WO2020137268A1 - Amortisseur à force d'amortissement réglable et solénoïde - Google Patents

Amortisseur à force d'amortissement réglable et solénoïde Download PDF

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Publication number
WO2020137268A1
WO2020137268A1 PCT/JP2019/045354 JP2019045354W WO2020137268A1 WO 2020137268 A1 WO2020137268 A1 WO 2020137268A1 JP 2019045354 W JP2019045354 W JP 2019045354W WO 2020137268 A1 WO2020137268 A1 WO 2020137268A1
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WIPO (PCT)
Prior art keywords
damping force
solenoid
brazing
fixed iron
magnetic
Prior art date
Application number
PCT/JP2019/045354
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English (en)
Japanese (ja)
Inventor
ミルトン ムジィヴィジィワ
浩一 山香
Original Assignee
日立オートモティブシステムズ株式会社
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.)
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=71126479&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2020137268(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2020562926A priority Critical patent/JP7217756B2/ja
Publication of WO2020137268A1 publication Critical patent/WO2020137268A1/fr
Priority to JP2023008556A priority patent/JP2023053967A/ja

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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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • 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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures

Definitions

  • the present invention relates to a damping force adjusting shock absorber and a solenoid that dampen vibration of a vehicle, for example.
  • a suspension system such as a semi-active suspension mounted on a vehicle is equipped with a damping force adjustment type shock absorber that variably adjusts the damping force according to the running conditions and behavior of the vehicle.
  • a damping force adjusting type shock absorber using a solenoid as an electromagnetic proportional actuator for variably adjusting the damping force is known.
  • Patent Document 1 as this type of solenoid, a coil that generates a magnetic force when energized, first and second fixed iron cores (stator cores) made of a magnetic material and arranged on the inner peripheral side of the coil, A non-magnetic member that connects the first and second fixed iron cores in the axial direction, and a movable iron core that is arranged on the inner peripheral side of the first and second fixed iron cores and the non-magnetic member and is movable in the axial direction ( Plunger) is included.
  • Patent Document 2 describes that a brazing means is used for joining a non-magnetic member between the first and second fixed iron cores.
  • the second fixed iron core and the non-magnetic member are joined by brazing, and then the inner peripheral surface thereof is cut to form a flat surface without steps. This improves the slidability of the movable iron core.
  • Patent Document 3 describes a configuration in which a thin portion that partially reduces the magnetic path cross-sectional area is provided between the first and second fixed iron cores. Thereby, the magnetic flux density passing through the movable iron core is increased between the first and second fixed iron cores, and the performance as the solenoid is improved.
  • a non-magnetic member is joined between the first and second fixed iron cores, and the non-magnetic member increases the magnetic flux density of the magnetic circuit with respect to the movable iron core.
  • mechanical processing for example, cutting of the inner peripheral surface
  • the magnetic characteristics change due to processing strain and the non-magnetic member is easily magnetized.
  • a thin portion for partially reducing the magnetic path cross-sectional area is provided between the first and second fixed iron cores, the thin portion reduces the mechanical strength of the entire fixed iron core, and There is a problem that the life is shortened.
  • the present invention has been made in view of the above-described problems of the conventional art, and an object of the present invention is to maintain the characteristics of a non-magnetic member and to provide a magnetic flux density to a movable iron core between the first and second fixed iron cores. It is an object of the present invention to provide a damping force adjustable shock absorber and a solenoid capable of maintaining a high value.
  • an embodiment of the present invention includes a cylinder in which a working fluid is sealed, a piston that is inserted into the cylinder and defines the inside of the cylinder into a rod side chamber and a bottom side chamber, and A piston rod that is connected to a piston and extends to the outside of the cylinder, a flow path in which the flow of the working fluid is generated by the movement of the piston rod, and a damping force adjustment valve that is provided in the flow path and whose opening/closing operation is adjusted by a solenoid.
  • a damping force adjusting type shock absorber wherein the solenoid includes a coil that generates a magnetic force when energized, first and second fixed iron cores provided on an inner peripheral side of the coil, and the first and second fixed iron cores.
  • a non-magnetic member provided between the first and second fixed cores and integrally fixed to the first and second fixed cores by brazing; the first and second fixed cores;
  • a non-magnetic member is provided with an inner peripheral side, a movable iron core provided so as to be movable in the axial direction, a shaft portion provided on the movable iron core, and first and second bushes supporting the shaft portion.
  • a valve body of the damping force adjusting valve is provided at an end portion of the shaft portion on the second fixed iron core side, and the non-magnetic member is larger than inner diameters of the first and second fixed iron cores. The inner diameter of is large or small.
  • a solenoid includes a coil that generates a magnetic force when energized, first and second fixed iron cores provided on the inner peripheral side of the coil, and the first and second fixed iron cores. And a non-magnetic member that is integrally fixed to the first and second fixed iron cores by brazing, and inner circumferential sides of the first and second fixed iron cores and the non-magnetic member. And a first and second bush for supporting the shaft portion, and a first and second bushes that support the shaft portion.
  • the inner diameter of the non-magnetic member is larger or smaller than the inner diameter of the fixed iron core.
  • a cylinder in which a working fluid is sealed, a piston inserted into the cylinder to define a rod-side chamber and a bottom-side chamber in the cylinder, and a piston connected to the piston are provided.
  • a piston rod extending to the outside of the cylinder, a flow passage in which the flow of the working fluid is generated by the movement of the piston rod, and a damping force adjustment valve provided in the flow passage and whose opening/closing operation is adjusted by a solenoid.
  • a non-magnetic member provided between the iron cores and integrally fixed to the first and second fixed iron cores by brazing, and inner circumferences of the first and second fixed iron cores and the non-magnetic member.
  • a movable core disposed on the side of the movable core, the movable core being provided so as to be movable in the axial direction, a shaft portion provided on the inner peripheral side of the movable core, and first and second bushes supporting the shaft portion,
  • a valve body of the damping force adjusting valve is provided at an end of the shaft portion on the side of the second fixed core, and an inner diameter portion that defines an inner diameter of the non-magnetic member is not machined after brazing. It is characterized by
  • the present invention it is possible to prevent the characteristics of the non-magnetic member from changing due to the influence of heat, etc., and maintain a high magnetic flux density between the first and second fixed iron cores through the movable iron core. be able to.
  • FIG. 1 is a vertical cross-sectional view showing a damping force adjusting hydraulic shock absorber provided with a solenoid according to an embodiment of the present invention. It is sectional drawing which expands and shows the damping force control valve and solenoid in FIG.
  • FIG. 3 is a cross-sectional view showing an enlarged solenoid with the damping force adjusting valve in FIG. 2 removed.
  • FIG. 4 is a cross-sectional view showing a state where the first and second stator cores and the non-magnetic ring of the solenoid in FIG. 3 are preassembled.
  • the damping force adjusting hydraulic shock absorber 1 (hereinafter referred to as the hydraulic shock absorber 1) is provided with a solenoid 33 described later.
  • the hydraulic shock absorber 1 includes an outer cylinder 2, an inner cylinder 4, a piston 5, a piston rod 8, a rod guide 9, a damping force adjusting device 17, and the like.
  • one side of the outer cylinder 2 and the inner cylinder 4 in the axial direction is referred to as a lower side, a lower side, or a lower end side
  • the other axial side is referred to as an upper side, an upper side, or an upper end side.
  • the bottomed cylindrical outer cylinder 2 forming the outer shell of the hydraulic shock absorber 1 is closed at the lower end by a bottom cap 3, and the upper end of the outer cylinder 2 is a caulking portion 2A bent inward in the radial direction. ..
  • a rod guide 9 and a seal member 10 are provided between the caulking portion 2A and the inner cylinder 4.
  • an opening 2B is formed concentrically with a connection port 12C of an intermediate cylinder 12 which will be described later, and a damping force adjusting device 17 which will be described later is attached so as to face the opening 2B.
  • the bottom cap 3 is provided with a mounting eye 3A which is mounted on the wheel side of the vehicle, for example.
  • an inner cylinder 4 is provided coaxially with the outer cylinder 2.
  • the lower end side of the inner cylinder 4 is fitted and attached to the bottom valve 13, and the upper end side thereof is fitted and attached to the rod guide 9.
  • a working liquid as a working fluid is enclosed in the inner cylinder 4.
  • the working liquid is not limited to an oil liquid or an oil, but may be water mixed with an additive, for example.
  • An annular reservoir chamber A is formed between the inner cylinder 4 and the outer cylinder 2, and a gas is enclosed in the reservoir chamber A together with the oil liquid.
  • This gas may be atmospheric pressure air, or may be compressed gas such as nitrogen gas.
  • an oil hole 4A is formed at a midway position in the length direction (axial direction) of the inner cylinder 4 so that the rod-side oil chamber B is always communicated with the annular oil chamber D in the radial direction.
  • the piston 5 is slidably inserted into the inner cylinder 4.
  • the piston 5 defines the inside of the inner cylinder 4 into a rod side chamber (rod side oil chamber B) and a bottom side chamber (bottom side oil chamber C).
  • the piston 5 is formed with a plurality of oil passages 5A and 5B that allow the rod-side oil chamber B and the bottom-side oil chamber C to communicate with each other, and are separated from each other in the circumferential direction.
  • the extension side disc valve 6 is provided on the lower end surface of the piston 5.
  • the disk valve 6 on the extension side opens when the pressure in the rod-side oil chamber B exceeds the relief setting pressure when the piston 5 slides upward in the extension stroke of the piston rod 8, and at this time.
  • the pressure is relieved to the bottom side oil chamber C side via each oil passage 5A.
  • This relief setting pressure is set to a pressure higher than the valve opening pressure when the damping force adjusting device 17 described later is set to hardware.
  • a compression-side check valve 7 is provided on the upper end surface of the piston 5, which opens when the piston 5 slides downward in the compression stroke of the piston rod 8 and closes at other times.
  • the check valve 7 allows the oil liquid in the bottom side oil chamber C to flow in the respective oil passages 5B toward the rod side oil chamber B, and prevents the oil liquid from flowing in the opposite direction.
  • the valve opening pressure of the check valve 7 is set to a pressure lower than the valve opening pressure when the damping force adjusting device 17 described later is set to software, and the check valve 7 does not substantially generate the damping force.
  • the fact that the damping force is not substantially generated is a force equal to or less than the friction of the piston 5 and the seal member 10, and does not affect the movement of the vehicle.
  • the piston rod 8 extends in the inner cylinder 4 in the axial direction (upward and downward).
  • the lower end side of the piston rod 8 is inserted into the inner cylinder 4 and fixed to the piston 5 with a nut 8A or the like. Further, the upper end side of the piston rod 8 projects so as to extend to the outside of the outer cylinder 2 and the inner cylinder 4 via the rod guide 9.
  • a stepped cylindrical rod guide 9 is provided on the upper end side of the inner cylinder 4.
  • the rod guide 9 positions the upper part of the inner cylinder 4 at the center of the outer cylinder 2, and guides the piston rod 8 axially slidably on the inner peripheral side thereof.
  • An annular seal member 10 is provided between the rod guide 9 and the caulked portion 2A of the outer cylinder 2.
  • the seal member 10 is formed by baking an elastic material such as rubber on an annular metal plate through which the piston rod 8 is inserted at the center. Seal.
  • the seal member 10 is formed with a lip seal 10A as a check valve extending on the lower surface side so as to come into contact with the rod guide 9.
  • the lip seal 10A is arranged between the oil sump chamber 11 and the reservoir chamber A, and prevents oil liquid or the like in the oil sump chamber 11 from flowing toward the reservoir chamber A side through the return passage 9A of the rod guide 9. Forgive and prevent the reverse flow.
  • an intermediate cylinder 12 made of a cylindrical body is arranged between the outer cylinder 2 and the inner cylinder 4, an intermediate cylinder 12 made of a cylindrical body is arranged.
  • the intermediate cylinder 12 is attached to, for example, the outer peripheral side of the inner cylinder 4 via upper and lower cylindrical seals 12A and 12B.
  • the intermediate cylinder 12 has an annular oil chamber D formed therein so as to surround the outer circumference of the inner cylinder 4 over the entire circumference, and the annular oil chamber D is an oil chamber independent of the reservoir chamber A.
  • the annular oil chamber D is always in communication with the rod-side oil chamber B by means of a radial oil hole 4A formed in the inner cylinder 4.
  • the annular oil chamber D serves as a flow path in which the flow of the working liquid is generated by the movement of the piston rod 8.
  • a connection port 12C to which a cylindrical holder 20 of a damping force adjusting valve 18 to be described later is attached is provided on the lower end side of the intermediate cylinder 12.
  • the bottom valve 13 is located on the lower end side of the inner cylinder 4 and is provided between the bottom cap 3 and the inner cylinder 4.
  • the bottom valve 13 includes a valve body 14 that defines a reservoir chamber A and a bottom oil chamber C between the bottom cap 3 and the inner cylinder 4, and a reduction-side disk valve provided on the lower surface side of the valve body 14. 15 and an extension side check valve 16 provided on the upper surface side of the valve body 14.
  • oil passages 14A and 14B that allow the reservoir chamber A and the bottom oil chamber C to communicate with each other are formed at intervals in the circumferential direction.
  • the reduction side disc valve 15 opens when the pressure in the bottom side oil chamber C exceeds the relief set pressure when the piston 5 slides downward in the reduction stroke of the piston rod 8, and the pressure at this time Is relieved to the reservoir chamber A side through each oil passage 14A.
  • This relief setting pressure is set to a pressure higher than the valve opening pressure when the damping force adjusting device 17 described later is set to hardware.
  • the extension side check valve 16 opens when the piston 5 slides upward in the extension stroke of the piston rod 8 and closes at other times.
  • the extension side check valve 16 allows the oil liquid in the reservoir chamber A to flow through the oil passages 14B toward the bottom oil chamber C, and prevents the oil liquid from flowing in the opposite direction.
  • the valve opening pressure of the extension side check valve 16 is set to a pressure lower than the valve opening pressure when the damping force adjusting device 17 described later is set to soft, and substantially no damping force is generated.
  • a damping force adjusting device 17 for variably adjusting the generated damping force of the hydraulic shock absorber 1 will be described with reference to FIG. 2 in addition to FIG.
  • the plunger 48 (actuating pin 49) of FIG. 2 is operated by externally energizing the coil 34A of the solenoid 33 (for example, control for generating a hard damping force).
  • the figure shows a state in which the pilot valve body 32 has moved to the left side (that is, the valve closing direction in which the pilot valve body 32 is seated on the valve seat portion 26E of the pilot body 26).
  • the damping force adjusting device 17 is arranged such that the base end side (the left end side in FIG. 1) is interposed between the reservoir chamber A and the annular oil chamber D, and the tip end side (FIG. 1). Is provided so as to project radially outward from the lower side of the outer cylinder 2.
  • the damping force adjusting device 17 includes a damping force adjusting valve 18 for generating a damping force having a hard or soft characteristic by variably controlling the flow of the oil liquid from the annular oil chamber D to the reservoir chamber A, and the damping force adjusting valve 18.
  • a solenoid 33 which will be described later, that adjusts the opening/closing operation of the valve 18 is included.
  • the valve opening pressure of the damping force adjusting valve 18 is adjusted by the solenoid 33 used as a damping force variable actuator, whereby the generated damping force is variably controlled to have a hard or soft characteristic.
  • the damping force adjusting valve 18 is a valve whose opening/closing operation is adjusted by a solenoid 33, and a flow path (for example, between the annular oil chamber D and the reservoir chamber A) in which the flow of the working fluid is generated by the movement of the piston rod 8. It is provided in.
  • the damping force adjusting valve 18 includes a valve case 19 having a substantially cylindrical shape, the base end side of which is fixed around the opening 2 ⁇ /b>B of the outer cylinder 2 and the front end side of which is provided so as to project radially outward from the outer cylinder 2.
  • a cylindrical holder 20 having a base end side fixed to the connection port 12C of the intermediate cylinder 12 and a distal end side serving as an annular flange portion 20A, which is arranged inside the valve case 19 with a gap, and the cylindrical holder 20. It is configured to include a valve member 21 that abuts the flange portion 20A.
  • the base end side of the valve case 19 is an annular inner flange portion 19A extending inward in the radial direction, and the tip end side of the valve case 19 is a connection for connecting the valve case 19 and a cover member 51 of the solenoid 33 described later. It is a male screw portion 19B to which the ring 52 is screwed.
  • An annular oil that constantly communicates with the reservoir chamber A between the inner peripheral surface of the valve case 19 and the outer peripheral surface of the valve member 21, and between the inner peripheral surface of the valve case 19 and the outer peripheral surface of the pilot body 26 and the like. It has become room 19C.
  • the inside of the cylindrical holder 20 has an oil passage 20B that communicates with the annular oil chamber D on one side and extends to the position of the valve member 21 on the other side.
  • An annular spacer 22 is sandwiched between the flange portion 20A of the tubular holder 20 and the inner flange portion 19A of the valve case 19.
  • the spacer 22 is provided with a plurality of notches 22A that radially extend to connect the oil chamber 19C and the reservoir chamber A and serve as an oil passage in the radial direction.
  • the spacer 22 is provided with the notch 22A for forming the oil passage.
  • the inner flange portion 19A of the valve case 19 may be provided with radial notches for forming the oil passage.
  • the valve member 21 is provided with a central hole 21A located at the center in the radial direction and extending in the axial direction. Further, the valve member 21 is provided with a plurality of oil passages 21B circumferentially spaced around the center hole 21A. Each of these oil passages 21B has a cylinder on one side (left side in FIGS. 1 and 2). It is in constant communication with the oil passage 20B of the shape holder 20. Further, on the other end (right side in FIGS. 1 and 2) of the valve member 21, an annular recess 21C formed so as to surround the other side opening of the oil passage 21B, and a radial outside of the annular recess 21C.
  • each oil passage 21B of the valve member 21 is provided between the oil passage 20B of the cylindrical holder 20 communicating with the annular oil chamber D and the oil chamber 19C of the valve case 19 communicating with the reservoir chamber A. It becomes a flow path through which the flow rate of the pressure oil according to the opening degree of 23 flows.
  • the main valve 23 is composed of a disc valve whose inner peripheral side is sandwiched between the valve member 21 and the large diameter portion 24A of the pilot pin 24.
  • the outer peripheral side of the main valve 23 is seated on the annular valve seat 21D of the valve member 21.
  • An elastic seal member 23A is fixed to the outer peripheral portion of the main valve 23 on the back side thereof by means such as baking.
  • the main valve 23 is opened by receiving pressure on the oil passage 21B side (the annular oil chamber D side) of the valve member 21 and separating from the annular valve seat 21D.
  • the oil passage 21B (annular oil chamber D side) of the valve member 21 communicates with the oil chamber 19C (reservoir chamber A side) via the main valve 23, and the pressure oil flow rate at this time is equal to that of the main valve 23. It is variably adjusted according to the opening.
  • the pilot pin 24 is formed in a stepped cylindrical shape, and an annular large diameter portion 24A is provided in the axially intermediate portion thereof.
  • the pilot pin 24 has a central hole 24B that extends in the axial direction on the inner peripheral side thereof, and a small diameter hole (orifice 24C) is formed at one end of the central hole 24B (end on the cylindrical holder 20 side). ..
  • One end side (the left end side in FIGS. 1 and 2) of the pilot pin 24 is press-fitted into the center hole 21A of the valve member 21, and the main valve 23 is sandwiched between the large diameter portion 24A and the valve member 21.
  • the other end side (the right end side in FIGS. 1 and 2) of the pilot pin 24 is fitted into the center hole 26C of the pilot body 26.
  • an oil passage 25 extending in the axial direction is formed between the center hole 26C of the pilot body 26 and the other end side of the pilot pin 24.
  • the oil passage 25 communicates with a back pressure chamber 27 formed between the main valve 23 and the pilot body 26.
  • a plurality of oil passages 25 extending in the axial direction are provided in the side surface on the other end side of the pilot pin 24 in the circumferential direction, and the other circumferential positions are press-fitted into the center hole 26C of the pilot body 26.
  • the pilot body 26 is formed as a substantially bottomed tubular body having a cylindrical portion 26A having a stepped hole formed inside and a bottom portion 26B closing the cylindrical portion 26A.
  • the bottom portion 26B of the pilot body 26 is provided with a center hole 26C into which the other end side of the pilot pin 24 is fitted.
  • a projecting tubular portion 26D that extends to the valve member 21 side (that is, the left side in FIGS. 1 and 2) is integrally provided over the entire periphery thereof.
  • the elastic sealing member 23A of the main valve 23 is liquid-tightly fitted to the inner peripheral surface of the protruding tubular portion 26D, whereby a back pressure chamber 27 is formed between the main valve 23 and the pilot body 26. ing.
  • the back pressure chamber 27 generates a pressure that presses the main valve 23 in a valve closing direction, that is, a direction in which the main valve 23 is seated on the annular valve seat 21D of the valve member 21.
  • the bottom 26B of the pilot body 26 is provided with a valve seat portion 26E located at the other end side (the right end side in FIGS. 1 and 2) on which a pilot valve body 32 described later is seated so as to surround the center hole 26C.
  • a return spring 28 for urging the pilot valve body 32 in a direction away from the valve seat portion 26E of the pilot body 26, and a solenoid 33 described later are in a non-energized state (pilot A disk valve 29 that constitutes a fail-safe valve when the valve body 32 is farthest from the valve seat portion 26E), a holding plate 30 in which an oil passage 30A is formed on the center side, and the like are provided.
  • a cap 31 is fitted and fixed to the open end of the cylindrical portion 26A of the pilot body 26 with the return spring 28, the disc valve 29, the holding plate 30 and the like being arranged inside the cylindrical portion 26A.
  • the cap 31 is formed with notches 31A at four positions spaced apart in the circumferential direction, for example. These notches 31A serve as flow paths for allowing the oil liquid flowing to the solenoid 33 side through the oil passage 30A of the holding plate 30 to flow in the oil chamber 19C (reservoir chamber A side) in the direction of arrow X shown in FIG. ing.
  • the pilot valve body 32 constitutes a pilot valve together with the pilot body 26.
  • the pilot valve body 32 is formed in a stepped cylindrical shape, and a tip end portion of the pilot body 26, which is seated on and off the valve seat portion 26E, is a tapered taper portion.
  • An operating pin 49 of a solenoid 33 which will be described later, is fixed in a fitted state inside the pilot valve body 32, and the valve opening pressure of the pilot valve body 32 is adjusted according to the energization of the solenoid 33. ing.
  • a flange portion 32A serving as a spring bearing is formed over the entire circumference.
  • the flange portion 32A abuts the disc valve 29 when the solenoid 33 is in the non-energized state (that is, when the pilot valve body 32 is displaced to the fully open position where it is farthest from the valve seat portion 26E), and the pilot valve body 32 is It is intended to prevent the valve from opening more than this.
  • the solenoid 33 is used in a damping force adjusting shock absorber for adjusting the opening/closing operation of the damping force adjusting valve 18. That is, the solenoid 33 used as the damping force variable actuator of the damping force adjusting device 17 includes the mold coil 34, the first stator core 36, the core lid 37, the second stator core 40, the non-magnetic ring 44, the plunger 48, and the operating pin. 49 and the cover member 51 and the like.
  • the mold coil 34 is formed into a substantially cylindrical shape by integrally covering (molding) a coil 34A wound around a coil bobbin with a resin member 34B such as a thermosetting resin.
  • a part of the molded coil 34 in the circumferential direction serves as a cable take-out portion (not shown) protruding outward in the axial direction or the radial direction, and an electric cable (not shown) is connected to the cable take-out portion.
  • the coil 34A serves as an electromagnet to generate a magnetic force by supplying power (energization) from the outside through a cable.
  • a seal groove 34C is formed all around the side surface (end surface in the axial direction) facing the cover member 51 (plate 51B) described later.
  • a seal member (for example, an O-ring 35) is mounted in the seal groove 34C.
  • the O-ring 35 liquid-tightly seals between the mold coil 34 and the cover member 51 (plate 51B). Accordingly, it is possible to prevent dust containing rainwater or muddy water from entering the first and second stator cores 36, 40 side between the cover member 51 and the mold coil 34.
  • the coil used in the present invention is not limited to the molded coil 34 including the coil 34A and the resin member 34B, and other coils may be used.
  • the coil may be wound around a coil bobbin made of an electrically insulating material, and the outer circumference of the coil may be covered with an overmold (not shown) in which a resin material is molded on the coil bobbin. ..
  • the first stator core 36 constitutes a first fixed iron core provided on the inner peripheral side of the molded coil 34 (coil 34A).
  • the first stator core 36 is formed of a magnetic material such as low carbon steel or carbon steel for machine structure (S10C) as a cylindrical body.
  • the first stator core 36 has a small-diameter cylindrical portion 36A for joining formed on one axial side thereof (left side in FIGS. 3 and 4), and a non-magnetic ring 44 described later is attached to the small-diameter cylindrical portion 36A. It joins by the attachment part 45.
  • the first stator core 36 is formed such that the inner diameter thereof is slightly larger than the outer diameter of a plunger 48, which will be described later, and the plunger 48 is movable in the first stator core 36 in the axial direction.
  • a bottomed cylindrical core lid 37 is provided on the other axial side of the first stator core 36 (right side in FIGS. 3 and 4).
  • the core lid 37 is formed of a magnetic material similar to that of the first stator core 36 into a cylindrical shape with a bottom, and closes the first stator core 36 from the other side in the axial direction (the left side in FIGS. 2 and 3).
  • a bottomed stepped hole 37A is formed inside the core lid 37, and the stepped hole 37A is provided with a first bush 38 for slidably supporting an operation pin 49 described later.
  • a seal groove 37B (see FIG. 3) is provided on the outer peripheral side of the core lid 37 between the inner periphery of the first stator core 36 and the entire periphery.
  • An O-ring 39 as a seal member is mounted in the seal groove 37B, and the O-ring 39 liquid-tightly seals between the first stator core 36 and the core lid 37.
  • the end surface of the bottom of the core lid 37 is arranged to face a plate 51B of a cover member 51 described later with a gap in the axial direction.
  • This axial gap has a function of preventing an axial force from being directly applied to the first stator core 36 from the plate 51B side of the cover member 51 via the core lid 37.
  • the core lid 37 does not necessarily have to be formed of a magnetic material, but may be formed of a rigid metal material, a ceramic material, or a fiber-reinforced resin material.
  • the second stator core 40 constitutes a second fixed iron core that is provided on the inner peripheral side of the molded coil 34 (coil 34A) so as to be separated from the first stator core 36 in the one axial direction.
  • the second stator core 40 is formed of a magnetic material such as low carbon steel and carbon steel for machine structural use (S10C) in a stepped tubular shape.
  • the second stator core 40 has a cylindrical tubular portion 40A whose inner circumferential side is a stepped hole 40F to be described later, and an annular ring extending radially outward from the outer circumferential surface on one axial side of the tubular portion 40A. It is formed as an integrated body including a portion 40B and a tubular fitting portion 40C that projects from the outer peripheral side of the annular portion 40B toward one side in the axial direction (the damping force adjusting valve 18 side).
  • the cylindrical portion 40A of the second stator core 40 is provided with a circular concave portion 40D on the other side surface that faces a plunger 48 described later in the axial direction.
  • the concave portion 40D is formed as a circular groove having a diameter slightly larger than that of the plunger 48 so that a later-described plunger 48 can be inserted and retracted by magnetic force inside the concave portion 40D.
  • a conical projection 40E is provided on the other side of the tubular portion 40A so as to surround the periphery (outer periphery) of the concave portion 40D.
  • the outer peripheral surface of the conical protrusion 40E is formed as a conical surface so that the magnetic characteristic between the cylindrical portion 40A of the second stator core 40 and the plunger 48 becomes linear (linear). .. That is, the conical protrusion 40E projects in a tubular shape from the outer peripheral side of the tubular portion 40A of the second stator core 40 toward the other side in the axial direction, and the outer peripheral surface thereof extends from one side in the axial direction to the other side (FIG. 3, FIG.
  • the conical surface is tapered so that the outer diameter gradually decreases from the left side to the right side of the concave portion 40D shown in FIG.
  • a stepped hole 40F is formed on the inner peripheral side of the tubular portion 40A as shown in FIGS. 3 and 4, and an operation pin 49 described later is slidably supported in the stepped hole 40F.
  • the second bush 41 is fitted and provided.
  • a seal groove 40G in which a seal member (for example, an O ring 42) is mounted is formed on the other side surface facing the mold coil 34. A liquid-tight seal is provided between the coil 34 and the annular portion 40B.
  • the cap 31 of the damping force adjusting valve 18 is fitted (internally fitted) on the inner peripheral side of the fitting portion 40C.
  • the valve case 19 of the damping force adjusting valve 18 is fitted (externally fitted) on the outer peripheral side of the fitting portion 40C.
  • a seal groove 40H is provided on the outer peripheral surface of the fitting portion 40C over the entire circumference.
  • An O-ring 43 serving as a seal member is mounted in the seal groove 40H, and the O-ring 43 causes liquid-tightness between the second stator core 40 (fitting portion 40C) and the valve case 19 of the damping force adjusting valve 18. It is sealed in.
  • the non-magnetic ring 44 is a non-magnetic member provided between the first and second stator cores 36 and 40 and provided on the inner peripheral side of the mold coil 34 (coil 34A).
  • the non-magnetic ring 44 is formed as a stepped cylindrical body from a non-magnetic material such as austenitic stainless steel.
  • the non-magnetic ring 44 is composed of an axially intermediate thick-walled cylinder portion 44A, and first and second fitting tubular portions 44B and 44C that axially project from both ends of the thick-walled tubular portion 44A. There is.
  • the outer diameter dimensions of the thick-walled tubular portion 44A and the fitting tubular portions 44B and 44C are equal.
  • the thick-walled cylindrical portion 44A is formed to have the smallest inner diameter D1
  • the first and second fitting cylindrical portions 44B and 44C have the thick-walled cylindrical portion 44A (dimension D1). It has a larger inner diameter.
  • the first and second fitting tubular portions 44B and 44C are formed of a non-magnetic material with a required wall thickness (radial thickness) so that the desired coaxiality can be secured together with the thick-walled tubular portion 44A. ..
  • the first fitting tubular portion 44B of the non-magnetic ring 44 is fitted to the small diameter tubular portion 36A of the first stator core 36 from the outside, and the brazing portion 45 joins the two.
  • the second fitting tubular portion 44C is fitted to the outer circumferential side of the tubular portion 40A of the second stator core 40 and the conical protrusion 40E, and the two are joined by the brazing portion 46.
  • the brazing parts 45 and 46 perform brazing treatment (treatment of pure copper brazing) at 1000° C. or higher, for example, by using brazing materials made of pure copper brazing, so that the non-magnetic ring 44 is formed into first and second non-magnetic rings. Are joined to the stator cores 36, 40 of. A quenching process is performed after the brazing process.
  • the brazing parts 45 and 46 have a thickness of, for example, about 25 to 51 ⁇ m, and join the non-magnetic ring 44 to the first and second stator cores 36 and 40.
  • the inner diameter of the non-magnetic ring 44 that is, the dimension D1 of the thick-walled tubular portion 44A
  • the inner diameter of the first stator core 36 and the inner diameter of the second stator core 40 that is, the dimension D1, as shown in FIG. , The radial dimension of the recess 40D).
  • the inner diameter of the nonmagnetic ring 44 (that is, the dimension D1 of the thick-walled cylinder portion 44A) is larger than the inner diameters of the first and second fixed iron cores (first and second stator cores 36 and 40). ..
  • the inner diameter of the non-magnetic ring 44 is larger than the inner diameters of the first and second fixed iron cores, but the inner diameter of the non-magnetic ring 44 is the same as that of the first and second fixed iron cores.
  • the diameter may be smaller than the inner diameter of the fixed iron core.
  • the inner diameter of the non-magnetic ring 44 is smaller or larger than the inner diameters of the first and second fixed iron cores.
  • the non-magnetic ring 44 is the first and second fixed iron cores. This means that the inside is not cut after brazing. (If not cut, the inner diameters of the non-magnetic ring 44 and the first and second fixed iron cores have tolerances, and all inner diameters are the same in mass-produced products. Can never be).
  • An annular gap 47 is formed on the outer peripheral side of the small-diameter cylindrical portion 36A of the first stator core 36 and between the first fitting cylindrical portion 44B of the non-magnetic ring 44.
  • the gap 47 is provided for pouring the brazing filler metal (pure copper braze) between the first stator core 36 (small diameter tubular portion 36A) and the non-magnetic ring 44 (first fitting tubular portion 44B) in a heated and molten state. It is an introduction route.
  • the gap 47 functions as a gap for absorbing the difference in thermal expansion between the first and second stator cores 36, 40 and the nonmagnetic ring 44.
  • the brazing material of the brazing portion 46 is also provided between the second stator core 40 (the tubular portion 40A, the outer peripheral surface of the conical protrusion 40E) and the non-magnetic ring 44 (the second fitting tubular portion 44C).
  • An introduction path for pouring (pure copper braze) in a heated and molten state is formed similarly to the gap 47.
  • the non-magnetic ring 44 heats the brazing filler metal (pure copper braze) in order to join the second fitting tubular portion 44C to the second stator core 40 (the tubular portion 40A, the outer peripheral side of the conical protrusion 40E).
  • an axial gap 47 is formed so as to extend over the entire circumference between the small diameter cylindrical portion 36A of the first stator core 36 and the first fitting cylindrical portion 44B of the non-magnetic ring 44.
  • the non-magnetic ring 44 is joined between the first and second stator cores 36 and 40 by the brazing portions 45 and 46, and the rapid cooling process after brazing causes a difference in material (material) between the two. Even if a thermal expansion difference occurs due to the above, the gap 47 can suppress the occurrence of strain based on the difference.
  • the non-magnetic ring 44 as a non-magnetic member is provided between the first and second stator cores 36, 40 (fixed iron cores) and is integrated with the first and second stator cores 36, 40 by brazing. Fixed to.
  • the plunger 48 as a movable iron core is arranged on the inner peripheral side of the first and second stator cores 36 and 40 (first and second fixed iron cores) and the non-magnetic ring 44 (non-magnetic member), and moves in the axial direction. It is possible. That is, the plunger 48 is arranged on the inner peripheral side of the first and second stator cores 36 and 40 and the non-magnetic ring 44, and the magnetic force generated in the coil 34A causes the first and second bushes 38 and 41 and the operating pin 49. Is provided so as to be movable in the axial direction.
  • the plunger 48 is fixedly provided on an operating pin 49 extending through the center side of the plunger 48 and moves together with the operating pin 49.
  • the operating pin 49 is axially slidably supported by the core lid 37 on the first stator core 36 side and the second stator core 40 via first and second bushes 38, 41.
  • the plunger 48 is formed in a substantially cylindrical shape from an iron-based magnetic material, like the first and second stator cores 36 and 40, and when the coil 34A generates a magnetic force, the second stator core 40 The thrust is generated in the direction of being attracted toward the inside of the concave portion 40D.
  • the plunger 48 is formed with a plurality of communication passages 48A that are spaced apart in the circumferential direction and extend in the axial direction (front and rear directions). In these communication passages 48A, while the plunger 48 is axially displaced together with the operation pin 49, the oil liquid in the first and second stator cores 36, 40 smoothly flows in each communication passage 48A, This is a flow passage for suppressing the generation of flow resistance to the plunger 48.
  • the operating pin 49 is a shaft portion that transmits the thrust of the plunger 48 to the pilot valve body 32 of the damping force adjusting valve 18, and is formed of a hollow rod.
  • a plunger 48 as a movable iron core is integrally fixed to the axially intermediate portion of the actuating pin 49 by means of press fitting or the like, whereby the plunger 48 and the actuating pin 49 are sub-assembled.
  • Both axial sides of the operating pin 49 are slidable between the core lid 37 on the first stator core 36 side and the second stator core 40 (cylindrical portion 40A) via the first and second bushes 38, 41. Supported by.
  • the one end side (left end in FIG. 2) of the operating pin 49 projects from the second stator core 40, and the pilot valve body 32 of the damping force adjusting valve 18 is fixed to the projecting end. Therefore, the pilot valve body 32 integrally moves in the axial direction together with the plunger 48 and the operating pin 49. In other words, the valve opening set pressure of the pilot valve body 32 becomes a pressure value corresponding to the thrust of the plunger 48 based on the energization of the coil 34A.
  • the plunger 48 is configured to open and close the pilot valve of the hydraulic shock absorber 1 (that is, the pilot valve body 32 with respect to the pilot body 26) by moving in the axial direction by the magnetic force from the coil 34A.
  • the back pressure chamber 50 is an oil chamber formed between the core lid 37 and the other end of the actuation pin 49 (the right end in FIG. 2).
  • the back pressure chamber 50 communicates with the center hole 24B side of the pilot pin 24 via a hollow rod (operating pin 49). Therefore, the same pressure as that of the pilot valve element 32, which is seated on the valve seat portion 26E of the pilot body 26, acts on the back pressure chamber 50.
  • the pressure receiving area for this pressure the area where the other end surface of the operating pin 49 receives pressure in the back pressure chamber 50 is closer to the pilot valve body 32 (one end side of the operating pin 49) between the valve seat portion 26E. It is smaller than the area that receives pressure.
  • the thrust force to be transmitted from the plunger 48 to the pilot valve body 32 of the damping force adjusting valve 18 via the actuating pin 49 can be reduced by the pressure receiving area difference between the two. That is, by forming the back pressure chamber 50 between the other end of the operating pin 49 and the core lid 37, the back pressure chamber 50 is transmitted from the plunger 48 to the pilot valve body 32 of the damping force adjusting valve 18 via the operating pin 49.
  • the thrust force (for example, the magnetic force that should be generated by the coil 34A of the mold coil 34) can be reduced, and the overall size and weight of the solenoid 33 can be reduced.
  • the cover member 51 is a magnetic cover that covers the outer circumference of the coil 34A.
  • the cover member 51 is formed as a yoke using a magnetic material (magnetic material), and forms a magnetic circuit (magnetic path) on the outer peripheral side of the mold coil 34 (coil 34A).
  • the cover member 51 is formed in a tubular shape with a bottom as a whole, and includes a cylindrical tubular case 51A and the other end side (the right end portion in FIGS. 2 and 3) of the tubular case 51A. It is generally configured by a closing plate 51B.
  • the cylindrical case 51A is provided with a notch (not shown) for exposing the cable extraction portion of the mold coil 34 described above from the cover member 51.
  • the plate 51 ⁇ /b>B of the cover member 51 is provided with a fitting recess 51 ⁇ /b>C into which the core lid 37 (the bottom side thereof) of the first stator core 36 is inserted or accommodated.
  • the first stator core 36 can exchange magnetic flux with the plate 51B of the cover member 51 by fitting the bottom side of the core lid 37 into the fitting recess 51C.
  • the inner peripheral surface of the cylindrical case 51A of the cover member 51 faces the outer peripheral surface of the molded coil 34 with a gap.
  • the gap is configured to prevent the radial force applied to the cover member 51 from being directly applied to the mold coil 34.
  • the outer peripheral surface of the annular portion 40B of the second stator core 40 is in contact with the inner peripheral surface of the tubular case 51A by, for example, light press-fitting, and the cover member 51 and the second stator core 40 (annular portion 40B). The magnetic flux can be exchanged between and.
  • the engaging protrusion that protrudes radially outwardly from the other portions. 51D is provided (over the entire circumference or at a plurality of locations spaced apart in the circumferential direction).
  • the engagement protrusion 51D is engaged with the coupling ring 52 screwed to the valve case 19 of the damping force adjusting valve 18.
  • the coupling ring 52 is formed in a substantially cylindrical shape, and inside thereof, a female screw portion 52A that is screwed into the male screw portion 19B of the valve case 19, and an outer diameter dimension of the engaging convex portion 51D of the cylindrical case 51A having an inner diameter dimension. And a flange-shaped engaging portion 52B extending inward in the radial direction so as to be smaller than the above.
  • the coupling ring 52 is configured such that the female screw portion 52A and the male screw portion 19B of the valve case 19 are screwed with each other in a state where the flange-shaped engaging portion 52B is brought into contact with the engaging convex portion 51D of the tubular case 51A. It is a connecting member that integrally connects the damping force adjusting valve 18 and the solenoid 33.
  • the solenoid 33 and the hydraulic shock absorber 1 according to the present embodiment have the above-described configurations, and their operation will be described next.
  • the hydraulic shock absorber 1 is mounted on a vehicle such as an automobile, for example, the protruding end (upper end) side of the piston rod 8 is mounted on the vehicle body side of the vehicle, and the mounting eye 3A side provided on the bottom cap 3 is mounted on the wheel side.
  • the solenoid 33 of the damping force adjusting device 17 is connected to a control device (controller) provided on the vehicle body side of the vehicle via a cable (not shown) of electric wiring or the like.
  • the controller variably controls the damping force generated by the hydraulic shock absorber 1 by changing the current value of the control signal for energizing the coil 34A of the solenoid 33 and adjusting the valve opening pressure of the pilot valve body 32. can do.
  • the magnetic force (magnetic flux) generated by the coil 34A of the solenoid 33 passes from the first stator core 36 to the movable iron core (plunger 48) side so as to avoid the non-magnetic ring 44, which is a non-magnetic member, and from the plunger 48 to the first magnetic field.
  • the second stator core 40 that is, the conical protrusion 40E, the tubular portion 40A, the annular portion 40B, and the fitting portion 40C), the tubular case 51A of the cover member 51, and the plate 51B, and the first stator core 40. Configure the magnetic circuit to return to 36.
  • the magnetic circuit in this case all of the contact portions (except for the transfer of the magnetic flux between the plunger 48 and the first stator core 36 and the plunger 48 and the second stator core 40 which face each other with a minute gap therebetween) That is, the magnetic flux can be transferred by the portion where the magnetic bodies are in surface contact with each other. Therefore, the magnetic circuit of the solenoid 33 can ensure high magnetic efficiency.
  • the 1st stator core 36 and the 2nd stator core 40 which comprise the main part of the solenoid 33 it is located in the inner peripheral side of the mold coil 34 (coil 34A), and is a nonmagnetic ring which is a nonmagnetic member. 44 are provided.
  • This non-magnetic ring 44 is brazed between the first and second fixed iron cores (first and second stator cores 36, 40) so as to increase the magnetic flux density of the magnetic circuit with respect to the movable iron core (plunger 48). It is joined by the portions 45 and 46.
  • non-magnetic member non-magnetic ring 44
  • the magnetic characteristics change due to the processing strain at this time, and the non-magnetic member is magnetized.
  • the non-magnetic member is magnetized.
  • a non-magnetic ring 44 made of a non-magnetic material such as austenitic stainless steel is provided in the axially intermediate thick-walled cylinder portion 44A and axially from both ends of the thick-walled cylindrical portion 44A.
  • the projecting first and second fitting cylinder portions 44B and 44C form a stepped cylindrical integral body.
  • the non-magnetic ring 44 has an inner diameter dimension D1 larger than the inner diameters of the first and second stator cores 36 and 40.
  • the non-magnetic ring 44 is joined to the first stator core 36 and the second stator core 40 by the brazing portions 45 and 46, and the inner diameter of the non-magnetic ring 44 (that is, the thick-walled tubular portion 44A).
  • the dimension D1) is formed to be larger than the inner diameter of the first stator core 36 and larger than the inner diameter of the second stator core 40 (that is, the radial dimension of the recess 40D).
  • a plunger 48 as a movable iron core is axially arranged on the inner peripheral side of the first and second stator cores 36 and 40 (first and second fixed iron cores) and the non-magnetic ring 44 (non-magnetic member). It can be movably arranged. That is, since the plunger 48 can be arranged inside the non-magnetic ring 44 with a gap, the non-magnetic ring 44 is machined (for example, the inner peripheral surface is cut by machining after being joined to the first and second stator cores 36, 40). ) Is not necessary, and the magnetic characteristics of the non-magnetic ring 44 do not change due to thermal influence or strain.
  • the non-magnetic ring 44 is a non-magnetic member made of austenitic stainless steel, and the non-magnetic ring 44 is joined between the first stator core 36 and the second stator core 40 by brazing parts 45 and 46.
  • pure copper brazing (brazing material) or the like is used for brazing. That is, the austenitic stainless steel is subjected to solution heat treatment, for example, heat treatment at 1000° C. or higher, so that the work-induced martensite is removed and the crystal structure can be restored to an ideal face-centered cubic structure as a non-magnetic material. it can.
  • the material when distortion occurs due to deep drawing or cutting of non-magnetic austenitic stainless steel parts, the material generates work-induced martensite, and some crystal structures are ideal surfaces for non-magnetic materials.
  • the body is transformed into a body-centered cubic structure instead of a body-centered cubic structure, and the nonmagnetic material is likely to be magnetized.
  • the work-induced martensite of austenitic stainless steel is removed by heat treatment at 1000° C. or higher, and the ideal face-centered cubic structure is restored again. This treatment is called solution heat treatment.
  • pure copper braze is selected as the brazing filler metal having a brazing temperature of 1000° C. or higher, and the brazing portions 45 and 46 perform a process that serves as both brazing and solution heat treatment.
  • the non-magnetic ring 44 joined between the second stator cores 36 and 40 can return the crystal structure to an ideal face-centered cubic structure as a non-magnetic material.
  • the brazing material may be other than pure copper brazing as long as the brazing temperature is 1000° C. or higher.
  • brass solder, nickel solder, gold solder, palladium solder, etc. may be used.
  • the magnetic circuit of the solenoid 33 is made of a magnetic material except for the magnetic flux passing between the plunger 48 and the first stator core 36 that face each other with a minute gap therebetween, and also between the plunger 48 and the second stator core 40. Since the magnetic flux can be delivered and received in a state where they are in surface contact with each other, the magnetic circuit of the solenoid 33 can ensure high magnetic efficiency.
  • first fitting tubular portion 44B of the non-magnetic ring 44 is fitted to the small diameter tubular portion 36A of the first stator core 36 from the outside, and the two are joined by the brazing portion 45.
  • the second fitting tubular portion 44C is fitted to the outer circumferential side of the tubular portion 40A of the second stator core 40 and the conical protrusion 40E, and both are joined by the brazing portion 46.
  • the brazing parts 45 and 46 are brazed at a temperature of, for example, 1000° C. or more by using brazing materials made of pure copper brazing material, so that the non-magnetic ring 44 is attached to the first and second stator cores 36 and 40.
  • a joining process is performed, and a brazing process is followed by a quenching process.
  • the first and second stator cores 36, 40 and the non-magnetic ring 44 are configured as described above, and the brazing portions 45, 46 are made of pure copper brazing material (brazing material).
  • brazing material pure copper brazing material
  • the three members of the first and second stator cores 36 and 40 and the non-magnetic ring 44 can be joined to each other in a shape satisfying the coaxiality. It is also possible to secure pressure resistance against pressure oil.
  • the solenoid 33 used in the semi-accelerator (damping force adjusting type shock absorber) for adjusting the opening/closing operation of the damping force adjusting valve 18 has a fixed iron core (first and second). Between the magnetic members (first and second stator cores 36, 40) as a means for providing a non-magnetic portion for the purpose of forming a magnetic path between the stator cores 36, 40) and the movable iron core (plunger 48). By joining the non-magnetic member (non-magnetic ring 44) with the brazing parts 45 and 46, it is possible to provide an optimal method for dealing with the high withstand voltage of the damping force adjusting valve 18.
  • the brazing temperature when joining the non-magnetic ring 44 between the first and second stator cores 36 and 40 serves as solution heat treatment and is generated by cutting. It is possible to remove the processing-induced martensite (body-centered cubic structure) and obtain a metallographic structure having an ideal face-centered cubic structure as magnetic characteristics. And, since the cutting process for the purpose of shape correction after brazing is not performed, the ideal metallographic structure as a non-magnetic material is maintained without causing the process-induced martensite, and the thermal deformation during the brazing process is prevented. The structure can be suppressed.
  • the non-magnetic ring 44 as the non-magnetic portion has an ideal metallographic structure, it is possible to obtain excellent magnetic characteristics, and it is possible to improve the thrust as the solenoid 33 and optimize the thrust waveform. Moreover, the number of steps in manufacturing and manufacturing the solenoid 33 is reduced, and workability and productivity can be improved.
  • the second stator core 40 is configured to include the cylindrical tubular portion 40A, the annular portion 40B, and the tubular fitting portion 40C projecting to one side in the axial direction is taken as an example. I explained it.
  • the present invention is not limited to this, and, for example, the second fixed iron core (that is, the second stator core) is configured by the cylindrical tubular portion 40A and the annular portion 40B, and the tubular portion protrudes to one side in the axial direction.
  • the fitting portion may be omitted and eliminated.
  • the cover member 51 is made of a magnetic material as the yoke has been described as an example.
  • the present invention is not limited to this, and the cover member may be formed of, for example, a non-magnetic material, and may be a coil open type solenoid without a yoke.
  • the solenoid 33 is configured as a proportional solenoid has been described as an example.
  • the present invention is not limited to this, and for example, an ON/OFF solenoid may be used.
  • a cylinder in which a working fluid is sealed a piston that is inserted into the cylinder and defines the inside of the cylinder into a rod side chamber and a bottom side chamber, and is connected to the piston.
  • a piston rod extending to the outside of the cylinder, a flow path in which the flow of the working fluid is generated by the movement of the piston rod, and a damping force adjusting valve which is provided in the flow path and whose opening/closing operation is adjusted by a solenoid.
  • the solenoid includes a coil that generates a magnetic force when energized, first and second fixed iron cores provided on an inner peripheral side of the coil, and the first and second A non-magnetic member provided between the fixed iron cores and integrally fixed to the first and second fixed iron cores by brazing, and the first and second fixed iron cores and the non-magnetic member.
  • the shaft portion is provided on the inner peripheral side and is provided with a movable iron core provided so as to be movable in the axial direction, a shaft portion provided on the movable iron core, and first and second bushes supporting the shaft portion.
  • a valve body of the damping force adjusting valve is provided at an end of the second fixed iron core side, and the inner diameter of the non-magnetic member is larger than the inner diameters of the first and second fixed iron cores. It is characterized by a diameter or a small diameter.
  • the non-magnetic member is a member made of austenitic stainless steel.
  • a damping force adjusting type shock absorber according to a third aspect of the present invention is the above-mentioned first or second aspect, wherein the non-magnetic member uses the brazing material having a brazing temperature of 1000 degrees or more. Attached.
  • the non-magnetic member is brazed using a brazing material made of pure copper brazing.
  • a solenoid includes a coil that generates a magnetic force when energized, a first and second fixed iron cores provided on the inner peripheral side of the coil, and a first and second fixed iron cores. And a non-magnetic member that is integrally fixed to the first and second fixed iron cores by brazing, and an inner peripheral side of the first and second fixed iron cores and the non-magnetic member. And a movable iron core provided so as to be movable in the axial direction, a shaft portion provided on the movable iron core, and first and second bushes supporting the shaft portion.
  • the inner diameter of the non-magnetic member is larger or smaller than the inner diameter of the iron core.
  • the nonmagnetic member in the fifth aspect, is a member made of austenitic stainless steel.
  • the non-magnetic member in the fifth or sixth aspect, is brazed using a brazing material having a brazing temperature of 1000 degrees or more.
  • the non-magnetic member in the seventh aspect, is brazed by using a brazing material made of pure copper braze.
  • a solenoid according to a ninth aspect of the present invention is the solenoid according to any one of the fifth to eighth aspects, wherein an inner diameter portion defining an inner diameter of the first and second fixed iron cores and an inner diameter of the non-magnetic member are defined.
  • the inner diameter portion is characterized by being not cut after brazing.
  • a tenth aspect of the present invention is a cylinder in which a working fluid is sealed, a piston inserted into the cylinder to define a rod side chamber and a bottom side chamber inside the cylinder, and the cylinder connected to the piston.
  • a damping rod including a piston rod extending to the outside, a flow passage in which the working fluid flows by the movement of the piston rod, and a damping force adjusting valve provided in the flow passage and whose opening/closing operation is adjusted by a solenoid.
  • a force adjustment type shock absorber wherein the solenoid includes a coil that generates a magnetic force when energized, first and second fixed iron cores provided on an inner peripheral side of the coil, and the first and second fixed iron cores.
  • a non-magnetic member that is integrally fixed to the first and second fixed iron cores by brazing, and inner circumferential sides of the first and second fixed iron cores and the non-magnetic member.
  • a first and a second bush for supporting the shaft portion, the shaft portion provided on an inner peripheral side of the movable iron core, and the first and second bushes.
  • the valve body of the damping force adjusting valve is provided at the end of the portion on the side of the second fixed core, and the inner diameter portion that defines the inner diameter of the non-magnetic member should not be machined after brazing. Is characterized by.
  • the present invention is not limited to the above-described embodiment, and various modifications are included.
  • the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the configurations described.
  • a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Magnetically Actuated Valves (AREA)
  • Electromagnets (AREA)

Abstract

Entre un premier noyau de stator et un second noyau de stator formant la partie principale du solénoïde, un anneau non magnétique est positionné du côté périphérie interne d'une bobine. L'anneau non magnétique est lié par brasage entre un premier et un second noyau de fer fixes (les premier et second noyaux de stator) de façon à augmenter la densité de flux magnétique du circuit magnétique dans un noyau de fer mobile (piston). Le diamètre interne de l'anneau non magnétique, qui est constitué d'un matériau non magnétique tel que de l'acier inoxydable austénitique, est supérieur ou inférieur au diamètre interne du premier et du second noyau de stator, et un espace axial est formé entre l'anneau non magnétique et le piston.
PCT/JP2019/045354 2018-12-25 2019-11-20 Amortisseur à force d'amortissement réglable et solénoïde WO2020137268A1 (fr)

Priority Applications (2)

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JP2020562926A JP7217756B2 (ja) 2018-12-25 2019-11-20 減衰力調整式緩衝器およびソレノイド
JP2023008556A JP2023053967A (ja) 2018-12-25 2023-01-24 減衰力調整式緩衝器およびソレノイド

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JP2018241220 2018-12-25
JP2018-241220 2018-12-25

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111895031A (zh) * 2020-07-28 2020-11-06 河海大学 具有隔热功能的磁流变液阻尼器
WO2022070879A1 (fr) * 2020-09-30 2022-04-07 日立Astemo株式会社 Solénoïde, mécanisme de réglage de force d'amortissement, et amortisseur de type à réglage de force d'amortissement
KR102483515B1 (ko) * 2021-08-25 2023-01-05 주식회사 유니크 전자제어 현가장치용 솔레노이드 밸브

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JP2009127692A (ja) * 2007-11-21 2009-06-11 Aisin Aw Co Ltd リニアソレノイド装置および電磁弁
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CN111895031A (zh) * 2020-07-28 2020-11-06 河海大学 具有隔热功能的磁流变液阻尼器
WO2022070879A1 (fr) * 2020-09-30 2022-04-07 日立Astemo株式会社 Solénoïde, mécanisme de réglage de force d'amortissement, et amortisseur de type à réglage de force d'amortissement
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KR102483515B1 (ko) * 2021-08-25 2023-01-05 주식회사 유니크 전자제어 현가장치용 솔레노이드 밸브

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