WO2020022177A1 - 緩衝器 - Google Patents
緩衝器 Download PDFInfo
- Publication number
- WO2020022177A1 WO2020022177A1 PCT/JP2019/028226 JP2019028226W WO2020022177A1 WO 2020022177 A1 WO2020022177 A1 WO 2020022177A1 JP 2019028226 W JP2019028226 W JP 2019028226W WO 2020022177 A1 WO2020022177 A1 WO 2020022177A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- back pressure
- shock absorber
- chamber
- main valve
- pressure chamber
- Prior art date
Links
Images
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
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
-
- 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
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/369—Sealings for elements other than pistons or piston rods, e.g. valves
-
- 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
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination
-
- 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
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/368—Sealings in pistons
-
- 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
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
-
- 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
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
- F16F9/5126—Piston, or piston-like valve elements
-
- 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
- B60G17/06—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
- B60G2500/11—Damping valves
- B60G2500/114—Damping valves pressure regulating valves
-
- 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
-
- 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
- F16F2232/00—Nature of movement
- F16F2232/08—Linear
-
- 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
- F16F2234/00—Shape
- F16F2234/02—Shape cylindrical
-
- 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
- F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
- F16F9/061—Mono-tubular units
-
- 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
- F16F9/464—Control of valve bias or pre-stress, e.g. electromagnetically
Definitions
- the present invention relates to a shock absorber that generates a damping force by controlling the flow of a working fluid accompanying a stroke of a piston rod.
- Patent Document 1 discloses a hydraulic shock absorber in which a check valve is opened to introduce the pressure of a cylinder lower chamber into a back pressure chamber of an extension side main valve during a compression stroke of a piston rod. This shock absorber can prevent the damping force from being lost due to the opening of the extension-side main valve due to the pressure of the cylinder lower chamber during the contraction stroke.
- the shock absorber described in Patent Literature 1 arranges a plurality of disks and a check valve to form a passage (flow path) in order to introduce the oil liquid in the upstream chamber into the back pressure chamber during the reverse stroke. ing. In this case, the axial length (total length) of the cylinder becomes long, and the size of the shock absorber is increased.
- the object of the present invention is to provide a shock absorber that can be reduced in size.
- the shock absorber is a cylinder filled with a working fluid, a piston slidably fitted in the cylinder, one end connected to the piston, and the other end of the cylinder.
- a piston rod extended to the outside, a main valve for controlling a flow of a working fluid from an upstream chamber to a downstream chamber generated by one-way movement of the piston to generate a damping force, and the downstream valve
- a back pressure chamber that is arranged in the chamber and applies a back pressure in the valve closing direction to the main valve, and a seal mechanism that moves with the movement of the outer peripheral portion when the main disk is opened to partition the back pressure chamber.
- the sealing mechanism is When moving in the other direction of the piston, characterized in that a valve for introducing the working fluid on the downstream side of the chamber in one direction during movement of the piston in the back pressure chamber.
- the size of the shock absorber can be reduced.
- FIG. 3 is a partial cross-sectional view of the shock absorber according to the first embodiment. It is an enlarged view of the principal part of FIG. It is a sectional view of a part of shock absorber concerning a 2nd embodiment. It is an enlarged view of the principal part of FIG.
- FIG. 10 is an explanatory diagram of the third embodiment, corresponding to FIG. 2 of the first embodiment.
- the shock absorber 1 according to the first embodiment is a single-cylinder hydraulic shock absorber that is mounted between an unsprung portion (wheel) and a sprung portion (vehicle body) of a suspension device of an automobile or the like.
- the vertical direction in FIGS. 1 and 2 is the vertical direction in the shock absorber 1 according to the first embodiment.
- a piston 3 is movably (slidably) fitted inside the cylinder 2.
- the piston 3 defines the inside of the cylinder 2 into two chambers, an upper cylinder chamber 2A and a lower cylinder chamber 2B.
- a shaft portion 5 (small diameter portion) on one end side of a piston rod 4 is connected to the piston 3.
- the other end of the piston rod 4 is inserted through a rod guide and an oil seal (not shown) mounted on the upper end of the cylinder 2, and extends outside the cylinder 2.
- a free piston (not shown) is provided in the cylinder 2 so as to be vertically movable in the cylinder 2.
- the free piston divides the inside of the cylinder 2 into a cylinder lower chamber 2B on the piston 3 side and a gas chamber (not shown) on the bottom side.
- An oil liquid is sealed in the upper cylinder chamber 2A and the lower cylinder chamber 2B as a working fluid.
- the gas chamber is filled with a high-pressure gas (nitrogen gas) as a working fluid.
- the piston 3 is provided with a plurality of extension passages 7 (only one is shown in FIG. 1) and a compression passage 8 that communicate between the upper cylinder chamber 2A and the lower cylinder chamber 2B.
- An extension main valve 21 is provided at the lower end of the piston 3.
- the extension side main valve 21 is provided in the cylinder lower chamber 2B which is a downstream side chamber during the extension stroke.
- the extension-side main valve 21 is configured to move the oil liquid from the cylinder upper chamber 2A (upstream chamber) to the cylinder lower chamber 2B (downstream chamber) generated by sliding the piston 3 upward (one direction) during the extension stroke.
- the damping force on the extension side is generated by controlling the flow of air.
- a back pressure chamber forming member 22 having a bottomed cylindrical shape is provided on the inner peripheral side of the back pressure chamber forming member 22.
- the inner peripheral portion 23 is moved between the inner peripheral portion 6 of the piston 3 and the washer 12 by an axial force generated by tightening the nut 11 attached to the shaft portion 5 (hereinafter, referred to as “axial force of the nut 11”). Will be retained.
- a disk 24, a retainer 26, and a disk 27 are provided in order from the top. The disk 24, the retainer 26, and the disk 27 are sandwiched between the inner peripheral portion 23 of the back pressure chamber forming member 22 and the washer 12 by the axial force of the nut 11.
- An annular seat portion 32 is provided on the outer peripheral side of the lower end of the piston 3.
- the outer periphery of the disk-shaped extension-side main valve 21 is seated on the seat portion 32.
- the extension-side main valve 21 is not clamped at the inner peripheral portion, and is simply supported by a retainer 33 attached to the shaft portion 5 of the piston rod 4.
- a small-diameter shaft portion 34 into which the inner peripheral surface of the extension-side main valve 21 is slidably fitted is formed at the upper end of the retainer 33.
- an annular seat portion 35 is in contact with the back surface of the inner peripheral portion of the extension side main valve 21 (the surface opposite to the surface seated on the seat portion 32 of the piston 3). It is formed.
- the inner peripheral portion of the extension-side main valve 21 is seated on the seat portion 35 of the retainer 33, and is supported by the shaft portion 34 of the retainer 33 so as to be vertically movable.
- a disc-shaped regulating member 36 is provided between the shaft portion 34 of the retainer 33 and the inner peripheral portion 6 of the piston 3 to regulate the upward movement of the inner peripheral portion of the extension-side main valve 21.
- the seat portion 35 of the retainer 33 is formed such that the outer diameter decreases toward the tip (upper end).
- an annular packing 37 as a sealing mechanism made of an elastic material such as rubber is fixed to the back surface of the extension-side main valve 21.
- the packing 37 is slidable on the outer peripheral side seal portion 38 (seal mechanism) slidably in contact with the inner peripheral surface 40 of the cylindrical portion 39 of the back pressure chamber forming member 22 and the outer peripheral surface 42 of the retainer 33.
- an inner peripheral side sealing portion 41 (blocking member) to be brought into contact with.
- a back pressure chamber 43 of the extension side main valve 21 is defined and formed inside the back pressure chamber forming member 22.
- an outer peripheral side sealing portion 38, an inner peripheral side sealing portion 41, and a base portion 44 serving as a base are integrally formed.
- the outer peripheral side seal portion 38 is an annular wall extending downward from the base portion 44, and is formed so that the outer diameter and the inner diameter increase substantially downward in a conical shape.
- the outer peripheral side seal portion 38 receives the pressure of the back pressure chamber 43 and is pressed against the inner peripheral surface 40 of the cylindrical portion 39 of the back pressure chamber forming member 22.
- a cross-section (hereinafter referred to as a “cross-section by an axial plane”) of a plane including the axis of the piston rod 4 is formed between the outer peripheral portion of the packing 37 and the cylindrical portion 39 of the back pressure chamber forming member 22 in an annular wedge shape.
- a gap 45 is formed, and the gap 45 opens (communicates) with the cylinder lower chamber 2B.
- the inner peripheral side seal portion 41 is an annular wall extending downward from the base portion 44, and is formed so that the outer diameter and the inner diameter become substantially conical downward. Thus, the inner peripheral side seal portion 41 receives the pressure of the back pressure chamber 43 and is pressed against the outer peripheral surface 42 of the retainer 33.
- An annular concave portion 50 is formed on the outer peripheral side of the inner peripheral side seal portion 41. The area of the inner peripheral side seal portion 41 which receives the pressure of the back pressure chamber 43 can be adjusted by the shape (depth or the like) of the concave portion 50.
- annular passage 46 opening on the upper end surface of the inner peripheral portion 23 and an annular passage 47 opening on the lower end surface of the inner peripheral portion 23. And are provided.
- the upper passage 46 and the lower passage 47 are communicated with each other by a vertically extending groove-shaped passage 14 formed on the outer peripheral surface of the shaft portion 5 of the piston rod 4.
- a disk 48 is interposed between the inner peripheral portion 23 of the back pressure chamber forming member 22 and the retainer 33.
- the back pressure chamber 43 is communicated with the passage 14 of the shaft 5 via a slit-like passage 49 formed in the disk 48 and a passage 46 above the inner peripheral portion 23 of the back pressure chamber forming member 22.
- a contraction side main valve 51 is provided on the upper end side of the piston 3.
- the contraction-side main valve 51 is provided in the cylinder upper chamber 2A, which is a chamber on the downstream side during the contraction stroke.
- the contraction side main valve 51 controls the flow of the oil liquid from the cylinder lower chamber 2B (upstream chamber) to the cylinder upper chamber 2A (downstream chamber) caused by the downward sliding of the piston 3 during the contraction stroke. As a result, a contraction-side damping force is generated.
- a back pressure chamber forming member 52 as a bottomed cylindrical case member is provided on the upper end side of the piston 3.
- a substantially cylindrical inner peripheral portion 53 into which the shaft portion 5 of the piston rod 4 is fitted is formed on the inner peripheral side of the back pressure chamber forming member 52.
- the inner peripheral portion 53 is held between the inner peripheral portion 6 of the piston 3 and the washer 13 by the axial force of the nut 11.
- a disk 54, a retainer 56, and a disk 57 are provided in order from the bottom.
- the disk 54, the retainer 56, and the disk 57 are sandwiched between the inner peripheral portion 53 of the back pressure chamber forming member 52 and the washer 13 by the axial force of the nut 11.
- An annular seat portion 62 is provided on the outer peripheral side of the upper end of the piston 3.
- the outer periphery of the disk-shaped contraction-side main valve 51 is seated on the seat portion 62.
- the contraction side main valve 51 is not clamped at the inner peripheral portion, and is simply supported by a retainer 63 attached to the shaft portion 5 of the piston rod 4.
- a small-diameter shaft portion 64 into which the inner peripheral surface of the contraction-side main valve 51 is slidably fitted is formed at the lower end of the retainer 63.
- an annular seat portion 65 that contacts the back surface of the inner peripheral portion of the contraction side main valve 51 (the surface opposite to the surface seated on the seat portion 62 of the piston 3). It is formed.
- the inner peripheral portion of the contraction side main valve 51 is seated on the seat portion 65 of the retainer 63, and is supported by the shaft portion 64 of the retainer 63 so as to be movable in the vertical direction.
- a disc-shaped regulating member 66 is provided between the shaft portion 64 of the retainer 63 and the inner peripheral portion 6 of the piston 3 to regulate the downward movement of the inner peripheral portion of the contraction-side main valve 51.
- the seat portion 65 of the retainer 63 is formed such that the outer diameter decreases toward the front end (lower end).
- An annular packing 67 made of an elastic material such as rubber is fixed to the rear surface of the contraction side main valve 51.
- the packing 67 is slidably contacted with the outer peripheral side seal portion 68 slidably in contact with the inner peripheral surface 70 of the cylindrical portion 69 of the back pressure chamber forming member 52 and the outer peripheral surface 72 of the retainer 63.
- an inner peripheral side sealing portion 71 (blocking member) is formed inside the back pressure chamber forming member 52.
- an outer peripheral side seal portion 68, an inner peripheral side seal portion 71, and a base portion 74 serving as a base are integrally formed.
- the inner peripheral side seal portion 71 (blocking member) is fixedly provided on the back surface of the contraction side main valve 51.
- an O-ring is provided between the retainer 63 and the contraction side main valve 51.
- the outer peripheral side seal portion 68 is an annular wall extending upward from the base portion 74, and is formed such that the outer diameter and the inner diameter increase substantially upward in a conical shape. Thereby, the outer peripheral side seal portion 68 receives the pressure of the back pressure chamber 73 and is pressed against the inner peripheral surface 70 of the cylindrical portion 69 of the back pressure chamber forming member 52.
- the oil liquid in the cylinder lower chamber 2B upstream chamber
- An annular gap 75 having a wedge-shaped cross section along the axial plane is formed between the outer peripheral portion of the packing 67 and the cylindrical portion 69 of the back pressure chamber forming member 52, and the gap 75 opens to the cylinder upper chamber 2A. Communication).
- the inner peripheral side seal portion 71 is an annular wall extending upward from the base portion 74, and is formed such that the outer diameter and the inner diameter increase substantially upward in a conical shape. Thus, the inner peripheral side seal portion 71 is pressed against the outer peripheral surface 72 of the retainer 63 under the pressure of the back pressure chamber 73.
- An annular concave portion 80 is formed on the outer peripheral side of the inner peripheral side seal portion 71. The area of the inner peripheral side seal portion 71 that receives the pressure of the back pressure chamber 73 can be adjusted by the shape (depth or the like) of the concave portion 80.
- annular passage 76 opening on the lower end surface of the inner peripheral portion 53 and an annular passage 77 opening on the upper end surface of the inner peripheral portion 53. And are provided.
- the lower passage 76 and the upper passage 77 are connected by a passage 14 formed on the outer peripheral surface of the shaft portion 5 of the piston rod 4.
- a disk 78 is interposed between the inner peripheral portion 53 of the back pressure chamber forming member 52 and the retainer 63.
- the back pressure chamber 73 is communicated with the passage 14 of the shaft 5 via a slit-shaped passage 79 formed in the disk 78 and a passage 76 below the inner peripheral portion 53 of the back pressure chamber forming member 52.
- the oil liquid in the cylinder upper chamber 2 ⁇ / b> A (upstream chamber) is supplied to the passage 16 formed on the inner peripheral side of the disk 54, Via a passage 77 formed in the back pressure chamber forming member 52, a passage 14 formed in the shaft portion 5 of the piston rod 4, and a passage 49 formed in the disk 48 through an extension side back pressure introduction passage, It is introduced into the back pressure chamber 43 of the extension side main valve 21.
- the oil liquid in the cylinder lower chamber 2B (upstream chamber) becomes The passage 18 formed on the inner peripheral side of the disk 24, the passage 47 formed on the back pressure chamber forming member 22, the passage 14 formed on the shaft 5 of the piston rod 4, and the passage 79 formed on the disk 78 It is introduced into the back pressure chamber 73 of the contraction side main valve 51 via the contraction side back pressure introduction passage configured.
- the cylinder 3 moves from the cylinder upper chamber 2 ⁇ / b> A (upstream chamber) to the cylinder lower chamber 2 ⁇ / b> B (downstream chamber) as the piston 3 slides (moves upward) in the cylinder 2.
- the damping force is generated by controlling the flow of the oil liquid.
- the oil liquid (pressure) in the cylinder upper chamber 2A is introduced into the back pressure chamber 43 of the extension main valve 21 via the extension side back pressure introduction passage described above.
- the oil liquid in the cylinder upper chamber 2 ⁇ / b> A flows through the passage 16 formed on the inner peripheral side of the disk 54 and the back pressure chamber.
- the passage 77 formed in the inner peripheral portion 53 of the forming member 52, the passage 14 formed in the shaft portion 5 of the piston rod 4, the passage 47 formed in the inner peripheral portion 23 of the back pressure chamber forming member 22, and the disk 24 Flows through the passage 18 formed on the inner peripheral side of the cylinder lower chamber 2B to generate a damping force having orifice characteristics.
- the extension-side main valve 21 When the extension-side main valve 21 is opened due to an increase in the piston speed, a damping force having valve characteristics corresponding to the opening degree of the extension-side main valve 21 is generated.
- the outer peripheral side seal portion 38 (seal mechanism) of the packing 37 bends (falls) by receiving the pressure of the cylinder lower chamber 2B during the contraction stroke of the piston rod 4 which is the reverse stroke. ) Is separated from the contact state (can be separated), and functions as a check valve in which the oil liquid (pressure) in the cylinder lower chamber 2B is introduced into the back pressure chamber 43.
- the force acting on the extension-side main valve 21 in the valve closing direction becomes larger than the force acting on the extension-side main valve 21 in the valve opening direction.
- the oil liquid (pressure) in the cylinder lower chamber 2B is introduced into the back pressure chamber 43 through the outer periphery of the extension-side main valve 21 so that the back pressure chamber 43 is released.
- the inner peripheral side sealing portion 41 (blocking member) of the packing 37 is pressed against the outer peripheral surface 42 of the retainer 33.
- the oil liquid (pressure) introduced into the back pressure chamber 43 during the contraction stroke (reverse stroke) passes between the inner peripheral portion of the simply supported extension main valve 21 and the retainer 33 and extends to the extension passage 7. And the damping force can be prevented from being lost due to the oil liquid flowing to the cylinder upper chamber 2A.
- the damping force is generated by controlling the flow of the oil liquid to the air.
- the oil liquid (pressure) in the cylinder lower chamber 2B is introduced into the back pressure chamber 73 of the contraction-side main valve 51 via the above-described contraction-side back pressure introduction passage.
- the oil liquid in the cylinder lower chamber 2 ⁇ / b> B causes the passage 18 formed on the inner peripheral side of the disk 24 and the passage 47 formed on the inner peripheral portion 23 of the back pressure chamber forming member 22.
- a cylinder formed through a passage 14 formed in the shaft portion 5 of the piston rod 4, a passage 77 formed in the inner peripheral portion 53 of the back pressure chamber forming member 52, and a passage 16 formed in the inner peripheral side of the disk 54.
- the oil liquid (pressure) in the cylinder upper chamber 2A is introduced into the back pressure chamber 73 via the outer periphery of the contraction side main valve 51, thereby causing the back pressure chamber 73 to return.
- the inner peripheral side sealing portion 71 (blocking member) of the packing 67 is pressed against the outer peripheral surface 72 of the retainer 63.
- the oil liquid (pressure) introduced into the back pressure chamber 73 during the extension stroke (reverse stroke) passes between the inner peripheral portion of the simply supported contraction side main valve 51 and the retainer 63 and the contraction side passage 8. Flow to the cylinder lower chamber 2 ⁇ / b> B, thereby preventing loss of the damping force.
- the working fluid in the upstream chambers 2B and 2A is introduced into the back pressure chambers 43 and 73 via the outer circumferences of the main valves 21 and 51. Because of this, a plurality of disks and a check valve are provided for a passage (flow path) for introducing the working fluid in the chambers 2B and 2A, which are on the upstream side during the reverse stroke, into the back pressure chambers 43 and 73. It is not necessary to form with. Therefore, the axial length of the shaft portion 5 of the piston rod 4 and thus the overall length of the cylinder 2 can be reduced, and the shock absorber 1 can be reduced in size.
- the first embodiment has the following advantages. According to the first embodiment, a cylinder filled with a working fluid, a piston slidably fitted in the cylinder, one end is connected to the piston, and the other end is extended outside the cylinder. A piston rod, a main valve that controls a flow of a working fluid from an upstream chamber to a downstream chamber generated by one-way movement of the piston to generate a damping force, and a main valve that is disposed in the downstream chamber. A back pressure chamber for applying a back pressure in the valve closing direction to the valve, a seal mechanism that moves with the movement of the outer peripheral portion when the main disc is opened to separate the back pressure chamber, and a back pressure for the working fluid in the upstream chamber.
- a back pressure introducing passage for introducing the piston into the chamber.
- the shock absorber controls opening of the main valve by the back pressure of the back pressure chamber.
- Downstream chamber when moving in one direction Since it becomes a valve for introducing the working fluid to the back pressure chamber, a plurality of disks and a check valve are arranged to introduce the working fluid of the chamber on the upstream side during the backward stroke of the piston rod into the back pressure chamber. It is not necessary to form a passage (flow path), the axial length (total length) of the cylinder can be shortened, and the shock absorber can be downsized.
- the main valve has a simple (cantilevered) support structure in which the inner peripheral side is not clamped, the main valve can be opened at a lower piston speed. As a result, the soft damping force can be set lower, and the riding comfort of the vehicle can be improved. Further, when the generated soft damping force is the same, a main valve having a smaller outer diameter can be used as compared with a main valve having an inner peripheral portion clamped. Thus, the outer diameter of the cylinder can be reduced, and the shock absorber can be downsized.
- the shut-off member is provided on the inner peripheral side of the main valve, so that the working fluid is prevented from flowing to the upstream chamber at the time of the reverse stroke in which the piston slides in the other direction. It is possible to prevent the working fluid in the back pressure chamber from flowing to the upstream chamber through the inner peripheral side of the simply supported main valve, and to prevent the damping force from coming off.
- the movable member is a packing integrally provided on the outer periphery of the main valve, the number of parts can be reduced, and the number of assembly steps can be reduced. Further, in the first embodiment, the movable member is formed on the outer peripheral side of the packing, the blocking member is formed on the inner peripheral side of the packing, and the main valve, the movable member, and the blocking member are integrally provided. Can be prevented from increasing the number of components.
- the movable member and the blocking member need not be formed on the outer peripheral side and the inner peripheral side of one packing.
- a movable member made of packing is provided on the outer peripheral side of the main valve, and the inner peripheral side of the main valve is provided.
- the movable member and the blocking member may be provided separately such that a blocking member made of packing is provided. Further, the blocking member may be, for example, an O-ring or the like in addition to the packing.
- the first embodiment the case where the present invention is applied to a single-cylinder hydraulic shock absorber has been described. However, the first embodiment can be applied to a double-cylinder hydraulic shock absorber in which a reservoir is formed between the cylinder 2 and the outer tube. . In this case, a free piston is not required, and a base valve is disposed between the cylinder lower chamber 2B and the reservoir. By using a double cylinder, the axial length of the cylinder 2 can be further reduced.
- the shock absorber 1 according to the first embodiment is a so-called conventional suspension damper having a single damping force characteristic with respect to the piston speed.
- the shock absorber 81 according to the second embodiment is a so-called semi-active suspension damper having a damping force variable mechanism 82.
- the basic structure of the shock absorber 81 according to the second embodiment including the damping force variable mechanism 82 is the same as the conventional semi-active suspension damper. Therefore, a detailed description of the basic structure of the semi-active suspension damper will be omitted.
- the extension-side main valve 21 in the second embodiment is simply supported by the retainer 33 mounted on the shaft portion 84 of the piston case 83.
- a packing 37 is fixed to the back surface of the extension-side main valve 21.
- the outer peripheral side seal portion 38 slidably abuts on the inner peripheral surface 40 of the cylindrical portion 39 of the back pressure chamber forming member 22, and the inner peripheral side seal portion 41 can slide on the outer peripheral surface 33 of the retainer 33.
- an annular back pressure chamber 43 is formed inside the back pressure chamber forming member 22.
- the movement of the extension-side main valve 21 is regulated by the regulation member 36 provided between the shaft portion 34 of the retainer 33 and the inner peripheral portion 6 of the piston 3.
- the movement of the extension-side main valve 21 is restricted by the inner peripheral portion 6 of the piston 3.
- annular seat 87 is provided at the upper end of the piston 3.
- a disk valve 88 composed of a plurality of disks is seated on the seat portion 87.
- An annular valve member 89 is mounted on the upper end of the shaft 84 of the piston case 83.
- a disk valve 90 mounted on the shaft 84 of the piston case 83 is provided.
- the disc valve 90 is seated on an annular seat portion 91 provided on an outer peripheral edge of a lower end portion of the valve member 89 and an annular seat portion 92 provided on an inner peripheral side with respect to the seat portion 91. Is done.
- the oil liquid (working fluid) in the cylinder lower chamber 2B side is pressurized by sliding of the piston 3 in the cylinder 2, so that the oil liquid in the cylinder lower chamber 2B passes through the contraction side passage 20.
- the disc valve 88 is opened to flow to the cylinder upper chamber 2A.
- the damping force of the valve characteristics by the disc valve 88 is obtained.
- the thrust (control current) of the solenoid 97 is controlled to vary the set load (valve opening pressure) of the valve 98, so that the valve 98 is opened against the thrust of the solenoid 97.
- the oil liquid in the cylinder lower chamber 2B side passes through the passage 99, the chamber 100, the passage 101, and the annular passage 102, and further opens the disk valve 90 in which the passage 93 (back pressure chamber introduction passage) is formed. Then, it flows to the cylinder upper chamber 2A. At this time, the damping force of the valve characteristics by the disc valve 90 can be obtained.
- the outer peripheral side seal portion 38 (seal mechanism) of the packing 37 is slidably brought into contact with the inner peripheral surface 40 of the cylindrical portion 39 of the back pressure chamber forming member 22 so that the extension side main valve 21 is formed.
- Back pressure chamber 43 is formed.
- the valve seat 111 (seal mechanism) as a cylindrical member is attached to the rear surface of the outer peripheral portion of the extension side main valve 21 (with respect to the surface seated on the seat portion 32 of the piston 3).
- the back pressure chamber 43 of the extension-side main valve 21 is formed by abutting against the opposite surface).
- a protruding portion 112 protruding inward is provided.
- an annular seat portion 113 provided to face the seat portion 32 of the piston 3 is formed.
- an annular seat portion 114 is formed on the lower surface of the inner peripheral portion of the projecting portion 112.
- the seat portion 114 of the valve seat 111 is seated on the outer peripheral edge of the disk 115 having elasticity.
- the valve seat 111 is urged upward by the elasticity of the disk 115, and the seat portion 113 is pressed against the extension-side main valve 21.
- the inner periphery of the disk 115 is sandwiched between the retainer 33 and the inner periphery of the back pressure chamber forming member 116 (cylindrical member) as an annular fixed disk.
- the back pressure chamber forming member 116 is mounted on the shaft 5 of the piston rod 4 by the axial force of the nut 11.
- the inner peripheral surface 118 of the valve seat 111 is slidably abutted on the outer peripheral end surface 117 of the back pressure chamber forming member 116.
- a liquid-tight seal is provided between the outer peripheral end surface 117 of the back pressure chamber forming member 116 and the inner peripheral surface 118 of the valve seat 111 by an annular seal portion 119 provided on the outer peripheral end surface 117 of the back pressure chamber forming member 116. Is done.
- the oil liquid in the cylinder upper chamber 2 ⁇ / b> A flows into the passage 14 formed in the shaft 5 of the piston rod 5 and the inner peripheral surface of the back pressure chamber forming member 116. It is introduced into the back pressure chamber 43 via a back pressure introducing passage including the formed annular passage 120 and a passage 121 (notch) formed in the inner peripheral portion of the disk 115.
- An annular chamber 122 is formed between the disk 115 and the back pressure chamber forming member 116, and the chamber 122 and the back pressure chamber 43 form a passage 123 (notch) formed on the outer periphery of the disk 115.
- the cylinder is separated from the extension-side main valve 21, whereby the oil liquid (pressure) in the cylinder lower chamber 2 ⁇ / b> B is introduced into the back pressure chamber 43 via the outer periphery of the extension-side main valve 21.
- the force acting on the extension-side main valve 21 in the valve closing direction becomes larger than the force acting on the extension-side main valve 21 in the valve opening direction.
- the oil liquid (pressure) in the cylinder lower chamber 2B is introduced into the back pressure chamber 43 through the outer periphery of the extension-side main valve 21 so that the back pressure chamber 43 is released.
- the packing 124 (blocking member) is pressed against the outer peripheral surface 42 of the retainer 33.
- the oil liquid (pressure) introduced into the back pressure chamber 43 during the contraction stroke (reverse stroke) passes between the inner peripheral portion of the simply supported extension main valve 21 and the retainer 33 and extends to the extension passage 7. Flow to the cylinder upper chamber 2 ⁇ / b> A.
- the present invention is not limited to the above-described embodiment, and includes various modifications.
- the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described above.
- a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of one embodiment can be added to the configuration of another embodiment.
- shock absorber 2 ⁇ 2 cylinder, 2A cylinder upper chamber, 2B cylinder lower chamber, 3 piston, 4 piston rod, 21 extension main valve, 43 back pressure chamber, 68 outer peripheral seal part (seal mechanism)
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
- Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
Abstract
Description
第1実施形態に係る緩衝器1は、自動車等のサスペンション装置のばね下(車輪)、ばね上(車体)間に装着される単筒式油圧緩衝器である。説明の便宜上、図1、図2における上下方向を、第1実施形態に係る緩衝器1における上下方向とする。
ディスク24の内周側に形成された通路18、背圧室形成部材22に形成された通路47、ピストンロッド4の軸部5に形成された通路14、およびディスク78に形成された通路79によって構成される縮み側背圧導入通路を介して、縮み側メインバルブ51の背圧室73に導入される。
ピストンロッド4の伸び行程時には、シリンダ2内のピストン3の摺動(上方向への移動)に伴う、シリンダ上室2A(上流側の室)からシリンダ下室2B(下流側の室)への油液の流れを制御することにより、減衰力を発生させる。当該伸び行程では、シリンダ上室2Aの油液(圧力)が、前述した伸び側背圧導入通路を介して伸び側メインバルブ21の背圧室43に導入される。
そして、第1実施形態では、逆行程となるピストンロッド4の縮み行程時に、シリンダ下室2Bの圧力を受けてパッキン37の外周側シール部38(シール機構)が内周側に撓む(倒れる)ことにより、接触した状態から離間し(離接可能)、シリンダ下室2Bの油液(圧力)が背圧室43に導入されるチェックバルブとして機能する。これにより、伸び側メインバルブ21に作用する閉弁方向の力が、伸び側メインバルブ21に作用する開弁方向の力よりも大きくなる。その結果、逆行程時に伸び側メインバルブ21が開弁されるのを抑止することが可能であり、安定した減衰力を得ることができる。
そして、第1実施形態では、逆行程となるピストンロッド4の伸び行程時に、シリンダ上室2Aの圧力を受けてパッキン67の外周側シール部68(可動部材)が内周側に撓む(倒れる)ことにより、シリンダ上室2Aの油液(圧力)が背圧室73に導入される。これにより、縮み側メインバルブ51に作用する閉弁方向の力が、縮み側メインバルブ51に作用する開弁方向の力よりも大きくなる。その結果、逆行程時に縮み側メインバルブ51が開弁されるのを抑止することが可能であり、安定した減衰力を得ることができる。
第1実施形態によれば、作動流体が封入されたシリンダと、該シリンダ内に摺動可能に嵌装されたピストンと、一端がピストンに連結され、他端がシリンダの外部へ延出されたピストンロッドと、ピストンの一方向の移動によって生じる上流側の室から下流側の室への作動流体の流れを制御して減衰力を発生させるメインバルブと、下流側の室に配置され、メインバルブに閉弁方向の背圧を作用させる背圧室と、メインディスクの開弁時における外周部の移動と共に移動し、背圧室を区画するシール機構と、上流側の室の作動流体を背圧室へ導入するための背圧導入通路と、を備え、背圧室の背圧によってメインバルブの開弁を制御する緩衝器であって、シール機構は、ピストンの他方向の移動時に、ピストンの一方向の移動時の下流側の室の作動流体を背圧室に導入するバルブとなるので、ピストンロッドの逆行程時に上流側となる室の作動流体を背圧室に導入するため、複数枚のディスク、および逆止弁を配置して通路(流路)を形成する必要がなく、シリンダの軸長(全長)を短くすることが可能であり、緩衝器を小型化することができる。
また、遮断部材は、パッキンの他、例えばOリング等とすることができる。
また、第1実施形態では、単筒式油圧緩衝器に適用した場合を説明したが、シリンダ2とアウタチューブとの間にリザーバが形成された複筒式油圧緩衝器への適用が可能である。この場合、フリーピストンは必要なく、シリンダ下室2Bとリザーバとの間にベースバルブが配置される。複筒化することによりシリンダの2の軸長をさらに短縮することができる。
ピストンロッド4の伸び行程時には、シリンダ2内のピストン3の摺動にによってシリンダ上室2A側の油液(作動流体)が加圧されると、弁体96の閉弁状態では、シリンダ上室2A(上流側の室)の油液が、前述した伸び側背圧導入通路を介して背圧室43に導入される。そして、ソレノイド97の推力(制御電流)を制御して背圧室43の圧力、すなわち、伸び側メインバルブ21の背圧を可変させることにより、伸び側メインバルブ21のセット荷重(開弁圧力)を調節することができる。
ピストンロッド4の伸び行程時には、シリンダ上室2Aの油液(圧力)が、前述した伸び側背圧導入通路を介して伸び側メインバルブ21の背圧室43に導入される。ピストン速度の上昇によって伸び側メインバルブ21が開弁すると、当該伸び側メインバルブ21の開度に応じたバルブ特性の減衰力が発生する。
そして、逆行程となるピストンロッド4の縮み行程時には、シリンダ下室2Bの圧力を受けてバルブシート111(シール機構)が下方向へ移動(摺動)することでバルブシート111のシート部113が伸び側メインバルブ21から離座し、これにより、シリンダ下室2Bの油液(圧力)が、伸び側メインバルブ21の外周を介して背圧室43に導入される。これにより、伸び側メインバルブ21に作用する閉弁方向の力が、伸び側メインバルブ21に作用する開弁方向の力よりも大きくなる。その結果、逆行程時に伸び側メインバルブ21が開弁されるのを抑止することが可能であり、安定した減衰力を得ることができる。
Claims (8)
- 緩衝器であって、該緩衝器は、
作動流体が封入されたシリンダと、
該シリンダ内に摺動可能に嵌装されたピストンと、
一端が前記ピストンに連結され、他端が前記シリンダの外部へ延出されたピストンロッドと、
前記ピストンの一方向の移動によって生じる上流側の室から下流側の室への作動流体の流れを制御して減衰力を発生させるメインバルブと、
前記下流側の室に配置され、前記メインバルブに閉弁方向の背圧を作用させる背圧室と、
前記メインディスクの開弁時における外周部の移動と共に移動し、前記背圧室を区画するシール機構と、
前記上流側の室の作動流体を前記背圧室へ導入するための背圧導入通路と、を備え、
前記背圧室の背圧によって、前記メインバルブの開弁が制御されており、
前記シール機構は、前記ピストンの他方向の移動時に、前記ピストンの一方向の移動時の下流側の室の作動流体を前記背圧室に導入するバルブとなることを特徴とする緩衝器。 - 請求項1に記載の緩衝器において、
前記シール機構は、前記メインバルブの外周に一体的に設けられる可撓性のパッキンであることを特徴とする緩衝器。 - 請求項2に記載の緩衝器において、
前記背圧室を形成する有底筒状のケース部材を有し、前記パッキンは、前記ケース部材の筒部と離接可能に設けられることを特徴とする緩衝器。 - 請求項1に記載の緩衝器において、
前記シール機構は、前記メインバルブに離接可能な円筒部材からなり、
前記シール機構と、該円筒部材の内周側と摺動可能に設けられた固定円板とによって、前記背圧室が形成されていることを特徴とする緩衝器。 - 請求項1ないし3のいずれか1項に記載の緩衝器において、
前記メインバルブは、内周側がクランプせずに支持されていることを特徴とする緩衝器。 - 請求項5に記載の緩衝器において、
前記メインバルブの内周側には、前記ピストンの他方向の移動による前記背圧室から前記上流側の室への作動流体の流通を遮断する遮断部材が設けられることを特徴とする緩衝器。 - 請求項6に記載の緩衝器において、
前記遮断部材は、前記メインバルブの内周側に一体的に設けられるパッキンであることを特徴とする緩衝器。 - 請求項6または7に記載の緩衝器において、
前記遮断部材の外周側には、環状の凹部が形成されることを特徴とする緩衝器。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020207032868A KR102439407B1 (ko) | 2018-07-25 | 2019-07-18 | 완충기 |
DE112019003735.8T DE112019003735T5 (de) | 2018-07-25 | 2019-07-18 | Stoßdämpfer |
CN201980040260.2A CN112352117B (zh) | 2018-07-25 | 2019-07-18 | 缓冲器 |
JP2020532334A JP6972352B2 (ja) | 2018-07-25 | 2019-07-18 | 緩衝器 |
US17/255,119 US11867253B2 (en) | 2018-07-25 | 2019-07-18 | Shock absorber |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2018139411 | 2018-07-25 | ||
JP2018-139411 | 2018-07-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2020022177A1 true WO2020022177A1 (ja) | 2020-01-30 |
Family
ID=69181578
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2019/028226 WO2020022177A1 (ja) | 2018-07-25 | 2019-07-18 | 緩衝器 |
Country Status (6)
Country | Link |
---|---|
US (1) | US11867253B2 (ja) |
JP (1) | JP6972352B2 (ja) |
KR (1) | KR102439407B1 (ja) |
CN (1) | CN112352117B (ja) |
DE (1) | DE112019003735T5 (ja) |
WO (1) | WO2020022177A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2024009629A1 (ja) * | 2022-07-08 | 2024-01-11 | 日立Astemo株式会社 | 減衰力発生機構 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005344911A (ja) * | 2004-06-07 | 2005-12-15 | Hitachi Ltd | 油圧緩衝器 |
JP2008256129A (ja) * | 2007-04-06 | 2008-10-23 | Hitachi Ltd | シリンダ装置 |
WO2015050241A1 (ja) * | 2013-10-03 | 2015-04-09 | カヤバ工業株式会社 | 液圧緩衝器 |
JP2016183702A (ja) * | 2015-03-25 | 2016-10-20 | 株式会社ショーワ | 圧力緩衝装置 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101067431B (zh) * | 2001-11-27 | 2010-09-15 | 株式会社索密克石川 | 回转式阻尼器和具备该回转式阻尼器的汽车零件以及旋转动作辅助机构 |
JP4967091B2 (ja) * | 2007-04-19 | 2012-07-04 | 日立オートモティブシステムズ株式会社 | 流体圧緩衝器 |
JP5120629B2 (ja) * | 2008-03-31 | 2013-01-16 | 日立オートモティブシステムズ株式会社 | 減衰力調整式緩衝器及びこれを用いたサスペンション制御装置 |
JP5418778B2 (ja) * | 2010-02-26 | 2014-02-19 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP5648790B2 (ja) | 2010-08-31 | 2015-01-07 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
KR101239919B1 (ko) | 2011-01-28 | 2013-03-06 | 주식회사 만도 | 쇽업소버의 밸브 구조 |
JP5850688B2 (ja) * | 2011-09-28 | 2016-02-03 | 日立オートモティブシステムズ株式会社 | シリンダ装置の製造方法 |
JP5909557B2 (ja) * | 2012-09-20 | 2016-04-26 | 日立オートモティブシステムズ株式会社 | サスペンション装置 |
DE112014005430T5 (de) | 2013-11-29 | 2016-08-25 | Hitachi Automotive Systems, Ltd. | Stoßdämpfer |
JP2016050613A (ja) | 2014-08-29 | 2016-04-11 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
-
2019
- 2019-07-18 CN CN201980040260.2A patent/CN112352117B/zh active Active
- 2019-07-18 US US17/255,119 patent/US11867253B2/en active Active
- 2019-07-18 KR KR1020207032868A patent/KR102439407B1/ko active IP Right Grant
- 2019-07-18 WO PCT/JP2019/028226 patent/WO2020022177A1/ja active Application Filing
- 2019-07-18 JP JP2020532334A patent/JP6972352B2/ja active Active
- 2019-07-18 DE DE112019003735.8T patent/DE112019003735T5/de active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005344911A (ja) * | 2004-06-07 | 2005-12-15 | Hitachi Ltd | 油圧緩衝器 |
JP2008256129A (ja) * | 2007-04-06 | 2008-10-23 | Hitachi Ltd | シリンダ装置 |
WO2015050241A1 (ja) * | 2013-10-03 | 2015-04-09 | カヤバ工業株式会社 | 液圧緩衝器 |
JP2016183702A (ja) * | 2015-03-25 | 2016-10-20 | 株式会社ショーワ | 圧力緩衝装置 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2024009629A1 (ja) * | 2022-07-08 | 2024-01-11 | 日立Astemo株式会社 | 減衰力発生機構 |
Also Published As
Publication number | Publication date |
---|---|
CN112352117B (zh) | 2022-08-09 |
US20210246960A1 (en) | 2021-08-12 |
KR102439407B1 (ko) | 2022-09-01 |
JPWO2020022177A1 (ja) | 2021-04-30 |
KR20200139823A (ko) | 2020-12-14 |
JP6972352B2 (ja) | 2021-11-24 |
US11867253B2 (en) | 2024-01-09 |
CN112352117A (zh) | 2021-02-09 |
DE112019003735T5 (de) | 2021-05-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5843842B2 (ja) | 減衰力調整式緩衝器 | |
US10619694B2 (en) | Shock absorber | |
JP4919045B2 (ja) | 減衰力調整式流体圧緩衝器 | |
KR102133063B1 (ko) | 실린더 장치 | |
KR101326935B1 (ko) | 감쇠력 조정식 유압 완충기 | |
JP5034074B2 (ja) | 減衰力調整式流体圧緩衝器 | |
US8517154B2 (en) | Shock absorber | |
US20140262654A1 (en) | Two position valve with face seal and pressure relief port | |
US20110186393A1 (en) | Shock absorber | |
JP2015194198A (ja) | 減衰力調整式緩衝器 | |
US11655875B2 (en) | Damping valve and shock absorber | |
WO2019239521A1 (ja) | 圧力緩衝装置 | |
KR102140353B1 (ko) | 완충기 | |
KR20160026753A (ko) | 완충기 | |
JP2000193014A (ja) | 減衰力調整式油圧緩衝器 | |
JP2009052703A (ja) | 減衰力調整式油圧緩衝器 | |
WO2020022177A1 (ja) | 緩衝器 | |
JP2017048825A (ja) | 緩衝器 | |
JP2004257507A (ja) | 油圧緩衝器 | |
JP6496592B2 (ja) | 緩衝器 | |
US20010002639A1 (en) | Solenoid apparatus for use in hydraulic shock absorber | |
KR102627961B1 (ko) | 감쇠력 조정식 완충기 | |
JP7129385B2 (ja) | 減衰力調整式緩衝器 | |
JP2009108984A (ja) | 流体圧緩衝器 | |
JP2021050782A (ja) | 減衰力調整式緩衝器 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 19840711 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2020532334 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 20207032868 Country of ref document: KR Kind code of ref document: A |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 19840711 Country of ref document: EP Kind code of ref document: A1 |