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
  • 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
  • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
• • 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
  • F16F9/34—Special valve constructions; Shape or construction of throttling passages
• • 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
  • F16F9/461—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 characterised by actuation means
• • 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
  • F16F9/465—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 using servo control, the servo pressure being created by the flow of damping fluid, e.g. controlling pressure in a chamber downstream of a pilot passage
• • 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
  • H01F7/081—Magnetic constructions
• • 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
• • 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
  • H01F7/1607—Armatures entering the winding
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
  • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
  • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
  • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
  • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
  • B60G17/016—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
  • B60G17/0165—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input to an external condition, e.g. rough road surface, side wind
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
  • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
  • B60G17/08—Characteristics of fluid dampers
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
  • B60G2202/20—Type of damper
  • B60G2202/24—Fluid damper
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
  • B60G2204/62—Adjustable continuously, e.g. during driving
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
  • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
  • B60G2206/40—Constructional features of dampers and/or springs
  • B60G2206/41—Dampers
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2500/00—Indexing codes relating to the regulated action or device
  • B60G2500/10—Damping action or damper
  • B60G2500/104—Damping action or damper continuous
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
  • B60G2600/18—Automatic control means
  • B60G2600/184—Semi-Active control means
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
  • B60G2800/16—Running
  • B60G2800/162—Reducing road induced vibrations
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
  • B60G2800/90—System Controller type
  • B60G2800/91—Suspension Control
  • B60G2800/916—Body Vibration Control
• • 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
  • F16F2222/00—Special physical effects, e.g. nature of damping effects
  • F16F2222/12—Fluid damping
• • 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
  • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
  • F16F2228/06—Stiffness
  • F16F2228/066—Variable stiffness
• • 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
  • F16F2230/00—Purpose; Design features
  • F16F2230/18—Control arrangements
• • 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
  • H01F7/081—Magnetic constructions
  • H01F2007/086—Structural details of the armature

Definitions

• the present disclosure relates to, for example, solenoids, damping force adjustment mechanisms, and damping force adjustable shock absorbers.
• a vehicle such as a four-wheeled vehicle is provided with a shock absorber (damper) between the body (sprung) side and each wheel (unsprung) side.
• a shock absorber for example, a damping force adjustable hydraulic shock absorber that variably adjusts the damping force according to driving conditions, vehicle behavior, and the like is known.
• a damping force adjustable hydraulic shock absorber constitutes a semi-active suspension of a vehicle.
• the damping force adjustable hydraulic shock absorber variably adjusts the generated damping force by, for example, adjusting the opening pressure of the damping force adjustment valve with a damping force variable actuator.
• a solenoid is used as the damping force variable actuator.
• Patent Literature 1 describes a solenoid in which a cutout portion that is uneven in the circumferential direction of the mover is provided by cutting the mover (movable iron core) diagonally. According to this solenoid, the mover is biased to any position in the circumferential direction, and non-uniform force is applied to the bearing in the circumferential direction. This is intended to suppress deflection and vibration of the mover.
• An object of one embodiment of the present invention is to provide a solenoid, a damping force adjustment mechanism, and a damping force adjustable shock absorber that can both ensure the thrust of the mover (movable iron core) and suppress vibration.
• One embodiment of the present invention is a solenoid, comprising a coil that generates a magnetic field when energized, and a movable iron core that is at least partly located on the inner peripheral side of the coil and is provided movably in the axial direction of the coil. , a fixed core facing the movable core in the axial direction, and a shaft portion displaceable integrally with the movable core, the movable core having a large diameter portion and a small diameter portion, the small diameter portion being the It is provided on the fixed core side.
• a solenoid for axially driving a movable iron core including at least a first magnetic resistance portion by magnetic action when a coil is energized, wherein the solenoid is attached to the movable iron core. bearings supporting both ends of the movable iron core; and a second magnetic resistance unit exerting an action of moving at least the movable iron core in a radial direction by the magnetic action, wherein the second magnetic resistance The portion is formed by notching one side in the axial direction of the movable iron core along the circumferential direction.
• one embodiment of the present invention is a damping force adjustable shock absorber
• the damping force adjustable shock absorber includes a cylinder in which a working fluid is sealed, and a rod inserted in the cylinder and extending in the cylinder.
• a piston defining a side chamber and a bottom side chamber; a piston rod connected to the piston on one side and extending to the outside of the cylinder on the other side; a damping force adjustment valve provided in the flow path and driven by a solenoid;
• the solenoid includes a coil that generates a magnetic field when energized; and a fixed core facing the movable core in the axial direction, the movable core having a large diameter portion and a small diameter portion, the small diameter portion being the fixed core provided on the side.
• one embodiment of the present invention is a damping force adjustment mechanism, comprising: a coil that generates a magnetic field when energized; A stator axially opposed to a mover, and a control valve controlled by axial movement of the mover, the mover having a large diameter portion and a small diameter portion, the small diameter portion being It is provided on the stator side.
• one embodiment of the present invention is a solenoid, comprising: a coil that generates a magnetic field when energized; An iron core, a fixed iron core facing the movable iron core in the axial direction, an axial portion displaced integrally with the movable iron core, and a magnetic member provided between the coil and the movable iron core in the radial direction, A radial gap between the movable core and the magnetic member is larger on the fixed core side than at other locations.
• FIG. 1 is a longitudinal sectional view showing a damping force adjustable shock absorber incorporating a solenoid and a damping force adjusting mechanism according to an embodiment
• FIG. 2 is an enlarged sectional view showing a damping force adjusting valve and a solenoid taken out from FIG. 1
• FIG. 2 is an enlarged cross-sectional view showing a solenoid taken out from FIG. 1
• FIG. FIG. 2 is an enlarged sectional view of (IV) in FIG. 1
• FIG. 5 is an enlarged cross-sectional view at the same position as in FIG. 4 showing a solenoid according to a first modified example
• FIG. 5 is an enlarged cross-sectional view at the same position as in FIG.
• FIG. 4 showing a solenoid according to a second modification
• 5 is an enlarged cross-sectional view at the same position as in FIG. 4 showing a solenoid according to a third modified example
• FIG. 11 is a vertical cross-sectional view showing a movable iron core (mover) according to fourth to sixth modified examples
• FIG. 11 is a vertical cross-sectional view and a bottom view showing movable cores (movable elements) according to seventh and eighth modified examples;
• a damping force adjustable hydraulic damper 1 (hereinafter referred to as damper 1) includes a damping force adjusting mechanism 17 having a solenoid 33 as a drive source. That is, a damper 1 as a damping force adjustable damper includes an outer cylinder 2 and an inner cylinder 4 as cylinders, a piston 5, a piston rod 8, a rod guide 9, and a damping force adjusting mechanism 17. It is configured.
• a shock absorber 1 which is a hydraulic shock absorber, has a cylindrical outer cylinder 2 with a bottom that forms an outer shell.
• the lower end side of the outer cylinder 2 is closed by a bottom cap 3 using welding means or the like.
• the upper end side of the outer cylinder 2 serves as a crimped portion 2A that is bent radially inward.
• a rod guide 9 and a seal member 10 are provided between the crimped portion 2A and the inner cylinder 4.
• an opening 2B is formed concentrically with the connection port 12C of the intermediate cylinder 12 on the lower side of the outer cylinder 2.
• a damping force adjusting mechanism 17 is attached to the lower side of the outer cylinder 2 so as to face the opening 2B.
• the bottom cap 3 is provided with a mounting eye 3A that is mounted on the wheel side of the vehicle, for example.
• An inner cylinder 4 is provided in the outer cylinder 2 coaxially with the outer cylinder 2 .
• the lower end side of the inner cylinder 4 is fitted and attached to the bottom valve 13 .
• the upper end side of the inner cylinder 4 is fitted and attached to the rod guide 9 .
• the outer cylinder 2 and the inner cylinder 4, which are cylinders, are filled with oil as hydraulic fluid (working fluid).
• the hydraulic fluid is not limited to liquid oil or oil, and may be, for example, water mixed with an additive.
• An annular reservoir chamber A is formed between the inner cylinder 4 and the outer cylinder 2 . Gas is enclosed in the reservoir chamber A together with oil. This gas may be air at atmospheric pressure, or a gas such as compressed nitrogen gas may be used. Reservoir chamber A compensates for the entry and exit of piston rod 8 .
• An oil hole 4A is formed in the inner cylinder 4 at a midway position in the length direction (axial direction) in the radial direction so that the rod-side oil chamber B is always in communication with the annular oil chamber D. As shown in FIG.
• the piston 5 is slidably provided within the inner cylinder 4 .
• the piston 5 is inserted in the inner cylinder 4, and the inner cylinder 4 is divided into two chambers, a rod-side oil chamber B (rod-side chamber) and a bottom-side oil chamber C (bottom-side chamber).
• the piston 5 is provided 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 spaced apart in the circumferential direction.
• the disk valve 6 on the extension side is provided on the lower end surface of the piston 5 .
• the extension-side disk valve 6 opens when the pressure in the rod-side oil chamber B exceeds the relief set pressure when the piston 5 slides upward in the extension stroke of the piston rod 8, and the pressure at this time is is relieved to the bottom side oil chamber C side through each oil passage 5A.
• the relief setting pressure is set to a pressure higher than the valve opening pressure when the damping force adjustment mechanism 17 is set to hard.
• a contraction side check valve 7 is provided on the upper end surface of the piston 5.
• the check valve 7 opens when the piston 5 slides downward in the contraction stroke of the piston rod 8, and closes otherwise.
• the check valve 7 allows the oil in the bottom side oil chamber C to flow through each oil passage 5B toward the rod side oil chamber B, and prevents the oil from flowing in the opposite direction.
• the valve opening pressure of the check valve 7 is set lower than the valve opening pressure when the damping force adjustment mechanism 17 is set soft, and substantially no damping force is generated. The fact that substantially no damping force is generated means that the force is 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 axially (upward and downward in FIG. 1) inside the inner cylinder 4 .
• a lower end side of the piston rod 8 is inserted into the inner cylinder 4 .
• the piston rod 8 is fixed to the piston 5 with a nut 8A or the like.
• the upper end side of the piston rod 8 protrudes outside the outer cylinder 2 and the inner cylinder 4 via a rod guide 9 . That is, the piston rod 8 is connected to the piston 5 at its lower side, and extends to the outside of the inner cylinder 4 and the outer cylinder 2 at its upper side, which is the other side.
• the lower end of the piston rod 8 may be further extended to protrude outward from the bottom portion (for example, the bottom cap 3) side to form a so-called double rod.
• 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 portion of the inner cylinder 4 at the center of the outer cylinder 2 and guides the piston rod 8 on the inner peripheral side thereof so as to be slidable in the axial direction.
• An annular seal member 10 is provided between the rod guide 9 and the caulked portion 2A of the outer cylinder 2. As shown in FIG.
• the seal member 10 is formed by, for example, baking an elastic material such as rubber on a metal circular ring plate having a hole through which the piston rod 8 is inserted. The seal member 10 seals with the piston rod 8 by sliding the inner circumference of the elastic material against the outer circumference of the piston rod 8 .
• the seal member 10 has 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 reservoir chamber 11 and the reservoir chamber A.
• the lip seal 10A allows the oil or the like in the oil reservoir chamber 11 to flow toward the reservoir chamber A side through the return passage 9A of the rod guide 9, and prevents the flow in the opposite direction.
• 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 tube 12 is attached, for example, to the outer peripheral side of the inner tube 4 via upper and lower cylindrical seals 12A and 12B.
• the intermediate cylinder 12 forms therein an annular oil chamber D extending so as to surround the outer circumference of the inner cylinder 4 over the entire circumference.
• the annular oil chamber D is an oil chamber independent of the reservoir chamber A.
• the annular oil chamber D always communicates with the rod-side oil chamber B through a radial oil hole 4A formed in the inner cylinder 4 .
• the annular oil chamber D constitutes a flow path through which the movement of the piston rod 8 causes the hydraulic fluid to flow.
• a connection port 12 ⁇ /b>C to which a connection pipe body 20 of the damping force adjustment valve 18 is attached is provided on the lower end side of the intermediate cylinder 12 .
• the bottom valve 13 is positioned on the lower end side of the inner cylinder 4 and provided between the bottom cap 3 and the inner cylinder 4 .
• the bottom valve 13 includes a valve body 14 that partitions (partitions) the reservoir chamber A and the bottom side oil chamber C between the bottom cap 3 and the inner cylinder 4, and a contraction side valve provided on the lower surface side of the valve body 14. It is composed of a disk valve 15 and an extension side check valve 16 provided on the upper surface side of the valve body 14 .
• the valve body 14 is formed with oil passages 14A and 14B that allow the reservoir chamber A and the bottom-side oil chamber C to communicate with each other in the circumferential direction.
• the contraction-side disk 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 contraction stroke of the piston rod 8, and the pressure at this time is is relieved to the reservoir chamber A side through each oil passage 14A.
• the relief setting pressure is set to a pressure higher than the valve opening pressure when the damping force adjustment mechanism 17 is set to hard.
• the extension side check valve 16 opens when the piston 5 slides upward during the extension stroke of the piston rod 8, and closes otherwise.
• the check valve 16 allows the oil in the reservoir chamber A to flow through the oil passages 14B toward the bottom side oil chamber C, and prevents the oil from flowing in the opposite direction.
• the valve opening pressure of the check valve 16 is set to a pressure lower than the valve opening pressure when the damping force adjustment mechanism 17 is set to soft, and substantially no damping force is generated.
• the damping force adjustment mechanism 17 is a mechanism that controls the flow of hydraulic fluid generated by sliding of the piston 5 in the cylinder (inner cylinder 4) to generate damping force and variably adjusts the damping force generated by the shock absorber 1.
• the armature 48 (operating pin 49) is controlled by externally energizing the coil 34A of the solenoid 33 (for example, controlling to generate a hard damping force). It shows a state in which the pilot valve element 32 has moved to the left (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 adjustment mechanism 17 is arranged so that its base end side (left end side in FIG. 1) is interposed between the reservoir chamber A and the annular oil chamber D, and its tip end side (left end side in FIG. 1) right end side) is provided so as to protrude radially outward from the lower side of the outer cylinder 2 .
• the damping force adjustment mechanism 17 generates damping force by controlling the flow of oil from the annular oil chamber D to the reservoir chamber A with the damping force adjustment valve 18 . Further, the generated damping force is variably adjusted by adjusting the valve opening pressure of the damping force adjustment valve 18 with a solenoid 33 that is used as a damping force variable actuator.
• the damping force adjustment mechanism 17 controls the flow of the working fluid (oil liquid) caused by the sliding of the piston 5 inside the inner cylinder 4 to generate damping force.
• the damping force adjustment mechanism 17 includes a damping force adjustment valve 18 and a solenoid 33 .
• the damping force adjustment valve 18 variably controls the flow of oil from the annular oil chamber D to the reservoir chamber A to generate damping force with hard or soft characteristics.
• the damping force adjustment valve 18 is driven by a solenoid 33 . That is, the damping force adjustment valve 18 is a valve whose opening and closing operation is adjusted by the solenoid 33. Movement (extension and contraction) of the piston rod 8 causes flow of the hydraulic fluid (for example, the annular oil chamber D and the reservoir chamber).
• a solenoid 33 adjusts the opening/closing operation of the damping force adjustment valve 18 . That is, the valve opening pressure of the damping force adjustment valve 18 is adjusted by a solenoid 33 used as a damping force variable actuator, whereby the generated damping force is variably controlled to hard or soft characteristics.
• the damping force adjusting valve 18 is provided with a substantially cylindrical valve case 19 having a proximal end fixed around the opening 2B of the outer cylinder 2 and a distal end protruding radially outward from the outer cylinder 2.
• a connection pipe 20 having a base end fixed to the connection port 12C of the intermediate cylinder 12 and an annular flange portion 20A at the tip end disposed inside the valve case 19 with a gap; and a valve member 21 that abuts on the flange portion 20A.
• the base end side of the valve case 19 forms an annular inner flange portion 19A extending radially inward.
• the distal end of the valve case 19 is a male threaded portion 19B into which a lock nut 53 that couples the valve case 19 and the yoke 39 (one side cylinder portion 39G) of the solenoid 33 is screwed.
• a lock nut 53 that couples the valve case 19 and the yoke 39 (one side cylinder portion 39G) of the solenoid 33 is screwed.
• an annular oil always communicates with the reservoir chamber A.
• the room is 19C.
• the valve case 19 and the solenoid 33 may be connected by the lock nut 53, or, for example, may be configured such that the tip end of the valve case is crimped to the yoke of the solenoid (configuration without using the lock nut).
• the inside of the connecting pipe body 20 forms 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 connecting pipe body 20 and the inner flange portion 19A of the valve case 19, an annular spacer 22 is sandwiched.
• the spacer 22 is provided with a plurality of radially extending cutouts 22A serving as radial oil passages for communicating the oil chamber 19C and the reservoir chamber A.
• the notch 22A for forming the oil passage is provided in the spacer 22.
• the inner flange portion 19A of the valve case 19 may be radially provided with cutouts (grooves) for forming oil passages.
• the valve member 21 is provided with a center hole 21A located in 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 spaced apart in the circumferential direction around the center hole 21A. One side (the left side in FIGS. 1 and 2) of each oil passage 21B always communicates with the oil passage 20B side of the connection pipe body 20 . 1 and 2), an annular recess 21C formed to surround the other side opening of the oil passage 21B, and and an annular valve seat 21D on which the main valve 23 is seated.
• each oil passage 21B of the valve member 21 is provided between the oil passage 20B of the connecting pipe body 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 pressurized oil flows according to the degree of opening of 23 .
• 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 and off the annular valve seat 21 ⁇ /b>D of the valve member 21 .
• An elastic seal member 23A is fixed to the outer periphery of the main valve 23 on the back side by means of baking or the like.
• the main valve 23 is opened by receiving pressure on the oil passage 21B side (annular oil chamber D side) of the valve member 21 and leaving the annular valve seat 21D.
• the oil passage 21B (on the side of the annular oil chamber D) of the valve member 21 communicates with the oil chamber 19C (on the side of the reservoir chamber A) via the main valve 23, and the amount of pressurized oil flowing in the arrow Y direction at this time is (Flow rate) is variably adjusted according to the opening degree of the main valve 23 .
• the pilot pin 24 is formed in a stepped cylindrical shape, and is provided with an annular large-diameter portion 24A in the axially intermediate portion.
• the pilot pin 24 has a center hole 24B extending axially on the inner peripheral side.
• a small-diameter hole (orifice 24C) is formed at one end of the central hole 24B (the end on the side of the connecting pipe body 20).
• 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. As shown in FIG.
• the other end side of the pilot pin 24 (the right end side in FIGS. 1 and 2) is fitted into the center hole 26C of the pilot body 26.
• an axially extending oil passage 25 is formed between the center hole 26 ⁇ /b>C of the pilot body 26 and the other end of the pilot pin 24 .
• This 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 circumferential direction on the side surface of the pilot pin 24 on the other end side, 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 cylindrical body with a bottom, and has a cylindrical portion 26A with a stepped hole formed inside, and a bottom portion 26B closing the cylindrical portion 26A.
• a 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.
• One end side (the left end side in FIGS. 1 and 2) of the bottom portion 26B of the pilot body 26 is integrally provided with a protruding cylindrical portion 26D located on the outer diameter side and protruding toward the valve member 21 over the entire circumference. .
• the elastic seal member 23A of the main valve 23 is fitted to the inner peripheral surface of the protruding cylindrical portion 26D in a liquid-tight manner, thereby forming a back pressure chamber 27 between the main valve 23 and the pilot body 26. ing.
• the back pressure chamber 27 generates a pressure (internal pressure, pilot pressure) that presses the main valve 23 in the closing direction, that is, the direction in which the main valve 23 is seated on the annular valve seat 21 ⁇ /b>D of the valve member 21 .
• a valve seat portion 26E on which the pilot valve body 32 is seated and disengaged is provided on the other end side (the right end side in FIGS. 1 and 2) of the bottom portion 26B of the pilot body 26 so as to surround the center hole 26C.
• a return spring 28 biases the pilot valve body 32 in a direction away from the valve seat portion 26E of the pilot body 26.
• 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 disk valve 29, the holding plate 30, etc. arranged inside the cylindrical portion 26A.
• Notches 31A are formed in the cap 31, for example, at four locations spaced apart in the circumferential direction. As indicated by an arrow X in FIG. 2, the notch 31A serves as a flow path for circulating the oil that has flowed to the solenoid 33 side through the oil passage 30A of the holding plate 30 to the oil chamber 19C (reservoir chamber A side). .
• the pilot valve body 32 constitutes a pilot valve (control valve) together with the pilot body 26 .
• the pilot valve body 32 is formed in a stepped cylindrical shape.
• a tip portion of the pilot valve body 32 that is, a tip portion that is seated on and off the valve seat portion 26E of the pilot body 26 has a tapered shape.
• An actuation pin 49 of the solenoid 33 is fitted and fixed 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 .
• the pilot valve (pilot body 26 and pilot valve element 32) as a control valve is controlled by the axial movement of the actuation pin 49 (that is, the armature 48) of the solenoid 33.
• a flange portion 32A serving as a spring support is formed along the entire periphery of the pilot valve body 32 on the base end side thereof.
• FIG. 3 attaches
• the solenoid 33 is incorporated in the damping force adjustment mechanism 17 as a damping force variable actuator of the damping force adjustment mechanism 17 . That is, the solenoid 33 is used in the damping force adjustment type shock absorber to adjust the opening/closing operation of the damping force adjustment valve 18 .
• the solenoid 33 includes a molded coil 34, a housing 36 as a magnetic member (accommodating member), a yoke 39, an anchor 41 as a fixed iron core (stator), a cylinder 44 as a joining member (non-magnetic ring), It has an armature 48 as a movable iron core (mover), an operating pin 49 as a shaft portion, and a cover member 51 .
• the molded coil 34 is formed in a substantially cylindrical shape by integrally covering (molding) a coil 34A around a coil bobbin 34B with a resin member 34C such as a thermosetting resin. .
• a portion of the molded coil 34 in the circumferential direction is provided with a cable extraction portion 34E projecting axially or radially outward, and a wire cable (not shown) is connected to the cable extraction portion 34E.
• a coil 34A of the molded coil 34 is annularly wound around the coil bobbin 34B, and becomes an electromagnet to generate a magnetic field (magnetic force) when power is supplied (energized) through a cable from the outside.
• a seal groove 34D is formed over the entire circumference on the side surface (one end surface in the axial direction) facing the yoke 39 (annular portion 39B).
• a seal member for example, an O-ring 35
• the O-ring 35 liquid-tightly seals between the molded coil 34 and the yoke 39 (annular portion 39B). As a result, it is possible to prevent dust including rainwater and muddy water from entering the cylindrical projection 39C side of the yoke 39 through the space between the yoke 39 and the molded coil 34 .
• the coil employed in this embodiment is not limited to the molded coil 34 comprising the coil 34A, the coil bobbin 34B and the resin member 34C, and other coils may be employed.
• a 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 from above (on the outer circumference side).
• the housing 36 constitutes a magnetic member (accommodating member) arranged and provided on the inner peripheral side of the molded coil 34 (that is, the inner periphery of the coil 34A).
• the housing 36 is made of a magnetic material (magnetic substance) such as low-carbon steel, carbon steel for machine structural use (S10C), or the like, and is formed as a cylindrical body with a lid.
• the housing 36 extends in the direction of the winding axis of the molded coil 34 (coil 34A) and has an opening at one end (left side in FIG. 2, bottom side in FIG. 3).
• a stepped lid portion 36B that closes the other end side (the right side in FIG. 2, the upper side in FIG. 3) of the portion 36A and the opening side (one side) of the storage cylinder portion 36A are arranged so that the outer circumference is reduced in diameter. 36 C of small diameter cylinder parts for joining formed.
• the inner circumference of the cylinder 44 is joined to the outer circumference of the small-diameter cylindrical portion 36C of the housing 36 by brazing.
• the cylindrical storage portion 36A of the housing 36 has an inner diameter slightly larger than the outer diameter of the armature 48, and the armature 48 is accommodated in the cylindrical storage portion 36A so as to be axially movable. That is, the housing 36 is open at one end in the axial direction and accommodates the armature 48 .
• the storage cylinder portion 36A of the housing 36 has a first end portion 36D, a second end portion 36E, and a third end portion 36F in order from the inner circumference of the open end (in order from the inner diameter side to the outer diameter side). ing.
• the first end portion 36D faces the anchor 41, more specifically, the outer peripheral convex portion 41C (reduced diameter portion 41C1) of the anchor 41.
• the first end portion 36 ⁇ /b>D constitutes a magnetic flux transfer portion for transferring magnetic flux to and from the armature 48 .
• the second end 36E is in contact with the other axial end 44A of the cylinder 44 .
• the second end portion 36 ⁇ /b>E constitutes a position fixing portion that aligns (positions) the housing 36 by coming into contact with the other end 44 ⁇ /b>A of the cylinder 44 .
• the third end portion 36F faces the other end 44A of the cylinder 44 with a gap, and this gap serves as a brazing material storage portion in which a brazing material (copper ring) serving as a sealing material is stored.
• the housing 36 and the cylinder 44 form a pressure vessel by press-fitting the housing 36 (the small-diameter cylindrical portion 36C) into the cylinder 44 and performing brazing.
• the lid portion 36B of the housing 36 is formed integrally with the storage cylinder portion 36A as a lidded cylinder that closes the storage cylinder portion 36A from the other side in the axial direction.
• the lid portion 36B has a stepped shape with an outer diameter smaller than that of the storage cylinder portion 36A.
• the housing 36 is formed with a bottomed stepped hole 37 positioned inside the lid portion 36B.
• the stepped hole 37 is composed of a bush mounting hole portion 37A and a small diameter hole portion 37B located on the inner side of the bush mounting hole portion 37A and having a small diameter.
• a first bush 38 as a bearing for slidably supporting the operating pin 49 is provided in the bush mounting hole portion 37A.
• the other side end surface of the lid portion 36B of the housing 36 faces the lid plate 51B of the cover member 51 with a gap in the axial direction.
• This axial clearance has a function of preventing an axial force from being directly applied to the housing 36 from the lid plate 51B side of the cover member 51 through the lid portion 36B.
• the lid portion 36B of the housing 36 does not necessarily need to be integrally formed of the same material (magnetic material) as the housing cylinder portion 36A.
• the lid portion 36B can be made of, for example, a rigid metal material, a ceramic material, or a fiber-reinforced resin material instead of a magnetic material. Note that the joint between the storage tube portion 36A and the lid portion 36B of the housing 36 is positioned in consideration of the exchange of magnetic flux.
• the yoke 39 is provided on one side in the moving direction of the armature 48 .
• the yoke 39 is a magnetic member that, together with the housing 36, forms a magnetic circuit (magnetic path) over the inner peripheral side and the outer peripheral side of the molded coil 34 (coil 34A).
• the yoke 39 is formed using a magnetic material (magnetic body) similarly to the housing 36, extends radially on one axial side (one side in the winding axial direction) of the molded coil 34 (coil 34A), and An annular portion 39B having a stepped fixing hole 39A on the peripheral side, and a cylinder protruding in a cylindrical shape from the inner peripheral side of the annular portion 39B toward the other side in the axial direction (coil 34A side) along the axial direction of the fixing hole 39A.
• 39C of shaped protrusions The tubular projection 39C constitutes a projection (tubular portion) for joining with the cylinder 44, and the cylinder 44 is inserted into the inner diameter side of the tubular projection 39C.
• the yoke 39 has a fixing hole 39A, and the inner peripheral surface of the fixing hole 39A faces part of the side surface portion 41D of the anchor 41.
• an inward flange portion 39D is provided in the fixing hole 39A so as to protrude radially inward along the entire circumference.
• An end surface (one end surface) of the cylinder 44 on one side in the axial direction is in contact with the side surface (side surface on the side of the coil 34A) of the inward flange portion 39D.
• the outer periphery of the cylinder 44 on one side in the axial direction is fitted to the inner periphery of the yoke 39, that is, the inner surface of the fixing hole 39A (in other words, the inner peripheral surface of the cylindrical protrusion 39C).
• the yoke 39 includes a cylindrical one-side cylindrical portion 39G extending from the outer peripheral side of the annular portion 39B toward one axial side (the damping force adjusting valve 18 side), and a cylindrical portion 39G extending from the outer peripheral side of the annular portion 39B toward the other axial side.
• the other-side cylindrical portion 39H formed so as to extend toward (the cover member 51 side) and surround the mold coil 34 from the outside in the radial direction; It is formed as an integrated body including a crimped portion 39J that holds 51C in a retaining state.
• a notch 39K is provided in the other side tubular portion 39H of the yoke 39 to expose the cable extraction portion 34E of the molded coil 34 to the outside of the other side tubular portion 39H.
• an engaging recess 39L having a semicircular cross section so as to open to the outer peripheral surface of the yoke 39 (over the entire circumference or in the circumferential direction). spaced apart).
• a lock nut 53 which is screwed onto the valve case 19 of the damping force adjusting valve 18, is engaged with the engaging recess 39L via a retainer ring 54 (see FIG. 2).
• a seal groove 39M is provided over the entire circumference of the outer peripheral surface of the one-side tubular portion 39G.
• An O-ring 40 (see FIG. 2) as a sealing member is mounted in the seal groove 39M. The O-ring 40 liquid-tightly seals the space between the yoke 39 (one side cylindrical portion 39G) and the valve case 19 of the damping force adjustment valve 18 .
• the anchor 41 is provided on one side in the moving direction of the armature 48 .
• the anchor 41 is arranged to face the armature 48 in the axial direction.
• the anchor 41 is a fixed iron core (stator) fixed in the fixing hole 39A of the yoke 39 by means of press fitting or the like.
• the anchor 41 is made of a magnetic material (magnetic substance) such as low-carbon steel, carbon steel for machine structural use (S10C), etc., and is shaped to fill the fixing hole 39A of the yoke 39 from the inside. .
• the anchor 41 is formed as a short cylindrical ring-shaped body having a central through hole 41A extending in the axial direction.
• One axial side surface of the anchor 41 (the surface axially facing the cap 31 of the damping force adjusting valve 18 shown in FIG. 2) is formed to be flat like one side surface of the annular portion 39B of the yoke 39. ing.
• a circular recessed portion 41B is provided so as to be coaxial with the storage cylinder portion 36A of the housing 36 .
• the concave portion 41B is formed as a circular groove slightly larger in diameter than the armature 48 so that the armature 48 can be inserted thereinto so as to be able to enter and exit by magnetic force.
• the other side of the anchor 41 is provided with a cylindrical outer peripheral projection 41C.
• the outer peripheral surface of the outer peripheral convex portion 41C on the opening side is formed as a conical surface so that the magnetic characteristics between the anchor 41 and the armature 48 are linear (straight) characteristics.
• the outer peripheral convex portion 41C which is also called a corner portion, protrudes in a cylindrical shape from the outer peripheral side of the anchor 41 toward the other side in the axial direction.
• the outer peripheral surface (the outer peripheral surface on the opening side) of the outer peripheral convex portion 41C is a tapered conical surface so that the outer diameter dimension gradually decreases toward the other side (the opening side) in the axial direction.
• the outer peripheral convex portion 41C of the anchor 41 is provided at a position facing the opening (more specifically, the first end portion 36D) of the housing 36 (the storage cylinder portion 36A), and is positioned to face the opening of the storage cylinder portion 36A. has a diameter-reduced portion 41C1 whose outer diameter is reduced as it approaches .
• a side surface portion 41D is formed along the outer periphery of the outer peripheral convex portion 41C and extends in a direction away from the opening of the storage cylinder portion 36A of the housing 36.
• An end portion of the side surface portion 41D remote from the opening forms an annular flange portion 41E that protrudes radially outward.
• the annular flange portion 41E is arranged at a position (that is, the end portion on the side opposite to the concave portion 41B) that is largely spaced apart in one axial direction from the open end of the storage cylinder portion 36A of the housing 36 .
• the annular flange portion 41E is fixed, for example, in the fixing hole 39A of the yoke 39 by using means such as press fitting.
• the annular flange portion 41E serves as a portion for fixing the anchor 41 (side surface portion 41D) to the fixing hole 39A of the yoke 39, and is also a portion where the flange portion 41E and the fixing hole 39A face each other in the radial direction.
• a side portion 41D (excluding the annular flange portion 41E) of the anchor 41 faces the inner peripheral surface of the cylinder 44 and the inner surface of the inward flange portion 39D of the yoke 39 with a gap (radial gap) therebetween.
• an outer peripheral convex portion 41C and a side portion 41D are formed integrally with a magnetic material.
• the anchor 41 is provided at a position facing the opening of the cylindrical storage portion 36A of the housing 36.
• the outer peripheral convex portion 41C protrudes toward the opening of the storage cylinder portion 36A of the housing 36.
• the side surface portion 41D extends from the outer periphery of the outer peripheral convex portion 41C in a direction away from the opening of the storage cylinder portion 36A of the housing 36.
• the side surface portion 41 ⁇ /b>D has a gap with respect to the inner peripheral surface of the cylinder 44 and the inner surface of the inward flange portion 39 ⁇ /b>D of the yoke 39 .
• a stepped through hole 41A formed on the center (inner circumference) side of the anchor 41 is fitted with a second bushing 43 as a bearing for slidably supporting the operating pin 49.
• the pilot body 26 of the damping force adjusting valve 18, the return spring 28, the disc valve 29, the holding plate 30, the cap 31, and the like are mounted on the inner peripheral side of the one side cylindrical portion 39G of the yoke 39. It is provided with an insert.
• the valve case 19 of the damping force adjusting valve 18 is fitted (outside fitted) on the outer peripheral side of the one-side tubular portion 39G.
• the cylinder 44 is provided between the yoke 39 and the anchor 41 in the radial direction. Also, the cylinder 44 is provided between the yoke 39 and the housing 36 in the axial and radial directions. That is, the cylinder 44 is positioned between the small-diameter cylindrical portion 36C of the housing 36 and the cylindrical protrusion 39C of the yoke 39, and is provided on the inner peripheral side of the molded coil 34 (coil 34A). joint member).
• the cylinder 44 is made of non-magnetic material. More specifically, the cylinder 44 is made of a non-magnetic material such as austenitic stainless steel as a cylindrical body (simple cylindrical body).
• the outer periphery of the cylinder 44 on one end side (yoke 39 side) in the winding axis direction of the molded coil 34 (coil 34A) is joined to the inner periphery of the yoke 39 (fixing hole 39A, cylindrical protrusion 39C).
• one side of the cylinder 44 in the axial direction is fixed to the yoke 39 serving as a stator.
• the inner periphery of the cylinder 44 on the other end side (housing 36 side) of the molded coil 34 (coil 34A) in the winding axis direction is joined to the outer periphery of the housing 36 (small diameter tubular portion 36C). That is, the cylinder 44 is fitted (press-fitted) to the outside (peripheral side) of the small-diameter cylindrical portion 36C of the housing 36, and both are joined by brazing.
• the housing 36 and the cylinder 44, and the cylinder 44 and the yoke 39 are joined via brazing material.
• Pure copper brazing material for example, can be used as the brazing material. That is, the brazing can be performed by using a brazing material (copper ring) made of pure copper brazing, for example, by brazing at 1000° C. or higher.
• the brazing filler metal may be other than pure copper brazing. For example, brass brazing, nickel brazing, gold brazing, palladium brazing, etc. may be used.
• the cylinder 44 is joined to the small-diameter tubular portion 36C of the housing 36 and the tubular protrusion 39C of the yoke 39 by brazing.
• the armature 48 is arranged between the cylindrical storage portion 36A of the housing 36 and the concave portion 41B of the anchor 41.
• the armature 48 is a movable iron core (moving element) made of a magnetic material and movably provided in the winding axis direction of the coil 34A. That is, the armature 48 is provided so as to be axially movable on the inner peripheral side of the coil 34A.
• the armature 48 is arranged on the cylindrical storage portion 36A of the housing 36, the concave portion 41B of the anchor 41, the cylindrical protrusion 39C of the yoke 39, and the inner peripheral side of the cylinder 44, and is arranged between the cylindrical storage portion 36A of the housing 36 and the anchor 41.
• the armature 48 is arranged on the inner peripheral side of the housing cylinder portion 36A of the housing 36 and the concave portion 41B of the anchor 41, and the first and second bushes 38, 43 and the operating pin 49 are engaged by the magnetic force generated in the coil 34A. It is possible to move in the axial direction through.
• the armature 48 is fixed (integrated) with an operating pin 49 extending through the center side thereof, and moves together with the operating pin 49 .
• the operating pin 49 is axially slidably supported by the lid portion 36B of the housing 36 and the anchor 41 via first and second bushes 38 and 43 .
• the armature 48 is formed in a substantially cylindrical shape using an iron-based magnetic material.
• the magnetic force generated in the coil 34A causes the armature 48 to generate a thrust (attractive force) in a direction in which the armature 48 is attracted toward the concave portion 41B of the anchor 41 .
• the operating pin 49 is a shaft portion that transmits the thrust of the armature 48 to the pilot valve body 32 of the damping force adjustment valve 18 (control valve), and is formed of a hollow rod.
• the operating pin 49 is displaced integrally with the armature 48 . That is, the armature 48 is integrally fixed to the axially intermediate portion of the operating pin 49 by means of press fitting or the like, whereby the armature 48 and the operating pin 49 are made into a sub-assembly.
• Both axial sides of the operating pin 49 are slidably supported by the lid portion 36B on the housing 36 side and the yoke 39 (anchor 41) via first and second bushes 38 and 43. As shown in FIG.
• One end of the operating pin 49 projects axially from the anchor 41 (yoke 39), and the projecting end is provided with a damping force adjustment valve.
• Eighteen pilot valve bodies 32 are fixed. Therefore, the pilot valve body 32 moves together with the armature 48 and the operating pin 49 in the axial direction.
• the set valve opening pressure of the pilot valve body 32 is a pressure value corresponding to the thrust of the armature 48 based on the energization of the coil 34A.
• the armature 48 is moved in the axial direction by the magnetic force from the coil 34A to open and close the pilot valve of the shock absorber 1 (that is, the pilot valve body 32 with respect to the pilot body 26).
• the cover member 51 is a magnetic cover that covers the mold coil 34 together with the other side cylindrical portion 39H of the yoke 39 from the outside.
• the cover member 51 is formed of a magnetic material (magnetic material) as a cover body that covers the molded coil 34 from the other side in the axial direction. (magnetic path) is formed.
• the cover member 51 is formed in a lidded tubular shape as a whole, and includes a cylindrical fitting cylinder portion 51A and the other end side of the fitting cylinder portion 51A (right end in FIG. 2, upper end in FIG. 3). ) and a disk-shaped cover plate 51B that closes the .
• the fitting cylinder portion 51A of the cover member 51 is fitted around the outer periphery of the lid portion 36B of the housing 36, and in this state, the lid portion 36B of the housing 36 is accommodated inside.
• the outer peripheral side of the cover plate 51B of the cover member 51 forms an annular flange 51C extending radially outward of the fitting tubular portion 51A. It is fixed to the provided crimped portion 39J.
• the other side cylindrical portion 39H of the yoke 39 and the cover plate 51B of the cover member 51 are pre-assembled (sub-assembled) with the molded coil 34 inside as shown in FIG.
• the lid portion 36B of the housing 36 is positioned inside the fitting tubular portion 51A of the cover member 51. is attached to the Thereby, magnetic flux can be transferred between the fitting tube portion 51A of the cover member 51, the cover plate 51B and the yoke 39.
• a sealing groove 51D is formed along the entire periphery of the fitting cylinder portion 51A of the cover member 51 on the outer peripheral side where the resin member 34C of the molded coil 34 is fitted.
• a seal member (for example, an O-ring 52) is mounted in the seal groove 51D.
• the O-ring 52 liquid-tightly seals between the molded coil 34 and the cover member 51 (fitting cylinder portion 51A). This prevents dust including rainwater and muddy water from entering between the housing 36 and the molded coil 34 through the space between the cover member 51 and the molded coil 34, and between the housing 36 and the cover member 51. can be prevented.
• the yoke 39 and the cover member 51 incorporate the molded coil 34 inside, and as shown in FIG. It is fastened to the valve case 19 of the adjustment valve 18 .
• the retainer ring 54 is attached to the engaging recess 39L of the yoke 39 before the lock nut 53 is attached.
• the retainer ring 54 partially protrudes radially outward from the engaging recess 39L of the yoke 39, and transmits the fastening force of the lock nut 53 to the one-side tubular portion 39G of the yoke 39. As shown in FIG.
• the lock nut 53 is formed as a stepped cylindrical body, and is positioned on one axial side of the lock nut 53 and has a female threaded portion 53A screwed to the male threaded portion 19B of the valve case 19 on the inner peripheral side thereof, and a retainer ring 54 having an inner diameter dimension.
• An engaging cylinder portion 53B is provided which is bent radially inward so as to be smaller than the outer diameter dimension and which engages with the retainer ring 54 from the outside.
• the lock nut 53 engages the female threaded portion 53A and the male threaded portion 19B of the valve case 19 in a state in which the inner surface of the engaging cylindrical portion 53B is in contact with the retainer ring 54 attached to the engaging recessed portion 39L of the yoke 39.
• a notch is formed by partially cutting the circumferential direction at a position where the mover (movable iron core) and the stator (stationary iron core) face each other.
• the axial attractive force (thrust force of the mover) between the mover and the stator is reduced, and there is a possibility that the mover will be difficult to move especially when the current is low.
• the change in the thrust characteristic becomes large due to the notch in the circumferential direction. For this reason, in the case of the conventional technology, in order to secure the thrust while suppressing the vibration, it is necessary to change the solenoid structure such as extending the shaft length and enlarging the outer diameter, which may increase the additional cost.
• the thrust force of the mover decreases and the characteristics of the thrust force change due to the formation of the notch in the mover.
• the effect of suppressing vibration is insufficient due to insufficient attractive force for attracting the mover in the radial direction (unevenness of the attractive force in the radial direction). Therefore, the following configuration is adopted in the embodiment. That is, the armature 48 as a mover (movable iron core) has a large diameter portion 48A and a small diameter portion 48B. . This secures both the radial attraction force (vibration suppressing force) and the axial attraction force (thrust force) between the anchor 41 and the armature 48 . These points will be described below.
• the shock absorber 1 includes an inner cylinder 4 and an outer cylinder 2 as cylinders, a piston 5, a piston rod 8, and an annular oil chamber D (more specifically, and a damping force adjustment valve 18 driven by a solenoid 33 .
• the damping force adjustment mechanism 17 includes a coil 34A, an armature 48 as a mover, an anchor 41 as a stator, and a pilot valve (a pilot body 26 and a pilot valve body 26) as a control valve. 32) Furthermore, a damping force adjustment valve 18 is provided.
• the solenoid 33 includes a coil 34A, an armature 48 as a movable core, an anchor 41 as a fixed core, and an operating pin 49 as a shaft.
• the solenoid also has a housing 36 as a magnetic member.
• the coil 34A generates a magnetic field when energized. At least a portion of the armature 48 is located on the inner peripheral side of the coil 34A and is provided movably in the axial direction. In other words, the armature 48 is provided on the inner peripheral side of the coil 34A so as to be movable in the axial direction.
• the anchor 41 axially faces the armature 48 .
• the operating pin 49 is displaced integrally with the armature 48 .
• the housing 36 is provided between the coil 34A and the armature 48 in the radial direction.
• the armature 48 has a large diameter portion 48A and a small diameter portion 48B.
• the small diameter portion 48B is provided on the anchor 41 side. That is, the radial clearance between the armature 48 and the housing 36 is larger on the anchor 41 side than on the other locations.
• the large-diameter portion 48A has the same diameter (outer diameter D) at any position in the circumferential direction, that is, has a circular peripheral edge that continues in the circumferential direction.
• the small-diameter portion 48B has the same diameter (outer diameter d) at any position in the circumferential direction, that is, has a circular peripheral edge that continues in the circumferential direction.
• the large-diameter portion 48A and the small-diameter portion 48B have a circular cross-sectional shape at any position in the axial direction.
• the large-diameter portion 48A and the small-diameter portion 48B having different outer diameters are connected by a stepped surface 48C.
• the large-diameter portion 48A which is the side facing the bottom portion (cover portion 36B) of the housing 36, has a larger diameter than the small-diameter portion 48B, which is the side facing the anchor 41. That is, the large diameter portion 48A has a larger outer diameter than the small diameter portion 48B.
• D can be, for example, 1.01d to 1.02d.
• the outer diameter dimension d of the small diameter portion 48B is kept the same as that of the configuration (for example, the current product) in which the outer diameter dimension of the movable iron core (armature) is the same throughout the axial direction.
• the outer diameter dimension D of the large diameter portion 48A is increased by, for example, about 1 to 2% of the outer diameter dimension d of the small diameter portion 48B.
• the magnetic force increases at the portion where the gap between the large diameter portion 48A and the housing 36 provided on the outer diameter side of the armature 48 is the smallest.
• the large-diameter portion 48A can cause the radial suction force to be uneven in the circumferential direction, and can absorb the vibration of the armature 48.
• the small-diameter portion 48B has the same diameter (circular cross-section) at any position in the circumferential direction, thereby ensuring an axial suction force (thrust force of the armature 48).
• the axial length L1 of the large diameter portion 48A is the same as the axial length L2 of the small diameter portion 48B, or smaller than the axial length L2 of the small diameter portion 48B. Therefore, it is possible to suppress the vibration based on the deviation of the radial attraction force by the large-diameter portion 48A while suppressing the decrease in the thrust force and the change in the characteristics.
• an operating pin 49 that is displaced integrally with the armature 48 is provided so as to extend axially on the inner peripheral sides of the armature 48 and the anchor 41 .
• the operating pin 49 has bushes 38 and 43 as bearings at both ends in the axial direction.
• a housing 36 as a magnetic member is provided on the outer peripheral side of the armature 48 .
• the gap between the large diameter portion 48A of the armature 48 and the housing 36 is made larger than the gap between the bushes 38, 43 and the operating pin 49.
• the difference between the outer diameter of the large diameter portion 48A and the inner diameter of the housing 36 is greater than the difference between the outer diameter of the operating pin 49 and the inner diameters of the bushes 38,43. Therefore, contact (contact) between the large-diameter portion 48A and the housing 36 can be suppressed.
• the gap between the armature 48 (large diameter portion 48A) and the housing 36 is the gap (radial direction gap ) is smaller than That is, the difference between the outer diameter of the large diameter portion 48A and the inner diameter of the housing 36 is smaller than the difference between the outer diameter of the small diameter portion 48B and the inner diameter of the outer peripheral protrusion 41C. Therefore, it is possible to suppress the abutment (contact) between the small-diameter portion 48B and the anchor 41 (the concave portion 41B).
• the solenoid 33 of the embodiment axially drives the armature 48 as a movable iron core composed of at least the first magnetic resistance portion by magnetic action when the coil 34A is energized.
• the solenoid 33 has an operating pin 49 as a shaft mounted on the armature 48 and bushes 38 and 43 as bearings supporting both ends of the armature 48 .
• the solenoid 33 has a second magnetic resistance portion that exerts the action of moving at least the armature 48 in the radial direction by magnetic action.
• This second magnetic resistance portion is formed by a notch formed by cutting one side of the armature 48 in the axial direction along the circumferential direction. This notch corresponds to the small diameter portion 48B formed on the anchor 41 side of the armature 48 by notching the entire circumference in the circumferential direction.
• the solenoid 33, the damping force adjusting mechanism 17, and the shock absorber 1 according to this embodiment have the configurations as described above, and their operation will be described next.
• the shock absorber 1 when the shock absorber 1 is mounted on a vehicle such as an automobile, for example, the upper end side (protruding end side) of the piston rod 8 is attached to the vehicle body side, and the mounting eye 3A provided on the bottom cap 3 is attached to the wheel side. Mounted on. Further, the solenoid 33 of the damping force adjusting mechanism 17 is connected to a control device (controller) provided on the vehicle body side of the vehicle via an electric wiring cable (both not shown) or the like.
• a control device controller
• the piston rod 8 When the vehicle is running, when vibrations occur in the vertical direction due to unevenness of the road surface, etc., the piston rod 8 is displaced so as to extend and contract from the outer cylinder 2, and a damping force is generated by the damping force adjustment mechanism 17 and the like. can dampen vehicle vibrations.
• the damping force generated by the buffer 1 can be variably adjusted.
• the movement of the piston 5 inside the inner cylinder 4 causes the compression side check valve 7 of the piston 5 to close.
• the oil in the rod-side oil chamber B is pressurized, and the damping force is adjusted through the oil hole 4A of the inner cylinder 4, the annular oil chamber D, and the connection port 12C of the intermediate cylinder 12. It flows into the oil passage 20B of the connecting pipe body 20 of the valve 18 .
• the oil corresponding to the movement of the piston 5 flows from the reservoir chamber A into the bottom side oil chamber C by opening the extension side check valve 16 of the bottom valve 13 .
• the disk valve 6 opens to relieve the pressure in the rod-side oil chamber B to the bottom-side oil chamber C.
• the oil flowing into the oil passage 20B of the connecting pipe 20 moves through the valve member as indicated by the arrow X in FIG. 21 , the center hole 24 B of the pilot pin 24 , the center hole 26 C of the pilot body 26 , pushes the pilot valve body 32 open, and flows into the pilot body 26 .
• the oil that has flowed into the inside of the pilot body 26 flows between the flange portion 32A of the pilot valve body 32 and the disk valve 29, the oil passage 30A of the holding plate 30, the notch 31A of the cap 31, the oil of the valve case 19, and the Flows to reservoir chamber A through chamber 19C.
• the pressure in the oil passage 20B of the connecting pipe 20 that is, the pressure in the rod-side oil chamber B reaches the valve opening pressure of the main valve 23.
• the inflowing oil passes through the oil passage 21B of the valve member 21, pushes the main valve 23 open, and flows through the oil chamber 19C of the valve case 19 into the reservoir chamber A, as indicated by the arrow Y in FIG.
• the movement of the piston 5 in the inner cylinder 4 opens the compression side check valve 7 of the piston 5 and closes the extension side check valve 16 of the bottom valve 13.
• the oil in the bottom side oil chamber C flows into the rod side oil chamber B before the bottom valve 13 (disk valve 15) is opened.
• the oil corresponding to the amount of the piston rod 8 entering the inner cylinder 4 flows from the rod-side oil chamber B to the reservoir chamber A via the damping force adjustment valve 18 in the same path as during the extension stroke. .
• the bottom valve 13 (disk valve 15) opens and the pressure in the bottom side oil chamber C is transferred to the reservoir chamber A. Relieve.
• the damping force is generated by the orifice 24C of the pilot pin 24 and the valve opening pressure of the pilot valve body 32 before the main valve 23 of the damping force adjustment valve 18 is opened.
• a damping force is generated according to the degree of opening of the main valve 23 .
• the damping force can be directly controlled regardless of the piston speed.
• the valve opening pressure of the pilot valve body 32 is reduced and a soft side damping force is generated.
• the thrust force of the armature 48 is increased by increasing the current supplied to the coil 34A, the valve opening pressure of the pilot valve body 32 increases, and the damping force on the hardware side is generated.
• the internal pressure of the back pressure chamber 27 communicated via the oil passage 25 on the upstream side changes depending on the opening pressure of the pilot valve element 32 . Accordingly, by controlling the valve opening pressure of the pilot valve body 32, the valve opening pressure of the main valve 23 can be adjusted at the same time, and the adjustment range of the damping force characteristics can be widened.
• the armature 48 has a large diameter portion 48A and a small diameter portion 48B, and the small diameter portion 48B is provided on the anchor 41 side. Therefore, the small-diameter portion 48B of the armature 48 on the side of the anchor 41 (that is, the side facing the anchor 41 in the axial direction) has the same diameter at any position in the circumferential direction (a circular peripheral edge that is uniformly continuous in the circumferential direction). ), it is possible to ensure the axial suction force. Thereby, the thrust of the armature 48 can be ensured.
• the large-diameter portion 48A on the side opposite to the anchor (the side opposite to the anchor 41) of the armature 48 has the smallest gap between the large-diameter portion 48A and the housing 36. becomes larger. For this reason, it is possible to generate a bias in the radial suction force in the circumferential direction, and to absorb the vibration of the armature 48 . As a result, it is possible to ensure both the thrust of the armature 48 and the suppression of vibration.
• the Thrust can be ensured by increasing the diameter of the large-diameter portion 48A without changing the shaft length (L1+L2) of the armature 48. Therefore, it is possible to suppress vibration while ensuring thrust without requiring a large structural change from the current product.
• the small-diameter portion 48B (and the large-diameter portion 48A) can be formed only by turning, for example, using a lathe, so additional costs can be reduced.
• the operating pin 49 is provided extending axially on the inner peripheral side of the armature 48 and the anchor 41 . Therefore, in addition to being able to provide the long operating pin 49 on the inner peripheral side of the armature 48 and the anchor 41, it is possible to ensure the thrust of this operating pin 49 and suppress vibration.
• the operating pin 49 has bushes 38 and 43 that serve as bearings at both ends in the axial direction. Therefore, the bushes 38 and 43 can smoothly and stably support the operating pin 49 that is displaced integrally with the armature 48 together with the armature 48 .
• the second magnetic resistance portion that exerts the effect of moving the armature 48 in the radial direction consists of the small diameter portion 48B formed by notching one side of the armature 48 in the axial direction along the circumferential direction.
• the small-diameter portion 48B that is notched over the entire circumference of the armature 48 can generate a force that moves the armature 48 in the radial direction with the large-diameter portion 48A that is not notched.
• the thrust of the armature 48 can be ensured, and vibration can be suppressed.
• the gap between the large diameter portion 48A of the armature 48 and the housing 36 is larger than the gap between the bushes 38, 43 and the operating pin 49. Therefore, contact between the large-diameter portion 48A of the armature 48 and the housing 36 can be suppressed.
• the axial length L1 of the large diameter portion 48A is smaller than the axial length L2 of the small diameter portion 48B. Therefore, by making the outer diameter of the small diameter portion 48B the same as the outer diameter of the current product (the outer diameter of the armature is the same throughout the axial direction), the same thrust as the current product can be achieved. can be ensured.
• the axial length L1 of the large-diameter portion 48A smaller than the axial length L2 of the small-diameter portion 48B, a decrease in thrust force and a change in characteristics are suppressed, and the radial attraction force (radial direction Vibration suppressing effect can be obtained based on the bias of the attractive force of the magnetic field. This can improve design robustness.
• the damping force adjustment valve 18 of the damper 1 is driven by the solenoid 33.
• the armature 48 of the solenoid 33 has a large diameter portion 48A and a small diameter portion 48B, and the small diameter portion 48B is provided on the anchor 41 side. Therefore, it is possible to both secure the thrust force of the solenoid 33 and suppress vibration, and to suppress vibration (noise) due to cavitation of the damping force adjustment valve 18 driven by the solenoid 33 . As a result, the stability of the buffer 1 can be improved.
• the armature 48 of the damping force adjusting mechanism 17 has a large diameter portion 48A and a small diameter portion 48B, and the small diameter portion 48B is provided on the anchor 41 side. Therefore, it is possible to secure the thrust of the armature 48 and suppress the vibration, and the pilot valve (the pilot body 26 and the pilot valve body 32) controlled by the armature 48 and the vibration (abnormality) of the damping force adjustment valve 18 due to cavitation. sound) can be suppressed.
• the radial clearance between the armature 48 and the housing 36 is larger on the anchor 41 side than at other locations.
• the side of the anchor 41 that is, the side where the armature 48 and the anchor 41 face each other in the axial direction
• the side opposite to the anchor the side opposite to the anchor 41
• the magnetic force increases at the portion where the radial gap is the smallest due to manufacturing tolerances.
• the inner diameter of the housing 36 (cylindrical storage portion 36A) is the same, and the outer diameter of the armature 48 is smaller on the anchor 41 side than on other locations. Therefore, by reducing the outer diameter of the armature 48 on the anchor 41 side, the radial clearance between the armature 48 on the anchor 41 side and the housing 36 can be made larger than other locations.
• the armature 48 is provided with one large-diameter portion 48A and one small-diameter portion 48B has been described as an example.
• the configuration is not limited to this, and for example, a configuration in which at least one of the large diameter portion and the small diameter portion is provided in plurality may be employed.
• the armature 61 may have one large diameter portion 61A and a plurality of (two) small diameter portions 61B, 61B.
• the armature 61 has a first small diameter portion 61B, a large diameter portion 61A, and a second small diameter portion 61B arranged in order from the anchor 41 side.
• the outer diameter dimension d of the small diameter portions 61B, 61B is maintained at the same dimension as that of the current product, for example.
• the outer diameter dimension D of the large diameter portion 61A is increased, for example, by about 1 to 2% of the outer diameter dimension d of the small diameter portion 48B.
• the armature 61 can be assembled in the same direction. is no longer regulated. That is, in this case, the first small diameter portion 61B may be on the anchor 41 side, and the second small diameter portion 61B may be on the anchor 41 side.
• the armature 61 is incorporated into the solenoid 33, a judgment mechanism for judging the large-diameter portion and the small-diameter portion is not required, and erroneous assembly can be suppressed.
• illustration is omitted, not only the small-diameter portion but also a plurality of (for example, two or more) small-diameter portions and large-diameter portions may be provided.
• the case where the inner diameter of the housing 36 (storage tube portion 36A) is the same and the outer diameter of the armature 48 on the anchor 41 side is smaller than that on the other portions has been described as an example.
• the invention is not limited to this.
• a housing 63 is provided between the coil 34A and the armature 62 in the radial direction.
• a radial gap between the armature 62 and the housing 63 (housing cylinder portion 63A) is larger on the anchor 41 side than on the other portions.
• the outer diameter of the armature 62 is the same, and the inner diameter of the housing 63 (cylindrical housing portion 63A) is larger at the anchor 41 side than at other locations.
• the inner diameter side of the storage cylinder portion 63A of the housing 63 has a large diameter portion 63B with a large inner diameter dimension and a small diameter portion 63C with an inner diameter dimension smaller than that of the large diameter portion 63B. 41 side.
• the outer diameter of the armature 62 is maintained at the same size as the current product, for example.
• the inner diameter of the large-diameter portion 63B of the housing 63 is also maintained at the same size as the current product.
• the inner diameter dimension d of the small diameter portion 63C of the housing 63 is reduced by, for example, about 1 to 2% of the inner diameter dimension D of the large diameter portion 63B.
• the inner diameter of the housing is reduced over the entire axial direction (that is, if only the small-diameter portion is reduced)
• the change in thrust characteristics becomes greater than that of the current product.
• the inner diameter is changed by the large diameter portion 63B and the small diameter portion 63C.
• the radial gap between the armature 62 on the anchor 41 side and the housing 63 is reduced to other locations. can be larger than
• the case where the small diameter portion 48B of the armature 48 has the same outer diameter dimension d along the axial direction has been described as an example.
• the invention is not limited to this, and for example, the outer peripheral surface of the small diameter portion 64B of the armature 64 may be tapered as in a third modification shown in FIG. That is, the small-diameter portion 64B of the armature 64 may be formed as an inclined surface inclined in a direction in which the diameter becomes smaller as it approaches the anchor 41 .
• the outer diameter dimension of the small diameter portion 64B closest to the anchor 41 side is the same as that of the configuration (for example, the current product) in which the outer diameter dimension of the movable iron core (armature) is the same throughout the axial direction. hold.
• the outer diameter D of the large diameter portion 64A can be, for example, about 1 to 2% larger than the outer diameter of the small diameter portion 64B closest to the anchor 41 side.
• the axial length L1 of the large diameter portion 64A can be made smaller than the axial length L2 of the small diameter portion 64B.
• the axial length L1 of the large diameter portion 64A is made smaller than the axial length L2 of the small diameter portion 64B.
• the axial length of the large diameter portion 64A and the axial length of the small diameter portion 64B may be the same.
• the outer peripheral surface of the small diameter portion 64B is a linear inclined surface.
• 64B may be a concave curved surface (concave curved surface).
• the small diameter portion 64B may be a convex curved surface (convex curved surface).
• the center (center axis line) of the large diameter portion 64A and the center of the small diameter portion 64B closest to the anchor 41 are concentric.
• the center (center axis line) of the large diameter portion 64A and the center of the small diameter portion 64B closest to the anchor 41 may be eccentric.
• the circumference of the small-diameter portion 64B closest to the anchor 41 (arc in cross section) may be inscribed in the circumference of the large-diameter portion 64A (arc in cross section).
• the shape may be non-uniform on one side and the other side in the circumferential direction).
• the case where the housing 36 and the cylinder 44, and the cylinder 44 and the yoke 39 are joined via the brazing material has been described as an example.
• the housing 36 and the cylinder 44, and the cylinder 44 and the yoke 39 may be joined by welding, for example.
• the anchor 41 is fixed in the fixing hole 39A of the yoke 39 by press fitting.
• the configuration is not limited to this, and the anchor may be fixed in the yoke by using a screwing means such as a screw or a caulking means.
• the anchor 41 and the yoke 39 are configured as separate bodies (separate parts) has been described as an example.
• the anchor and the yoke may be configured integrally (one part).
• one side of the cylinder 44 is fixed to the yoke 39
• the configuration is not limited to this, and for example, one side of the cylinder (joint member) may be fixed to the anchor.
• the yoke 39 is provided with the other side tubular portion 39H, and the tip side (the other side in the axial direction) of the other side tubular portion 39H is fixed to the outer peripheral side of the cover member 51 by the caulking portion 39J.
• the present invention is not limited to this, and for example, the annular portion of the yoke and the other side tubular portion may be formed separately, and the other side tubular portion may be integrally formed with the cover member.
• the solenoid 33 is configured as a proportional solenoid has been described as an example. However, it is not limited to this, and may be configured as an ON/OFF type solenoid, for example.
• the dual-tube shock absorber 1 consisting of the outer cylinder 2 and the inner cylinder 4 has been described as an example.
• the present invention is not limited to this, and may be used, for example, in a damping force adjustable shock absorber made of a single-tube tubular member (cylinder).
• the solenoid 33 is used as the variable damping force actuator of the shock absorber 1, that is, the pilot valve body 32 constituting the pilot valve of the damping force adjustment valve 18 is the object to be driven by the solenoid 33.
• the solenoid is not limited to this, and can be widely used as an actuator incorporated in various mechanical devices such as valves used in hydraulic circuits, that is, as a driving device that drives an object to be driven linearly.
• the movable core has a large-diameter portion and a small-diameter portion, and the small-diameter portion is provided on the fixed core side. It is for this reason, the small-diameter portion on the fixed core side of the movable core (that is, the side facing the fixed core in the axial direction) has the same diameter at any position in the circumferential direction (uniformly continuous in the circumferential direction). A small diameter portion of the circular periphery) can secure the suction force in the axial direction. Thereby, the thrust of the movable iron core can be ensured.
• the large-diameter side of the movable core opposite to the fixed core is the portion where the gap between the magnetic member provided on the outer diameter side of the movable core and the magnetic member provided on the outer diameter side of the movable core is the smallest due to the manufacturing tolerance of this large-diameter section.
• magnetic force increases. For this reason, it is possible to cause the radial attraction force to be uneven in the circumferential direction, and to absorb the vibration of the movable iron core. As a result, it is possible to ensure both the thrust of the movable core and the suppression of vibration.
• the small diameter portion can be formed only by lathe turning, for example, additional costs can be reduced.
• the shaft portion is provided so as to extend axially on the inner peripheral side of the movable core and the fixed core. Therefore, in addition to being able to provide a long shaft portion on the inner peripheral side of the movable core and the fixed core, it is possible to secure the thrust of this shaft portion and suppress vibration.
• the shaft has bearings at both ends in the axial direction. Therefore, the bearing can smoothly and stably support the shaft portion that is displaced integrally with the movable iron core together with the movable iron core.
• the second magnetic resistance portion that exerts the action of moving the movable core in the radial direction is formed of a notch extending circumferentially on one side of the movable core in the axial direction. For this reason, the notch formed along the entire circumference of the movable iron core can generate a force for moving the movable iron core in the radial direction at the non-notched portion. Thereby, the thrust of the movable iron core can be ensured, and vibration can be suppressed.
• the gap between the large-diameter portion of the movable iron core and the magnetic member is larger than the gap between the bearing and the shaft. Therefore, it is possible to suppress the contact (contact) between the large-diameter portion of the movable iron core and the magnetic member.
• the axial length of the large diameter portion is smaller than the axial length of the small diameter portion.
• the outer diameter of the small-diameter portion can be made, for example, the same as that of a configuration in which the outer diameter of the movable iron core is the same throughout the axial direction, thereby ensuring a thrust force similar to that of this configuration. can be done.
• the damping force adjustment valve of the damping force adjustable shock absorber is driven by a solenoid.
• the movable iron core of the solenoid has a large diameter portion and a small diameter portion, and the small diameter portion is provided on the fixed iron core side. Therefore, it is possible to both secure the thrust force of the solenoid and suppress the vibration, thereby suppressing the vibration (abnormal noise) due to the cavitation of the damping force adjustment valve driven by the solenoid. As a result, the stability of the damping force adjustable shock absorber can be improved.
• the mover of the damping force adjustment mechanism has a large diameter portion and a small diameter portion, and the small diameter portion is provided on the stator side. Therefore, it is possible to both ensure the thrust force of the mover and suppress vibration, thereby suppressing vibration (abnormal noise) due to cavitation of the control valve controlled by the mover.
• the radial gap between the movable core and the magnetic member is larger on the fixed core side than at other locations. Therefore, on the side of the fixed core (that is, the side where the movable core and the fixed core face each other in the axial direction), a radial gap of the same width can be provided in the circumferential direction, thereby ensuring the axial attractive force. Thereby, the thrust of the movable iron core can be ensured.
• the magnetic force increases at the portion where the radial gap is the smallest due to manufacturing tolerances. For this reason, it is possible to cause the radial attraction force to be uneven in the circumferential direction, and to absorb the vibration of the movable iron core. As a result, it is possible to ensure both the thrust of the movable core and the suppression of vibration.
• the diameter of the movable core is the same, and the inner diameter of the magnetic member is larger on the fixed core side than at other locations. Therefore, by increasing the inner diameter of the magnetic member on the fixed core side, the radial gap between the movable core on the fixed core side and the magnetic member can be made larger than other locations.
• the present invention is not limited to the above-described embodiments, and includes various modifications.
• 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.
• 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.
• shock absorber (damping force adjustable shock absorber)
• 2 outer cylinder (cylinder) 4: inner cylinder (cylinder)
• 5 piston
• 8 piston rod
• 17 damping force adjustment mechanism
• 18 damping force adjustment valve (control valve)
• 32 pilot valve body (control valve)
• 33 solenoid
• 34A coil
• 36, 63 housing (magnetic member)
• 38 first bush (bearing)
• 41 anchor (fixed iron core, fixed child)
• 43 second bush (bearing)
• 48, 61, 62, 64 armature (moving iron core, mover, first magnetic resistance portion)
• 48B, 61B , 62B, 64B small diameter portion (notch, second magnetic resistance portion)

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• Electromagnetism (AREA)
• General Engineering & Computer Science (AREA)
• Power Engineering (AREA)
• Mechanical Engineering (AREA)
• Fluid-Damping Devices (AREA)
• Electromagnets (AREA)

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• 2023
  • 2023-01-05 JP JP2024501011A patent/JP7843339B2/ja active Active
  • 2023-01-05 WO PCT/JP2023/000037 patent/WO2023157503A1/ja not_active Ceased
  • 2023-01-05 KR KR1020247019287A patent/KR20240112864A/ko active Pending
  • 2023-01-05 DE DE112023000985.6T patent/DE112023000985T5/de active Pending
  • 2023-01-05 US US18/834,434 patent/US20250172190A1/en active Pending
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