JP2000-257804 2000-08-28

Publications (1)

Publication Number Publication Date
WO2002018828A1 true WO2002018828A1 (fr) 2002-03-07

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PCT/JP2001/007282 WO2002018828A1 (fr) 2000-08-28 2001-08-24 Vanne electromagnetique

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JP (1) JP4210775B2 (fr)
AU (1) AU2001280160A1 (fr)
DE (1) DE10196576B4 (fr)
WO (1) WO2002018828A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005050000A1 (fr) * 2003-11-11 2005-06-02 Robert Bosch Gmbh Soupape de commande d'un fluide
JP2008202701A (ja) * 2007-02-20 2008-09-04 Inax Corp 湯水混合弁
WO2011036731A1 (fr) * 2009-09-28 2011-03-31 三菱電機株式会社 Electrovanne de commande de pression hydraulique
WO2022097515A1 (fr) * 2020-11-05 2022-05-12 イーグル工業株式会社 Distributeur à tiroir cylindrique

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DE102004028871A1 (de) * 2004-06-15 2006-01-05 Hydac Electronic Gmbh Betätigungsvorrichtung, insbesondere zum Betätigen von Ventilen
DE102009043320B4 (de) * 2009-09-28 2012-01-12 Hydraulik-Ring Gmbh Elektrohydraulisches Ventil
DE102015102066A1 (de) 2015-02-13 2016-08-18 Hilite Germany Gmbh Zentralaktuator für einen Schwenkmotorversteller einer Nockenwelle
DE102017119001A1 (de) * 2017-08-21 2019-02-21 Kendrion (Villingen) Gmbh Elektromagnetische Stellvorrichtung
JP2019110747A (ja) * 2017-12-18 2019-07-04 フスコ オートモーティブ ホールディングス エル・エル・シーＨＵＳＣＯ Ａｕｔｏｍｏｔｉｖｅ Ｈｏｌｄｉｎｇｓ ＬＬＣ 電磁アクチュエータのためのラッチ防止制振シム

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JPH06137453A (ja) * 1992-10-23 1994-05-17 Honda Motor Co Ltd 電磁ニードルバルブ
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JP2000046227A (ja) * 1998-07-31 2000-02-18 Aisin Seiki Co Ltd 電磁弁装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005050000A1 (fr) * 2003-11-11 2005-06-02 Robert Bosch Gmbh Soupape de commande d'un fluide
JP2008202701A (ja) * 2007-02-20 2008-09-04 Inax Corp 湯水混合弁
WO2011036731A1 (fr) * 2009-09-28 2011-03-31 三菱電機株式会社 Electrovanne de commande de pression hydraulique
JPWO2011036731A1 (ja) * 2009-09-28 2013-02-14 三菱電機株式会社 油圧制御電磁弁
WO2022097515A1 (fr) * 2020-11-05 2022-05-12 イーグル工業株式会社 Distributeur à tiroir cylindrique

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