WO2019021797A1 - 緩衝器およびその製造方法 - Google Patents
緩衝器およびその製造方法 Download PDFInfo
- Publication number
- WO2019021797A1 WO2019021797A1 PCT/JP2018/025874 JP2018025874W WO2019021797A1 WO 2019021797 A1 WO2019021797 A1 WO 2019021797A1 JP 2018025874 W JP2018025874 W JP 2018025874W WO 2019021797 A1 WO2019021797 A1 WO 2019021797A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- passage
- chamber
- free piston
- housing
- 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
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of 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
-
- 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
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/182—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein comprising a hollow piston rod
-
- 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
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
-
- 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
- F16F9/3207—Constructional features
- F16F9/3221—Constructional features of piston rods
-
- 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
- F16F9/3207—Constructional features
- F16F9/3228—Constructional features of connections between pistons and piston rods
-
- 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
- F16F9/3271—Assembly or repair
-
- 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
- F16F9/3405—Throttling passages in or on piston body, e.g. slots
-
- 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
- F16F9/50—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
- F16F9/50—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
-
- 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
- F16F9/516—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 resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
-
- 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
- B60G2204/10—Mounting of suspension elements
- B60G2204/12—Mounting of springs or dampers
- B60G2204/129—Damper mount on wheel suspension or knuckle
-
- 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
- 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
- B60G2206/70—Materials used in suspensions
- B60G2206/73—Rubber; Elastomers
-
- 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
- B60G2206/80—Manufacturing procedures
-
- 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
- B60G2500/112—Fluid actuation
-
- 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
- F16F2224/00—Materials; Material properties
- F16F2224/02—Materials; Material properties solids
-
- 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
- F16F2224/00—Materials; Material properties
- F16F2224/02—Materials; Material properties solids
- F16F2224/025—Elastomers
-
- 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
- F16F2226/00—Manufacturing; Treatments
- F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
-
- 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
- F16F2228/04—Frequency effects
-
- 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
- F16F2230/0005—Attachment, e.g. to facilitate mounting onto confer adjustability
-
- 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
- F16F9/062—Bi-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
- F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
- F16F9/064—Units characterised by the location or shape of the expansion chamber
-
- 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
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/185—Bitubular 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
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
- F16F9/3242—Constructional features of cylinders of cylinder ends, e.g. caps
-
- 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
- F16F9/362—Combination of sealing and guide arrangements for piston rods
-
- 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
- F16F9/58—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder
- F16F9/585—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder within the cylinder, in contact with working fluid
Definitions
- the present invention relates to a shock absorber and a method of manufacturing the same.
- Priority is claimed on Japanese Patent Application No. 201-144245, filed July 26, 2017, the content of which is incorporated herein by reference.
- the present invention provides a shock absorber capable of suppressing the generation of noise and a method of manufacturing the same.
- the shock absorber is a cylinder in which the working fluid is enclosed, and a piston slidably fitted in the cylinder and defining the cylinder into two chambers, one side chamber and the other side chamber.
- a piston rod connected to the piston and extended to the outside of the cylinder, a first passage from which working fluid flows out from one chamber in the cylinder when the piston moves in one direction, and the two chambers
- a second passage communicating with one of the chambers, a damping force generation mechanism provided in the first passage for generating a damping force, and a flow passage of at least a part of the second passage,
- a communication hole formed in the piston rod in communication with the side chamber, a housing in which at least a part of the second passage is formed in the inside, a movably provided in the housing and the second passage
- a bottomed cylindrical free piston having a tubular portion and a bottom portion, which is defined on the upstream side and the downstream side of the flow of the working fluid when the piston moves in one direction, and between the free piston and the
- shock absorber According to the above-described shock absorber, the generation of abnormal noise can be suppressed.
- FIG. 7 is a cross-sectional view of another type of free piston of a shock absorber according to an embodiment of the present invention.
- shock absorber and a method of manufacturing the same according to an embodiment of the present invention will be described below with reference to the drawings.
- the shock absorber 1 is a hydraulic shock absorber in which oil is used as a working fluid.
- the shock absorber 1 has a double cylinder type cylinder 4 having an inner cylinder 2 and an outer cylinder 3 as shown in FIG.
- the outer cylinder 3 is larger in diameter than the inner cylinder 2.
- the outer cylinder 3 is disposed coaxially with the inner cylinder 2 so as to cover the inner cylinder 2.
- a reservoir chamber 5 is formed between the inner cylinder 2 and the outer cylinder 3.
- this embodiment can be used not only for a double cylinder type but also for a single cylinder type shock absorber.
- the shock absorber 1 has a piston rod 8 and a piston 9.
- the piston 9 is connected to one axial end of the piston rod 8.
- the piston rod 8 is disposed on the central axis of the inner cylinder 2 and the outer cylinder 3.
- Piston rod 8 has one axial end side inserted into inner cylinder 2 and outer cylinder 3 (i.e., cylinder 4), and the other axial end side extends from inner cylinder 2 and outer cylinder 3 (i.e., cylinder 4) to the outside It has been issued.
- the piston 9 is slidably fitted in the inner cylinder 2 of the cylinder 4.
- the piston 9 divides the inside of the inner cylinder 2 into two chambers 11 (one side chamber) and a chamber 12 (other side chamber).
- the piston 9 is slidably provided in the cylinder 4, and one end thereof is connected to the other end side of the piston rod 8 extended to the outside of the cylinder 4.
- the piston rod 8 is disposed to penetrate the chamber 11 among the chambers 11 and 12. Therefore, the chamber 11 is a chamber on the rod side where the piston rod 8 is mainly disposed in the shock absorber 1.
- oil as a working fluid is sealed in the inner cylinder 2 of the cylinder 4.
- oil as a working fluid and high pressure (about 20 to 30 atm) gas are sealed in the reservoir chamber 5 between the inner cylinder 2 and the outer cylinder 3 in the cylinder 4. That is, the working fluid is sealed in the cylinder 4 having the inner cylinder 2 and the outer cylinder 3.
- air at atmospheric pressure may be sealed instead of high pressure gas.
- the shock absorber 1 has a rod guide 15, a seal member 16 and a friction member 17. Also, the shock absorber 1 has a base valve 18.
- the rod guide 15 is disposed at an end position of the cylinder 4 on the outer projecting side of the piston rod 8.
- the rod guide 15 has a stepped shape, and the large diameter side is fitted inside the outer cylinder 3 and the small diameter side is fitted inside the inner cylinder 2.
- the seal member 16 is disposed at the end of the cylinder 4 and outside the rod guide 15 in the axial direction of the cylinder 4.
- the friction member 17 is disposed between the seal member 16 and the rod guide 15.
- the base valve 18 is disposed at the end opposite to the axial rod guide 15, the seal member 16 and the friction member 17 in the cylinder 4.
- the rod guide 15, the seal member 16 and the friction member 17 are all annular in shape.
- the piston rod 8 is slidably inserted inside the rod guide 15, the seal member 16 and the friction member 17.
- the rod guide 15 axially movably supports the piston rod 8 while restricting its radial movement, and guides the movement of the piston rod 8.
- the seal member 16 is in sliding contact with the outer peripheral portion of the piston rod 8 moving in the axial direction at its inner peripheral portion, and the oil in the inner cylinder 2 and the high pressure gas and oil in the reservoir chamber 5 in the outer cylinder 3 Prevent the leakage to the outside.
- the friction member 17 is in sliding contact with the outer peripheral portion of the piston rod 8 at its inner peripheral portion to cause the piston rod 8 to generate frictional resistance.
- the friction member 17 is not intended to seal.
- the outer cylinder 3 of the cylinder 4 is composed of a cylindrical body member 21 and a bottom lid member 22.
- the bottom lid member 22 is fitted to one end of the body member 21 in the axial direction.
- the bottom lid member 22 has a bottom lid 23 and a rod-shaped portion 24.
- the bottom cover portion 23 is fitted to the inner peripheral portion of the body member 21 at the outer peripheral portion thereof.
- the rod-like portion 24 extends from the center in the radial direction of the bottom lid 23 to the opposite side to the body member 21.
- the bottom lid member 22 is fixed to the trunk member 21 in a sealed state by welding in a state where the bottom lid portion 23 is fitted to the trunk member 21.
- a mounting eye 25 is fixed by welding to the side of the rod portion 24 opposite to the bottom cover portion 23.
- the chamber 12 on the bottom lid 23 side of the cylinder 4 is a chamber on the bottom side in the cylinder 4.
- the body member 21 has an opening 27 on the side opposite to the bottom lid member 22.
- the body member 21 has a locking portion 28 at the opening 27.
- the seal member 16 and the rod guide 15 described above are fitted to the opening 27 side of the body member 21.
- the locking portion 28 protrudes radially inward from the end position of the opening 27 in the body member 21 and sandwiches the sealing member 16 with the rod guide 15.
- the base body 30 of the base valve 18 is disposed inside the bottom cover 23.
- the base body 30 defines a chamber 12 in the cylinder 4 and the reservoir chamber 5 described above.
- the base body 30 has a step shape in which one side in the axial direction is smaller in diameter than the other side.
- the base body 30 is mounted on the bottom cover 23 on the large diameter side and positioned in the radial direction.
- the inner cylinder 2 of the cylinder 4 has a cylindrical shape.
- one end side in the axial direction is supported in a fitted state on the small diameter side of the base body 30 of the base valve 18 and the other small end in the axial direction is the small diameter of the rod guide 15 inside the opening 27 of the outer cylinder 3 It is supported by the side in the fitting state.
- An insertion hole 29 penetrating in the axial direction is formed at the center of the base body 30 of the base valve 18 in the radial direction.
- Flow passages 31 a and 31 b axially penetrating the base body 30 are formed around the insertion holes 29.
- the flow passages 31 a and 31 b can communicate the chamber 12 in the inner cylinder 2 with the reservoir chamber 5 between the outer cylinder 3 and the inner cylinder 2.
- a disc valve 33a is disposed on the opposite side to the bottom cover 23, and a disc valve 33b is disposed on the bottom cover 23 side.
- the disc valve 33a is a check valve.
- the disc valve 33a can open and close the outer flow passage 31a.
- the disc valve 33 b is a damping valve.
- the disc valve 33 b can open and close the inner flow passage 31 b.
- the disc valves 33 a and 33 b are attached to the base body 30 with the radially inner portion clamped by the rivets 35 inserted into the insertion
- the disc valve 33 b allows the flow of oil from the chamber 12 to the reservoir 5 through the passage hole (not shown) of the disc valve 33 a and the flow passage 31 b of the base body 30 to generate a damping force. Regulate the flow of oil in the reverse direction.
- the disc valve 33a allows the oil flow from the reservoir chamber 5 to the chamber 12 side without resistance via the flow passage 31a of the base body 30, while restricting the flow of oil in the reverse direction.
- the disc valve 33b moves to the compression side where the piston rod 8 increases the amount of entry into the cylinder 4, and the piston 9 moves to the chamber 12 side to open the flow passage 31b when the pressure in the chamber 12 rises. It is a compression-side damping valve that generates damping force.
- the disc valve 33a moves the piston rod 8 to the extension side where the amount of protrusion from the cylinder 4 is increased, and the piston 9 moves to the chamber 11 side to open the flow passage 31a when the pressure of the chamber 12 drops. It is a suction valve that allows the fluid to flow from the reservoir chamber 5 into the chamber 12 substantially without generating a damping force.
- the expansion-side damping force may be positively generated by the disk valve 33a as a check valve.
- these disk valves 33a and 33b may be eliminated and used as orifices.
- the piston rod 8 has a mounting shaft 40 and a main shaft 41.
- the mounting shaft portion 40 is a portion to which the piston 9 is mounted.
- the mounting shaft portion 40 is formed on the insertion tip side of the piston rod 8 into the cylinder 4.
- the main shaft portion 41 is a portion other than the mounting shaft portion 40 of the piston rod 8.
- the main shaft portion 41 has a diameter larger than that of the mounting shaft portion 40.
- the piston rod 8 is slidably inserted inside the rod guide 15, the seal member 16 and the friction member 17 in the main shaft portion 41.
- a retainer 42 is fixed to the main shaft portion 41 so as to expand radially outward on the mounting shaft portion 40 side of the insertion portion into the rod guide 15.
- a shock absorber 43 made of an annular elastic material is provided on the opposite side of the retainer 42 from the mounting shaft 40 with the main shaft 41 inserted inside.
- the piston 9 has a plurality of flow passages 50a (first and second passages) (a plurality of first passages and a second passage) and a plurality of cross sections (FIG. 2).
- flow passage 50b shown only at one place in relation.
- the flow passage 50 a and the flow passage 50 b can communicate the chamber 11 with the chamber 12.
- a damping force generation mechanism 51b described later provided for the flow passage 50b closes the flow passage 50b.
- the movement of the piston 9 causes the oil to flow from the chamber 11 which is one of the chamber 11 and the chamber 12 toward the other chamber 12 through the flow passage 50 a.
- the working fluid flows out from the chamber 11 which is one of the chamber 11 and the chamber 12 in the cylinder 4 when the piston 9 moves in one direction.
- a damping force generating mechanism 51a described later provided for the flow passage 50a Shut up.
- the movement of the piston 9 causes the oil to flow from the chamber 12 which is the other of the chamber 11 and the chamber 12 toward the chamber 11 which is one through the flow passage 50b.
- the working fluid flows out from the chamber 11 which is the other of the chamber 11 and the chamber 12 in the cylinder 4 when the piston 9 moves in the other direction.
- the same number of flow passages 50 a and flow passages 50 b are formed in the piston 9.
- the flow passages 50a are formed at equal pitches such that one flow passage 50b is sandwiched between adjacent ones in the circumferential direction.
- one axial side (chamber 11 side) of the piston 9 is opened radially outward, and the other axial side (chamber 12 side) is opened radially inward.
- a damping force generating mechanism 51a that generates a damping force is provided in these flow passages 50a.
- the damping force generation mechanism 51 a is disposed on the side of the chamber 12 in the axial direction of the piston 9.
- the flow passage 50a constitutes a flow passage on the extension side from which the oil flows out from the chamber 11 during the extension stroke.
- the damping force generation mechanism 51a provided for the flow passage 50a serves as an extension-side damping force generation mechanism that generates a damping force by suppressing the flow of oil in the flow passage 50a on the extension side.
- the flow passages 50b are formed at equal pitches so as to sandwich one flow passage 50a between adjacent ones in the circumferential direction.
- the other axial side (the chamber 12 side) of the piston 9 is opened radially outward, and the one axial side (the chamber 11 side) is opened radially inward.
- a damping force generating mechanism 51b that generates damping force is provided.
- the damping force generation mechanism 51 b is disposed on the side of the chamber 11 in the axial direction of the piston 9.
- the flow passage 50b constitutes a compression-side flow passage from which the oil flows out of the chamber 12 during the above-described compression stroke.
- the damping force generation mechanism 51b provided for the flow passage 50b is a compression-side damping force generation mechanism that generates a damping force by suppressing the flow of oil in the flow passage 50b on the contraction side.
- a communication hole 55 is formed in the piston rod 8 at a position of the mounting shaft 40 so as to penetrate the mounting shaft 40 in the radial direction. Further, in the piston rod 8, a communication hole 56 having a diameter larger than that of the communication hole 55 is formed along the axial direction from the position of the communication hole 55 toward the opposite side to the main shaft portion 41. The communication hole 56 communicates with the communication hole 55 and opens at the tip of the mounting shaft 40.
- the communication holes 55, 56 constitute an in-rod passage 57 provided in the piston rod 8.
- a damping force variable mechanism 58 is attached to the piston rod 8 on the opposite side of the piston 9 of the mounting shaft 40 to the main shaft 41.
- the damping force variable mechanism 58 is attached so as to cover the communication hole 56 of the in-rod passage 57.
- the inside of the damping force variable mechanism 58 is in communication with the in-rod passage 57.
- the above-described shock absorber 1 is provided for each of the wheels of the vehicle. At that time, for example, one side of the shock absorber 1 is supported by the vehicle body, and the other side is fixed to the wheel side. Specifically, the mounting eye 25 connected to the vehicle body side by the piston rod 8 and connected to the side opposite to the protruding side of the piston rod 8 of the cylinder 4 is connected to the wheel side. Note that, contrary to the above, the other side of the shock absorber 1 may be supported by the vehicle body, and one side of the shock absorber 1 may be fixed to the wheel side.
- the fluid resistance of the passage formed in the piston 9 is made to differ depending on the speed and amplitude of the vibration, and by suppressing the vibration, the ride quality is improved.
- an inertial force or a centrifugal force generated on the vehicle body as the vehicle travels also acts between the cylinder 4 and the piston rod 8.
- centrifugal force is generated in the vehicle body when the traveling direction is changed by the steering wheel operation, and a force based on the centrifugal force acts between the cylinder 4 and the piston rod 8.
- the shock absorber 1 of the present embodiment has good characteristics against vibration based on the force generated on the vehicle body as the vehicle travels, and high stability is obtained when the vehicle travels.
- the piston 9 has a substantially disc-like piston main body 61 and a sliding contact member 62 mounted on the outer peripheral surface of the piston main body 61.
- the piston 9 is in sliding contact with the inner peripheral surface of the inner cylinder 2 of the cylinder 4 at the sliding contact member 62.
- An insertion hole 63 is formed in the center of the radial direction of the piston body 61 so as to penetrate in the axial direction.
- the mounting shaft portion 40 of the piston rod 8 is inserted into the insertion hole 63.
- the above flow passages 50 a and 50 b are formed in the piston main body 61 so as to surround the insertion hole 63.
- a valve seat 71 a is formed at an end of the piston body 61 on the side of the chamber 12 in the axial direction.
- the valve seat 71a is formed in an annular shape outside the opening position of one end of the flow passage 50a on the extension side.
- a valve seat 71 b is formed at an end of the piston main body 61 in the axial direction of the chamber 11.
- the valve seat 71b is annularly formed outside the opening position of one end of the compression side flow passage 50b.
- the valve seat 71a constitutes a damping force generating mechanism 51a
- the valve seat 71b constitutes a damping force generating mechanism 51b.
- annular step portion 72b whose height in the axial direction is lower than that of the valve seat 71a is a side opposite to the insertion hole 63 of the valve seat 71a.
- the other end of the flow passage 50b on the contraction side is open at the position of the step portion 72b.
- annular step portion 72a whose height in the axial direction is lower than that of the valve seat 71b.
- the other end of the flow passage 50a on the extension side is open at the position of the step portion 72a.
- the damping force generation mechanism 51a is composed of the above-described valve seat 71a and an annular disc valve 75a that can be seated on the valve seat 71a.
- the disk valve 75a is configured by superposing a plurality of annular single disks.
- an interposed disc 76a having a diameter smaller than that of the disc valve 75a is disposed.
- an annular valve regulating member 77a having a diameter smaller than that of the disc valve 75a is disposed.
- the interposed disk 76a is configured by superimposing a plurality of annular single disks.
- the damping force generation mechanism 51a has a fixed orifice 78a between the valve seat 71a and the disc valve 75a, which allows the flow passage 50a to communicate with the chamber 12 even when they are in contact with each other.
- the fixed orifice 78a is formed by a groove formed in the valve seat 71a or an opening formed in the disc valve 75a.
- the disc valve 75a opens the flow passage 50a by moving away from the valve seat 71a. At this time, the valve restricting member 77a restricts the deformation of the disc valve 75a in the opening direction.
- the damping force generation mechanism 51a is provided in the flow passage 50a, and generates damping force by suppressing the flow of oil generated in the flow passage 50a by the sliding of the piston 9 toward the chamber 11.
- the damping force generation mechanism 51b is composed of the above-described valve seat 71b and an annular disc valve 75b that can be seated on the valve seat 71b.
- the disk valve 75b is also configured by superposing a plurality of annular single disks.
- an interposed disc 76b having a diameter smaller than that of the disc valve 75b is disposed.
- an annular valve regulating member 77b having a diameter smaller than that of the disc valve 75b is disposed.
- the valve regulating member 77 b is in contact with the end face of the main shaft portion 41 of the piston rod 8 on the side of the attachment shaft portion 40.
- the damping force generation mechanism 51b has a fixed orifice 78b between the valve seat 71b and the disc valve 75b.
- the fixed orifice 78b allows the flow passage 50b to communicate with the chamber 11 even when the valve seat 71b and the disc valve 75b are in contact with each other.
- the fixed orifice 78b is formed by a groove formed in the valve seat 71b or an opening formed in the disk valve 75b.
- the disc valve 75b opens the flow passage 50b by moving away from the valve seat 71b. At this time, the valve restricting member 77b restricts the deformation of the disc valve 75b in the opening direction.
- the damping force generation mechanism 51b is provided in the flow passage 50b.
- the damping force generation mechanism 51b suppresses the flow of oil generated in the flow passage 50b by the sliding of the piston 9 toward the chamber 12 to generate damping force.
- the unitary disk closest to the piston main body 61 is cut away at the inner peripheral side.
- the notched portion constitutes an in-disk passage 70.
- An axial passage 200 extending in the axial direction is formed between the mounting shaft portion 40 of the piston rod 8 and the insertion hole 63 of the piston main body 61.
- the in-disk passage 70 keeps the axial passage 200 in communication with the flow passage 50a at all times.
- the communication hole 55 which constitutes the in-rod passage 57 of the piston rod 8 is always in communication with the axial passage 200.
- the piston main body 61 is composed of two, a piston body 201 on the chamber 12 side and a piston body 202 on the chamber 11 side.
- the piston body 201 and the piston body 202 are positioned and integrated in the circumferential direction and the radial direction with each other at an uneven engaging portion (not shown).
- a through hole 211 which constitutes a part of the above-described insertion hole 63 is formed to penetrate in the axial direction at the center in the radial direction.
- a through hole 212 which constitutes a part of the insertion hole 63 is axially penetrated at the center in the radial direction.
- the through hole 212 is smaller in diameter than the through hole 211.
- the mounting shaft portion 40 of the piston rod 8 fits in the through hole 212.
- the axial passage 200 is formed between the mounting shaft portion 40 of the piston rod 8 and the through hole 211 of the piston body 201.
- the annular valve seat 71 a and the step portion 72 b described above are formed on the piston body 201 on the opposite side to the piston body 202.
- the piston body 201 is provided with a disc valve 75a that abuts on the valve seat 71a and an interposed disc 76a.
- One side of the interposed disc 76a abuts on the piston body 201, and the other side abuts on the disc valve 75a.
- the interposing disc 76a has an outer diameter smaller than that of the valve seat 71a.
- the piston body 202 On the piston body 202, on the opposite side to the piston body 201, the annular valve seat 71b and the step portion 72a described above are formed.
- the piston body 202 is provided with a disc valve 75b and an interposed disc 76b that abut on the valve seat 71b.
- One side of the insertion disc 76b abuts on the piston body 202, and the other side abuts on the disc valve 75b.
- the insertion disc 76b has an outer diameter smaller than that of the valve seat 71b.
- the in-rod passage 57 provided in the piston rod 8 is in constant communication with the in-disk passage 70 via the axial passage 200.
- the in-disk passage 70, the axial passage 200, and the in-rod passage 57 are in constant communication with the chamber 11 via the flow passage 50a.
- An external screw 80 is formed on the tip end side of the communication hole 55 of the mounting shaft portion 40 of the piston rod 8.
- a nut 79 and the above-described damping force variable mechanism 58 are screwed into the male screw 80.
- the damping force variable mechanism 58 is a frequency sensitive unit that varies the damping force without being externally controlled by the frequency (vibration state).
- the nut 79 is screwed to the male screw 80, and the valve regulating member 77a, the disc valve 75a, the interposed disc 76a, the piston 9, the interposed disc 76b, the disc valve 75b and the valve regulating member 77b And the end face of the main shaft portion 41 of FIG.
- the damping force variable mechanism 58 is screwed on the male screw 80 until it abuts on the nut 79.
- the damping force variable mechanism 58 is configured of a housing 85 including a lid member 82 and a housing main body 83, a free piston 87, an O-ring 88 which is a rubber member, and an O-ring 89 which is a rubber member.
- the lid member 82 is formed with a female screw 81 screwed to the male screw 80 of the piston rod 8.
- the housing main body 83 has a substantially cylindrical shape, and one end opening side thereof is attached to the lid member 82.
- the free piston 87 is axially movably provided in the housing 85.
- the O-ring 88 is provided between the free piston 87 and the lid member 82 of the housing 85.
- the O-ring 88 is a compression-side elastic body that is compressed and deformed when the free piston 87 moves toward the lid member 82 in the axial direction with respect to the housing 85.
- the O-ring 89 is provided between the free piston 87 and the housing body 83 of the housing 85.
- the O-ring 89 is an extension-side elastic body that is compressed and deformed when the free piston 87 moves to the opposite side to the housing 85.
- O-rings 88 and 89 in the natural state are illustrated for the sake of convenience.
- the O-ring 89 also functions as a seal, it is desirable that the O-ring 89 be disposed so as to always be deformed into a non-circular cross section in the attached state.
- the above-mentioned O-ring 88 is a resistance element which generates a resistance against the displacement of the free piston 87 by compressive deformation when the free piston 87 moves in one direction.
- the O-ring 89 is a resistance element that generates a resistance against the displacement of the free piston 87 by compressive deformation when the free piston 87 moves in the other direction.
- the lid member 82 is made of metal such as iron.
- the lid member 82 is formed mainly of cutting.
- the lid member 82 has a lid inner cylindrical portion 91, a lid substrate portion 92, a lid outer cylindrical portion 93, and a fitting convex portion 94.
- the lid inner cylinder portion 91 has a substantially cylindrical shape, and the above-mentioned female screw 81 is formed on the inner peripheral portion thereof.
- the lid substrate portion 92 is in the form of a perforated disk that extends radially outward from one axial end of the lid inner cylindrical portion 91.
- the lid outer cylinder portion 93 extends from the outer peripheral side of the lid substrate portion 92 in the same direction as the lid inner cylinder portion 91.
- the fitting convex portion 94 has an annular shape that protrudes radially outward from the same side of the lid base portion 92 in the axial direction of the lid outer cylindrical portion 93.
- the fitting convex portion 94 has a tapered surface portion 95 which is gradually reduced in diameter and connected to the lid outer cylinder portion 93 at an end portion on the lid outer cylinder portion 93 side in the axial direction.
- the inner peripheral surface of the lid outer cylindrical portion 93 has a cylindrical surface portion 96 and an inclined surface portion 97 in order from the lid substrate portion 92 side.
- the cylindrical surface portion 96 has a constant diameter.
- the inclined surface portion 97 is connected to the cylindrical surface portion 96.
- the inclined surface portion 97 has an annular shape with a larger diameter as it gets farther from the cylindrical surface portion 96 in the axial direction.
- the inclined surface portion 97 has a substantially arc-shaped cross section in a plane including the central axis of the lid member 82.
- the housing body 83 is made of metal such as iron.
- the housing body 83 is formed mainly of cutting.
- the housing main body 83 has a substantially cylindrical shape.
- the housing main body 83 is formed with an inner annular projection 100 projecting radially inward on one side in the axial direction.
- a small diameter cylindrical surface portion 101, an inclined surface portion 102, a large diameter cylindrical surface portion 103, a tapered surface portion 105, and a fitting cylindrical surface portion 104 are formed on the inner peripheral surface of the housing main body 83 sequentially from one axial direction.
- the small diameter cylindrical surface portion 101 has a constant diameter.
- the inclined surface portion 102 is connected to the small diameter cylindrical surface portion 101.
- the inclined surface portion 102 is formed in an annular shape having a larger diameter as it is separated from the small diameter cylindrical surface portion 101.
- the large diameter cylindrical surface portion 103 is connected to the inclined surface portion 102.
- the large diameter cylindrical surface portion 103 has a constant diameter larger than that of the small diameter cylindrical surface portion 101.
- the tapered surface portion 105 is connected to the large diameter cylindrical surface portion 103.
- the tapered surface portion 105 is tapered such that the diameter increases with distance from the large diameter cylindrical surface portion 103.
- the fitting cylindrical surface portion 104 is connected to the tapered surface portion 105.
- the fitting cylindrical surface portion 104 has a constant diameter larger than that of the large diameter cylindrical surface portion 103.
- the inclined surface portion 102 has a substantially arc-shaped cross section in a plane including the central axis of the housing main body 83.
- the small diameter cylindrical surface portion 101 and the inclined surface portion 102 are formed on the inner annular projection 100.
- the housing main body 83 is described as cylindrical, the inner peripheral surface is desirably circular in cross section, but the outer peripheral surface may be non-circular in cross section such as a polygon.
- Such a housing main body 83 is a fitting convex portion of the lid member 82 on the fitting cylindrical surface portion 104 in a state where the fitting cylindrical surface portion 104 extends to the end opposite to the inner annular projection 100 in the axial direction. 94 is inserted. Then, in a state in which the tapered surface portion 95 of the fitting convex portion 94 is in contact with the tapered surface portion 105, the portion on the opposite side of the annular projection 100 in the axial direction with respect to the fitting convex portion 94 of the housing main body 83 is the radial direction By being bent inward, the housing body 83 and the lid member 82 are integrated into a housing 85.
- the lid outer cylindrical portion 93 of the lid member 82 constitutes an annular small diameter portion which protrudes inward in the radial direction of the large diameter cylindrical surface portion 103 in the housing 85.
- An inclined surface portion 97 is formed on the small diameter portion of the lid outer cylindrical portion 93.
- the inner annular projection 100 of the housing main body 83 constitutes an annular small diameter portion that protrudes radially inward of the large diameter cylindrical surface portion 103 in the housing 85.
- An inclined surface portion 102 is formed on the small diameter portion of the inner annular projection 100.
- the inclined surface portion 97 and the inclined surface portion 102 are disposed so as to axially face each other.
- the free piston 87 is, for example, an integrally molded article formed of a synthetic resin material such as polyacetal. As shown in FIGS. 3 and 4, the free piston 87 has a substantially cylindrical piston cylinder 108 (cylinder) and a curved plate-like piston bottom 109 (bottom). The piston bottom portion 109 is formed to close one end side in the axial direction of the piston cylinder portion 108. An opening 220 is formed on the side opposite to the piston bottom 109 in the axial direction of the piston cylinder 108.
- the free piston 87 has a bottomed cylindrical shape having a piston cylinder 108 and a piston bottom 109.
- the free piston 87 is formed only of a resin material.
- the piston cylindrical portion 108 is formed with an outer annular projecting portion 110 (a projecting portion, a projecting portion) projecting radially outward from the outer peripheral side at an intermediate position in the axial direction.
- the outer annular projecting portion 110 has an annular shape larger in diameter than the tubular portion main body portion 221 excluding the outer annular projecting portion 110 of the piston tubular portion 108 and projecting radially outward.
- the free piston 87 has an outer annular protrusion 110 that protrudes from the outer peripheral side of the piston cylinder 108.
- An end face 222 opposite to the axial opening 220 of the piston cylinder 108 extends in a direction orthogonal to the axis of the piston cylinder 108.
- the end surface 223 on the side of the opening 220 in the axial direction of the piston cylinder 108 also extends in the direction orthogonal to the axis of the piston cylinder 108.
- the inner peripheral surface of the piston cylindrical portion 108 has a cylindrical surface portion 225 on the opposite side of the piston bottom portion 109 to the opening 220, and the cylindrical surface portion 226 on the opening 220 side of the piston bottom portion 109.
- the cylindrical surface portions 225 and 226 are cylindrical surfaces having the same diameter and coaxial diameter.
- the end surfaces 222 and 223 and the cylindrical surface portions 225 and 226 are formed in the cylindrical portion main body portion 221.
- a small diameter cylindrical surface portion 117 and a tapered surface portion 118 are formed.
- the tapered surface portion 112, the small diameter cylindrical surface portion 113, the small diameter cylindrical surface portion 117 and the tapered surface portion 118 are formed in the cylindrical portion main body portion 221.
- the inclined surface portion 114, the large diameter cylindrical surface portion 115 and the inclined surface portion 116 are formed on the outer annular projecting portion 110.
- the tapered surface portion 112 is tapered such that the diameter decreases toward the side opposite to the small diameter cylindrical surface portion 113 in the axial direction.
- the small diameter cylindrical surface portion 113 is connected to the large diameter side of the tapered surface portion 112, and has a constant diameter.
- the inclined surface portion 114 is connected to the small diameter cylindrical surface portion 113.
- the inclined surface portion 114 is formed in an annular shape having a larger diameter as it is separated from the small diameter cylindrical surface portion 113 in the axial direction.
- the large diameter cylindrical surface portion 115 is connected to the large diameter side of the inclined surface portion 114.
- the large diameter cylindrical surface portion 115 has a constant diameter larger than that of the small diameter cylindrical surface portion 113.
- the inclined surface portion 114 has a substantially arc-shaped cross section in a plane including the central axis of the free piston 87.
- the inclined surface portion 116 is connected to the large diameter cylindrical surface portion 115.
- the inclined surface portion 116 has an annular shape with a diameter decreasing with distance from the large diameter cylindrical surface portion 115.
- a small diameter cylindrical surface portion 117 is connected to the small diameter side of the inclined surface portion 116.
- the small diameter cylindrical surface portion 117 has the same diameter as the small diameter cylindrical surface portion 113 and has a constant diameter.
- the tapered surface portion 118 is connected to the small diameter cylindrical surface portion 117.
- the tapered surface portion 118 has a tapered shape in which the diameter decreases toward the side opposite to the small diameter cylindrical surface portion 117 in the axial direction.
- the inclined surface portion 116 has a substantially arc-shaped cross section in a plane including the central axis of the free piston 87.
- the outer annular projection 110 is symmetrical with respect to a plane passing through its axial center position.
- a plurality of passage holes 119 are formed in the free piston 87 at intervals in the circumferential direction of the free piston 87.
- the passage hole 119 is formed at the axial center position of the outer annular protrusion 110.
- the passage hole 119 is formed at the axially central position of the large diameter cylindrical surface portion 115.
- the passage hole 119 radially penetrates the position of the outer annular protrusion 110 in the axial direction of the piston cylinder 108.
- the passage hole 119 has a tapered shape such that the diameter decreases toward the inside in the radial direction of the piston cylinder 108.
- the passage holes 119 are formed at two positions different by 180 degrees in the circumferential direction of the free piston 87.
- the piston bottom portion 109 is spherically curved so as to be separated from the opening 220 in the axial direction toward the radial center side.
- the piston bottom portion 109 is connected to the cylinder portion body portion 221 of the piston cylinder portion 108 to close the inside of the cylinder portion body portion 221, and the opening portion 220 from the radial center position of the bottom portion body portion 231.
- a protrusion 232 projecting to the opposite side.
- the piston bottom portion 109 is spherically curved such that the bottom main portion 231 is separated from the opening 220 in the axial direction toward the center in the radial direction. That is, in the bottom main body portion 231, the bottom surface portion 241 (first bottom surface portion) facing the opening 220 side on the opening 220 side is recessed in a curved surface shape, and the opposite side to the opening 220 is the opening A bottom surface portion 242 (second bottom surface portion) facing the opposite side to the surface 220 protrudes in a curved shape.
- the cylindrical surface portion 225 of the cylindrical portion main body portion 221 extends from the outer peripheral edge portion of the bottom surface portion 242 in the direction opposite to the opening 220.
- the cylindrical surface portion 226 extends in the direction of the opening 220 from the outer peripheral edge of the bottom surface portion 241.
- a molding die 260 for molding the free piston 87 includes a first die 261, a second die 262, and a pin 263, as shown in FIG.
- the molding die 260 has a plurality of pins 263.
- the molding die 260 has a cross section at positions where the pins 263 are present and where they are not. Therefore, only one pin 263 is shown in FIG.
- the first mold 261, the second mold 262, and the plurality of pins 263 are all made of metal.
- the first die 261 has a bottom surface forming surface 242A forming the bottom surface 242 of the free piston 87 shown in FIG. 3, a cylindrical surface forming surface 225A forming the cylindrical surface 225, and an end surface forming surface 222A forming the end surface 222.
- a tapered surface forming surface 112A forming the tapered surface 112, a small diameter cylindrical surface forming surface 113A forming the small diameter cylindrical surface 113, an inclined surface forming surface 114A forming the inclined surface 114, and an inclined surface of the large diameter cylindrical surface 115 It has a large diameter cylindrical surface portion forming surface 115A forming a half on the side 114, and a mating surface 271 with the second mold 262.
- the first mold 261 has a resin material inlet 272 at the center position in the radial direction of the bottom surface forming surface 242A.
- the second die 262 has a bottom surface forming surface 241A forming the bottom surface 241 of the free piston 87, a cylindrical surface forming surface 226A forming the cylindrical surface 226, an end surface forming surface 223A forming the end surface 223, and a tapered surface 118 A tapered surface forming surface 118A forming the small diameter cylindrical surface forming surface 117A forming the small diameter cylindrical surface 117, an inclined surface forming surface 116A forming the inclined surface 116, and a half of the large diameter cylindrical surface 115 on the inclined surface 116 side And a mating surface 275 with the first mold 261.
- the large diameter cylindrical surface portion forming surfaces 115A and 115B have the same diameter and the same axial length.
- the plurality of pins 263 are provided at positions of the mating surfaces 271 and 275 in parallel with the mating surfaces 271 and 275.
- the plurality of pins 263 are movable along the radial direction of the large diameter cylindrical surface portion forming surfaces 115A and 115B.
- the plurality of pins 263 move back and forth between an advanced position in contact with the cylindrical surface forming surface 226A and a retracted position in which the large diameter cylindrical surface forming surfaces 115A and 115B are retracted.
- the plurality of pins 263 are portions forming the plurality of passage holes 119 and have a tapered shape. Specifically, two pins 263 are provided.
- the plurality of pins 263 are disposed at positions different by 180 degrees in the circumferential direction of the large diameter cylindrical surface portion forming surfaces 115A and 115B.
- the molten resin material is filled from the inlet 272 Be done.
- the resin material is filled in the mold 260, and the free piston 87 is integrally molded.
- the joint surfaces 271 and 275 of the first mold 261 and the second mold 262 are separated, and the plurality of pins 263 are retracted to release the free piston 87 from the mold 260.
- the projection 232 of the piston bottom 109 is formed of a resin material in the inlet 272 of the first mold 261.
- the free piston 87 is formed by the molding die 260 as described above, the annular shape shown in FIG. 6 is formed by the mating surfaces 271 and 275 at an axial intermediate position of the large diameter cylindrical surface portion 115.
- the remaining muscle 281 shown is formed.
- the free piston 87 has at the position of the outer annular projection 110 a residual streak 281 which is produced by the molding of the mold 260.
- the remaining muscle 281 and the passage hole 119 are formed at a central position in the axial direction of the large diameter cylindrical surface portion 115. Therefore, the positions of the remaining muscle 281 and the passage hole 119 in the axial direction of the large diameter cylindrical surface portion 115 coincide with each other.
- the free piston 87 is formed with a passage hole 119 penetrating the piston cylinder 108 at the position of the remaining muscle 281.
- the free piston 87 is disposed in the housing 85 such that the piston bottom portion 109 is disposed on the side of the inner annular projection 100 in the axial direction.
- the large diameter cylindrical surface portion 115 axially slides at the position of the large diameter cylindrical surface portion 103 of the housing main body 83.
- the tapered surface portion 112 and the small diameter cylindrical surface portion 113 on one side axially move the position of the small diameter cylindrical surface portion 101 of the housing main body 83.
- the small diameter cylindrical surface portion 117 and the tapered surface portion 118 on the other side axially move the position of the cylindrical surface portion 96 of the lid outer cylinder portion 93 of the lid member 82.
- the inclined surface portion 102 of the housing body 83 and the inclined surface portion 114 of the free piston 87 overlap in position in the radial direction. Therefore, the inclined surface portion 102 of the housing main body 83 and the inclined surface portion 114 of the free piston 87 face each other in the moving direction of the free piston 87.
- the sloped surface portion 97 of the lid outer cylinder portion 93 of the lid member 82 and the sloped surface portion 116 of the free piston 87 overlap in position in these radial directions. Therefore, the inclined surface portion 97 of the lid member 82 and the inclined surface portion 116 of the free piston 87 face each other in the moving direction of the free piston 87.
- an O-ring 89 (the natural state is shown in FIG. 2) is disposed between the small diameter cylindrical surface portion 113 and the inclined surface portion 114 of the free piston 87 and the inclined surface portion 102 and the large diameter cylindrical surface portion 103 of the housing body 83.
- an O-ring 89 is disposed between the outer annular protrusion 110 of the free piston 87 and the inner annular protrusion 100 of the housing 85.
- the free piston 87 has an outer annular projection 110 in which an O-ring 89, which is an elastic body, is provided between the free piston 87 and the housing 85.
- the O-ring 89 has a circular cross section including the central axis.
- the inner diameter is smaller than the small diameter cylindrical surface portion 113 of the free piston 87, and the outer diameter is larger than the large diameter cylindrical surface portion 103 of the housing main body 83. That is, the O-ring 89 is fitted to both the free piston 87 and the housing 85 with these radial interferences.
- an O-ring 88 (the natural state is shown in FIG. 2) is disposed between the large diameter cylindrical surface portion 103 and the inclined surface portion 97 of the housing 85 and the inclined surface portion 116 and the small diameter cylindrical surface portion 117 of the free piston 87. .
- the O-ring 88 is disposed between the outer annular projecting portion 110 of the free piston 87 and the cover outer cylindrical portion 93 of the housing 85.
- the free piston 87 has an outer annular protrusion 110 in which an O-ring 88, which is an elastic body, is provided between the free piston 87 and the housing 85.
- the O-ring 88 When in the natural state, the O-ring 88 has a circular cross section including the central axis.
- the inner diameter is smaller than the small diameter cylindrical surface portion 117 of the free piston 87, and the outer diameter is larger than the large diameter cylindrical surface portion 103 of the housing 85. That is, the O-ring 88 is also fitted to both the free piston 87 and the housing 85 with these radial interferences.
- Both O-rings 88, 89 are common parts of the same size. O-rings 88, 89 bias the free piston 87 within the housing 85 to maintain the housing 85 in a predetermined neutral neutral position relative to the housing 85. At the same time, the O-rings 88 and 89 allow axial movement of the free piston 87 relative to the housing 85 by elastic deformation.
- the O-ring 88 contacts the small diameter cylindrical surface portion 117 and the inclined surface portion 116.
- the inclined surface portion 116 is inclined with respect to the moving direction of the free piston 87.
- the O-ring 88 contacts the large diameter cylindrical surface portion 103 and the inclined surface portion 97.
- the inclined surface portion 97 is inclined with respect to the moving direction of the free piston 87.
- the O-ring 89 contacts the small diameter cylindrical surface portion 113 and the inclined surface portion 114.
- the inclined surface portion 114 is inclined with respect to the moving direction of the free piston 87.
- the O-ring 89 contacts the large diameter cylindrical surface portion 103 and the inclined surface portion 102.
- the inclined surface portion 102 is inclined with respect to the moving direction of the free piston 87.
- the outer annular projecting portion 110 is provided on the outer peripheral portion of the free piston 87, and both axial direction surfaces of the outer annular projecting portion 110 constitute the inclined surface portion 114 and the inclined surface portion 116.
- an inner annular projection 100 having an inclined surface portion 102 and a lid outer cylindrical portion 93 having an inclined surface portion 97 are provided at positions on both sides of the outer annular protrusion 110 on the inner periphery of the housing 85.
- An O-ring 89 is provided between the outer annular protrusion 110 and the inner annular protrusion 100.
- an O-ring 88 is provided between the outer annular projecting portion 110 and the lid outer cylindrical portion 93.
- the O-ring 89 is inserted into the housing body 83 to the position of the inclined surface portion 102. Then, the free piston 87 is fitted to the inside of the housing main body 83 and the O-ring 89. At that time, the large diameter cylindrical surface portion 115 of the free piston 87 is guided to the large diameter cylindrical surface portion 103 of the housing main body 83. Thereafter, the tapered surface portion 112 is inserted into the O-ring 89 and the small diameter cylindrical surface portion 101 of the housing main body 83 from the small diameter side. Next, the O-ring 88 is inserted between the housing body 83 and the free piston 87 to the position of the inclined surface portion 116.
- the damping force variable mechanism 58 thus assembled in advance is attached by screwing a female screw 81 onto the male screw 80 of the mounting shaft portion 40 of the piston rod 8. At that time, the lid substrate portion 92 of the housing 85 abuts on the nut 79.
- the outer diameter of the damping force variable mechanism 58 that is, the outer diameter of the housing 85, is set smaller than the inner diameter of the inner cylinder 2 so as not to cause the flow path resistance.
- an inter-housing passage 121 is formed between the housing 85, the free piston 87, and the O-rings 88 and 89.
- the rod side passage 122 (second passage) is configured.
- the in-disk passage 70 is an orifice. In the rod side passage 122, when the pressure of the chamber 11 rises due to the movement of the piston 9 to the chamber 11 side, the fluid flows out of the chamber 11.
- the communication holes 55 and 56 formed in the piston rod 8 form a flow passage of at least a part of the rod side passage 122 and communicate with the chamber 11 on at least one side of the two chambers 11 and 12.
- the inside of the in-housing passage 121 formed in the housing 85 is a flow passage of at least a part of the rod-side passage 122.
- the in-housing passage 121 includes a rod chamber side passage portion 123 communicating with the chamber 11 on the piston rod 8 side by the O ring 89, the free piston 87 and the housing 85, and a bottom chamber side passage portion communicating with the chamber 12 on the bottom side. And 124 are defined.
- the rod chamber side passage portion 123 is composed of a chamber 125, a passage hole 119 and a chamber 126.
- the chamber 125 is surrounded by the lid member 82, the free piston 87 and the O-ring 88, and the in-rod passage 57 is opened.
- the passage hole 119 is formed in the free piston 87, and one end opens in the chamber 125.
- the chamber 126 is surrounded by the housing body 83, the O-ring 88, the O-ring 89, and the free piston 87, and the other end of the passage hole 119 is open.
- the bottom chamber side passage portion 124 is constituted of a portion surrounded by the inner annular protrusion 100 side of the housing main body 83, the O ring 89 and the free piston 87.
- the free piston 87 has a cylindrical shape, and an outer annular protrusion 110 including an annular large-diameter cylindrical surface 115 is formed on the outer periphery, and a chamber 12 which has a high pressure in the axial direction from the outer annular protrusion 110 in its inside.
- the piston bottom portion 109 is formed on the side.
- the free piston 87 is provided with a passage hole 119 for communicating between the chamber 126 between the annular O-rings 88 and 89 and the chamber 125 on the side of the chamber 11 which becomes high pressure during the extension stroke in the free piston 87. ing.
- one O-ring 89 provided between the free piston 87 and the housing 85 is the inclined surface portion 114 of the outer annular projecting portion 110 located between the O-rings 88 and 89 on the outer periphery of the free piston 87. It abuts on the inclined surface portion 102 of the inner annular projection 100 on the inner peripheral portion of the housing 85, and is elastically deformed by being sandwiched therebetween. That is, this one O-ring 89 generates an elastic force against the movement of the free piston 87 to one side in the extension stroke.
- the free piston 87 moves toward the lid member 82 in the axial direction with respect to the housing 85 while injecting oil into the bottom chamber side passage portion 124.
- the other O-ring 88 provided between the free piston 87 and the housing 85 is the inclined surface portion 116 of the outer annular projecting portion 110 of the outer periphery of the free piston 87 and the lid of the inner periphery of the housing 85 It abuts on the inclined surface portion 97 of the outer cylindrical portion 93, and is sandwiched between them to be elastically deformed. That is, the other O-ring 88 generates an elastic force against the movement of the free piston 87 to the other in the compression stroke.
- the bottom surface portion 241 on the side of the chamber 11 which is high in expansion stroke in the chambers 11 and 12 is concaved in a curved surface shape, and the chamber 12 on the side of the chamber 12 which is high in compression stroke
- the bottom portion 242 protrudes in a curved shape.
- the bottom surface portion 241 opposed to the rod chamber side passage portion 123 communicating with the chamber 11 which becomes high pressure in the extension stroke among the chambers 11 and 12 is concaved in a curved surface.
- a bottom surface portion 242 facing the chamber 12 which is high in pressure in a stroke projects in a curved shape.
- the free piston 87 moves, the O-ring 89, the free piston 87, and the housing 85 define the rod chamber side passage portion 123 and the bottom chamber side passage portion 124. Therefore, the free piston 87 moves the flow passage 50a on the upstream side of the oil flow when the piston 9 moves in one direction in the extension stroke of the rod side passage 122, the in-disk passage 70, the axial passage 200, and the inside of the rod.
- a passage 57, a rod chamber side passage portion 123, and a downstream bottom chamber side passage portion 124 are defined.
- the free piston 87 is provided with a bottom chamber side passage portion 124 on the upstream side and a rod chamber side passage portion 123 on the downstream side, in the flow of oil when the piston 9 moves in the other direction in the compression stroke.
- An in-rod passage 57, an axial passage 200, an in-disk passage 70 and a flow passage 50a are defined.
- the oil introduced from the chamber 11 into the flow passage 50a basically forms a normally open opening formed between the valve seat 71a and the disc valve 75a that abuts on the valve seat 71a.
- the oil introduced from the chamber 11 into the flow passage 50a basically passes between the disk valve 75a and the valve seat 71a while opening the disk valve 75a, and the chamber 12 Flow to For this reason, a damping force of valve characteristics (the damping force is approximately proportional to the piston speed) is generated.
- the fluid flows from the chamber 12 to the chamber 11 via the flow passage 50b.
- the oil introduced from the chamber 12 into the flow passage 50b basically forms a normally-opened opening formed between the valve seat 71b and the disc valve 75b abutting on the valve seat 71b.
- the oil introduced from the chamber 12 into the flow passage 50b basically passes between the disc valve 75b and the valve seat 71b while opening the disc valve 75b. It flows into the room 11. For this reason, a damping force of valve characteristics (the damping force is approximately proportional to the piston speed) is generated.
- the piston speed when the piston speed is low, that is, a region where the frequency in a very low speed region (for example, 0.05 m / s) is relatively high (for example, 7 Hz or more) is a vibration generated from, for example, surface irregularities of the road surface. In such situations it is preferable to lower the damping force.
- the region where the frequency is relatively low is vibration such as shaking by the roll of the vehicle body, contrary to the above. It is preferable to raise
- the above-mentioned damping force variable mechanism 58 makes the damping force variable according to the frequency even when the piston speed is similarly low. That is, when the piston speed is low, if the frequency of reciprocation of the piston 9 becomes high, the pressure of the chamber 11 becomes high in the extension stroke, and the flow passage 50a and the in-disk passage 70 of the rod side passage 122 While the hydraulic fluid is introduced from the chamber 11 to the rod chamber side passage portion 123 of the in-housing passage 121 of the damping force variable mechanism 58 via the directional passage 200 and the in-rod passage 57, the free piston 87 is on the axial chamber 12 side.
- the housing 85 is moved to the side of the chamber 12 in the axial direction against the biasing force of the O-ring 89.
- the free piston 87 moves to the chamber 12 side in the axial direction to introduce oil from the chamber 11 into the passage 121 in the housing, introduce it from the chamber 11 into the flow passage 50a, and pass through the damping force generating mechanism 51a.
- the flow rate of the fluid flowing into the chamber 12 is reduced. This reduces the damping force.
- the amount of oil flowing into the damping force variable mechanism 58 is controlled by the throttling effect of the in-disk passage 70.
- the pressure in the chamber 12 is increased, so that the damping force is variable via the rod inner passage 57, the axial passage 200, the disk inner passage 70, and the flow passage 50a of the rod side passage 122.
- the free piston 87 which has been moved to the chamber 12 side in the axial direction is discharged to the chamber 11 side in the axial direction while discharging oil from the rod chamber side passage portion 123 of the in-housing passage 121 of the mechanism 58 to the chamber 11
- the housing 85 is moved toward the chamber 11 in the axial direction against the biasing force of the O-ring 88.
- the free piston 87 moves to the side of the chamber 11 in the axial direction to enlarge the volume of the chamber 12, and is introduced from the chamber 12 into the flow passage 50b and passes through the damping force generating mechanism 51b to flow into the chamber 11.
- the flow rate of the fluid is reduced. This reduces the damping force.
- the amount of oil discharged from the damping force variable mechanism 58 is controlled by the throttling effect of the in-disk passage 70.
- the frequency of movement of the free piston 87 also follows and increases.
- the oil flows from the chamber 11 to the rod chamber side passage portion 123 of the passage 121 in the housing at each extension stroke, and the volume of the chamber 12 is expanded by the movement of the free piston 87 at each compression stroke. And the damping force is maintained in the lowered state.
- the free piston 87 compresses the O-ring 88 to axially move the housing 85 thereafter. Stop on the side of the chamber 11 and the volume of the chamber 12 is not affected. Therefore, the flow rate of the oil introduced into the flow passage 50b from the chamber 12 and flowing through the damping force generation mechanism 51b to the chamber 11 does not decrease, and the damping force becomes high.
- the free piston 87 shown in FIG. 7 is longer in axial length than the free piston 87 shown in FIG. 3.
- the width of the outer annular projecting portion 110 that is, the axial length of the large diameter cylindrical surface portion 115 is longer than that of the free piston 87 shown in FIG.
- the axial length of the cylindrical surface portion 226 is also long. Therefore, the widths of the outer annular projecting portion 110 of the plurality of types of free pistons 87 are different, and are distinguishable by this width.
- the one in which the free piston 87 having a long axial length is incorporated has a larger volume of the rod chamber side passage portion 123 than the one in which the free piston 87 having a short axial length is incorporated.
- the colors of the resin materials themselves which are the materials forming the plurality of free pistons 87 having different axial lengths, are also different, and the colors are different for each type.
- the plurality of types of free pistons 87 are distinguishable by color. By forming the free piston 87 with a resin material, the color can be easily made different for each type by making the color of the resin material different.
- the free piston of the kind chosen from a plurality of free pistons 87 in which the width of outside annular projection part 110 differs for every kind as mentioned above 87 is incorporated into the housing 85 and manufactured.
- the housing 85 is formed with the free piston 87 of the type selected from the plurality of types of free pistons 87 different in color depending on the types. It incorporates and manufactures.
- the plurality of types of free pistons 87 can be identified by the width of the outer annular projecting portion 110 in the state before being incorporated into the housing 85.
- the piston bottom portion 109 and the piston cylindrical portion 108 are mounted not only in the housing 85 but also in a state in which the outer annular protrusion 110 is covered with the housing 85, as well as the plurality of types of free pistons 87.
- the piston bottom portion 109 side is exposed inside the inner annular projection 100 of the housing body 83. Therefore, the type can be identified by the color on the piston bottom 109 and the piston bottom 109 side of the piston cylinder 108.
- the shock absorber described in Patent Document 1 has a damping force variable mechanism that makes the damping force characteristic variable according to the vibration state.
- a damping force variable mechanism that makes the damping force characteristic variable according to the vibration state.
- a free piston is provided in the housing, and the damping force is made variable by reciprocating the free piston according to the frequency of reciprocating motion of the piston.
- metal such as iron.
- the shock absorber 1 since the free piston 87 reciprocating by the damping force variable mechanism 58 is formed of a resin material, the weight can be reduced. Therefore, the reduction in weight reduces the inertial force acting on the free piston, so that the resonance frequency of the free piston 87 can be increased, so that the generation of abnormal noise caused by the resonance of the free piston 87 can be suppressed.
- the damping force variable mechanism 58 abuts against the base valve 18 at the stroke end of the shock absorber 1
- the free piston 87 made of a resin material abuts against the rivet 35 first, thereby suppressing the striking sound generated. be able to.
- the bottom surface portion 241 on the side of the chamber 11 which becomes high in the expansion stroke of the chambers 11 and 12 is concavely curved.
- a bottom surface portion 242 on the side of the chamber 12 at which the pressure is high is projected in a curved shape.
- the extension side damping force is set larger than the compression side damping force. Therefore, the pressure difference between the chambers 11 and 12 is larger in the extension stroke than in the contraction stroke.
- the bottom surface portion 241 on the side of the chamber 11 on the high pressure side in the extension stroke where the pressure difference between the chambers 11 and 12 is large is recessed in a curved surface
- the bottom portion 242 on the side of the chamber 12 protrudes in a curved shape. Therefore, the thickness can be reduced while securing the strength.
- the weight of the free piston 87 can be further reduced.
- the free piston 87 is provided with a passage hole 119 to guide the pressure on the side of the chamber 11 between the O-ring 88 and the O-ring 89.
- the pressure on the outer peripheral side of the free piston 87 is the pressure of the chamber 11 at the upper side in the drawing and the pressure of the chamber 12 at the lower side in the drawing at the O-ring 89 as a boundary.
- the axial position of the piston bottom portion 109 of the free piston 87 is the inner periphery of the O-ring 89.
- the rigidity since the pressure on the upper side of the free piston 87 above the O-ring 89 is substantially equal to that on the inner side, the rigidity may be low.
- the piston bottom portion 109 is provided at a position where a pressure difference occurs on the inside and the outside, the rigidity against the pressure difference is high on the inside and the outside, so that it is possible to reduce the overall thickness.
- the free piston 87 has the remaining streaks 281 generated by the first mold 261 and the second mold 262 of the mold 260 at the position of the outer annular projecting portion 110 protruding from the outer peripheral side of the piston cylinder 108 Even if the remaining muscle 281 is not removed, the O-rings 88 and 89 are not affected. Thus, the manufacturing cost can be reduced.
- the free piston 87 has a passage hole 119 penetrating the piston cylinder 108 at the position of the residual streak 281 generated by the mold split of the molding die 260.
- the pin 263 can be provided at the position of the mating surface 271, 275 of the first mold 261 and the second mold 262, and the passage hole 119 can be formed by the mold 260 at the time of injection molding of the free piston 87.
- the manufacturing cost can be reduced.
- the shock absorber 1 is manufactured by incorporating the free piston 87 of the type selected from among the plurality of types of free pistons 87 different in color according to types. Therefore, the plurality of free pistons 87 can be identified by color. Therefore, it is possible to suppress erroneous incorporation of the free piston 87 into the housing 85, and to easily check whether or not the assembly is proper after the incorporation.
- the free piston 87 of the type selected from among the plurality of types of free pistons 87 different in the width of the outer annular projecting portion 110 for each type is incorporated in the housing 85
- multiple types of free pistons 87 can be identified by the width of the outer annular projection 110.
- the shock absorber according to the first aspect of the above embodiment is provided with a cylinder in which the working fluid is enclosed, and slidably fitted in the cylinder, and the cylinder is partitioned into two chambers, one side chamber and the other side chamber.
- a second passage communicating with one of the two chambers, a damping force generating mechanism provided in the first passage for generating a damping force, and a flow passage of at least a part of the second passage are formed.
- a bottomed cylindrical free piston having a cylindrical portion and a bottom portion, which defines the passage on the upstream side and the downstream side of the flow of the working fluid when the piston moves in one direction, the free piston and the housing And an elastic body provided between the two.
- the free piston is formed of a resin material.
- the first bottom face on the one side chamber side where the high pressure is applied in the extension stroke is recessed in a curved surface shape, and the other side chamber side where the high pressure is applied in the compression stroke
- the second bottom surface portion of the second projection projects in a curved shape.
- the free piston is cylindrical, and an annular convex portion is formed on the outer periphery, and a compression stroke is performed in the axial direction from the annular convex portion inside
- the bottom portion is formed on the other side chamber side where high pressure is applied
- the annular elastic members are respectively provided on both sides in the axial direction of the annular convex portion on the outer periphery of the free piston, and the free piston Through holes are provided to communicate between the annular elastic bodies and one side chamber side where the high pressure is generated in the extension stroke in the free piston.
- the free piston has a protrusion which protrudes from the outer peripheral side of the cylindrical portion and the elastic body is provided between the free piston and the housing.
- the apparatus is characterized in that it has remaining streaks generated by mold splitting of the mold at the position of the protrusion.
- a fifth aspect is characterized in that in the fourth aspect, the free piston is formed with a through hole that penetrates the cylindrical portion at the position of the remaining muscle.
- a sixth aspect is the method of manufacturing the shock absorber according to the fourth or fifth aspect, wherein the type of free piston selected from among the plurality of types of free pistons in which the width of the protrusion differs for each type A piston is incorporated into the housing and manufactured.
- a seventh aspect is the method of manufacturing the shock absorber according to any one of the first to sixth aspects, wherein a free piston of a type selected from among the plurality of types of free pistons different in color according to types is provided. Are incorporated into the housing and manufactured.
- shock absorber According to the above-described shock absorber, the generation of abnormal noise can be suppressed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
本願は、2017年7月26日に、日本に出願された特願2017-144245号に基づき優先権を主張し、その内容をここに援用する。
シール部材16は、その内周部で、軸方向に移動するピストンロッド8の外周部に摺接して、内筒2内の油液と外筒3内のリザーバ室5の高圧ガスおよび油液とが外部に漏洩するのを防止する。摩擦部材17は、その内周部でピストンロッド8の外周部に摺接して、ピストンロッド8に摩擦抵抗を発生させる。なお、摩擦部材17は、シールを目的とするものではない。
ピストン9には、流通路50aと流通路50bとが同数ずつ形成されている。
連通穴56は、連通穴55に連通し取付軸部40の先端部に開口している。これら連通穴55,56が、ピストンロッド8に設けられるロッド内通路57を構成している。
上記シリンダ4とピストンロッド8との間には、車輪が発生する振動の他に、車両の走行に伴って車体に発生する慣性力や遠心力も作用する。例えばハンドル操作により走行方向が変化することにより車体に遠心力が発生し、この遠心力に基づく力が上記シリンダ4とピストンロッド8との間に作用する。以下で説明する通り、本実施形態の緩衝器1は車両の走行に伴って車体に発生する力に基づく振動に対して良好な特性を有しており、車両の走行時における高い安定性が得られる。
固定オリフィス78aは、弁座71aに形成された溝あるいはディスクバルブ75aに形成された開口によって形成されている。ディスクバルブ75aは、弁座71aから離座することで流通路50aを開放する。その際に、バルブ規制部材77aがディスクバルブ75aの開方向への規定以上の変形を規制する。減衰力発生機構51aは、流通路50aに設けられ、ピストン9の室11側への摺動によって流通路50aに生じる油液の流れを抑制して減衰力を発生させる。
固定オリフィス78bは、弁座71bに形成された溝あるいはディスクバルブ75bに形成された開口によって形成されている。ディスクバルブ75bは、弁座71bから離座することで流通路50bを開放する。その際に、バルブ規制部材77bがディスクバルブ75bの開方向への規定以上の変形を規制する。減衰力発生機構51bは、流通路50bに設けられる。減衰力発生機構51bは、ピストン9の室12側への摺動によって流通路50bに生じる油液の流れを抑制して減衰力を発生させる。
傾斜面部102は、小径円筒面部101に繋がっている。傾斜面部102は、小径円筒面部101から離れるほど大径となる円環状となっている。大径円筒面部103は、傾斜面部102に繋がっている。大径円筒面部103は、小径円筒面部101より大径の一定径をなしている。テーパ面部105は、大径円筒面部103に繋がっている。テーパ面部105は、大径円筒面部103から離れるほど大径となるテーパ状となっている。嵌合円筒面部104は、テーパ面部105に繋がっている。嵌合円筒面部104は、大径円筒面部103より大径の一定径をなしている。傾斜面部102はハウジング本体83の中心軸線を含む面での断面が略円弧状をなしている。小径円筒面部101と傾斜面部102とは、内側環状突起100に形成されている。なお、ハウジング本体83を円筒状と記述しているが、内周面は断面円形となることが望ましいが、外周面は、多角形等、断面非円形であってもよい。
複数のピン263は、具体的には2本設けられている。複数のピン263は、大径円筒面部形成面115A,115Bの周方向において180度異なる位置に配置されている。
また、ハウジング85の内周における、外側環状突出部110の両側の位置に、傾斜面部102を有する内側環状突起100と、傾斜面部97を有する蓋外筒部93とを設けている。外側環状突出部110と、内側環状突起100との間にOリング89を設けている。また、外側環状突出部110と、蓋外筒部93との間にOリング88を設けている。
減衰力可変機構58の外径つまりハウジング85の外径は、内筒2の内径よりも流路抵抗とならない程度に小さく設定されている。
通路穴119は、フリーピストン87に形成されており、室125に一端が開口する。室126は、ハウジング本体83とOリング88とOリング89とフリーピストン87とで囲まれており、通路穴119の他端が開口する。ボトム室側通路部124は、ハウジング本体83の内側環状突起100側とOリング89とフリーピストン87とで囲まれた部分から構成されている。
フリーピストン87は、円筒状で、外周に環状の大径円筒面部115を含む外側環状突出部110が形成され、その内部に、外側環状突出部110より軸方向において縮み行程で高圧となる室12側にピストン底部109が形成された形状である。フリーピストン87の外周の外側環状突出部110の軸方向両側に、それぞれ環状の弾性体であるOリング88,89が設けられている。フリーピストン87には、それぞれ環状のOリング88,89の間の室126と、フリーピストン87内の伸び行程で高圧となる室11側の室125との間を連通する通路穴119が設けられている。
その際にも、ディスク内通路70の絞り効果により減衰力可変機構58から排出される油液の量がコントロールされる。
また、フリーピストン87には通路穴119が設けられ、Oリング88とOリング89との間に室11側の圧力を導いている。このため、フリーピストン87の外周側の圧力はOリング89を境に、図中上側が室11の圧力、図中下側が室12の圧力となっている。ここで、フリーピストン87のピストン底部109の軸方向位置は、Oリング89の内周となっている。このため、フリーピストン87のOリング89より上側は、内側と外側が略同圧力となるので、剛性が低くてもよい。また、内側と外側に圧力差が生じる位置には、ピストン底部109が設けられるので、内側と外側に圧力差対する剛性が高いので、全体に薄肉化が可能となる。
4 シリンダ
8 ピストンロッド
9 ピストン
11 室(一側室)
12 室(他側室)
50a 流通路(第1通路,第2通路の一部)
51a 減衰力発生機構
55,56 連通穴
85 ハウジング
87 フリーピストン
88,89 Oリング(弾性体)
108 ピストン筒部(筒部)
109 ピストン底部(底部)
110 外側環状突出部(突出部)
119 通路穴(貫通穴)
122 ロッド側通路(第2通路)
241 底面部(第1底面部)
242 底面部(第2底面部)
281 残存筋
Claims (7)
- 作動流体が封入されるシリンダと、
前記シリンダ内に摺動可能に嵌装され、該シリンダ内を一側室および他側室の二室に区画するピストンと、
前記ピストンに連結されると共に前記シリンダの外部に延出されるピストンロッドと、
前記ピストンが一方向に移動したときに前記シリンダ内の一方の室から作動流体が流れ出す第1通路と、
前記二室のうちの一方の室に連通される第2通路と、
前記第1通路に設けられ減衰力を発生する減衰力発生機構と、
前記第2通路の少なくとも一部の流路が形成され、少なくとも一側室と連通する前記ピストンロッドに形成される連通穴と、
内部に前記第2通路の少なくとも一部の流路が形成されるハウジングと、
前記ハウジング内に移動可能に設けられ前記第2通路を前記ピストンが一方向に移動したときの作動流体の流れの上流側と下流側とに画成する、筒部および底部を有する有底筒状のフリーピストンと、
前記フリーピストンと前記ハウジングとの間に設けられる弾性体と、
を備え、
前記フリーピストンが樹脂材料により形成されている
緩衝器。 - 前記フリーピストンの底部は、伸び行程で高圧となる一側室側の第1底面部が曲面状に凹み、縮み行程で高圧となる他側室側の第2底面部が曲面状に突出している
請求項1記載の緩衝器。 - 前記フリーピストンは、円筒状で、外周に環状の凸部が形成され、内部に前記環状の凸部より軸方向において縮み行程で高圧となる他側室側に前記底部が形成された形状であり、前記フリーピストンの外周の前記環状の凸部の軸方向両側にそれぞれ環状の前記弾性体を設け、前記フリーピストンには、前記それぞれ環状の前記弾性体の間と前記フリーピストン内の伸び行程で高圧となる一側室側との間を連通する貫通穴が設けられている
請求項1または2に記載の緩衝器。 - 前記フリーピストンは、前記筒部の外周側から突出すると共に前記弾性体が前記ハウジングとの間に設けられる突出部を有しており、
前記突出部の位置に成形型の型割により生じる残存筋を有する
請求項1または2に記載の緩衝器。 - 前記フリーピストンは、前記残存筋の位置に前記筒部を貫通する貫通穴が形成されている
請求項4記載の緩衝器。 - 請求項4または5記載の緩衝器の製造方法であって、
種類毎に前記突出部の幅が異なる複数種類の前記フリーピストンの中から選択された種類のフリーピストンを前記ハウジングに組み込んで製造する
緩衝器の製造方法。 - 請求項1乃至6のいずれか一項記載の緩衝器の製造方法であって、
種類毎に色が異なる複数種類の前記フリーピストンの中から選択された種類のフリーピストンを前記ハウジングに組み込んで製造する
緩衝器の製造方法。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112018003791.6T DE112018003791T5 (de) | 2017-07-26 | 2018-07-09 | Stoßdämpfer und Verfahren zur Herstellung desselben |
CN201880049572.5A CN110945263A (zh) | 2017-07-26 | 2018-07-09 | 缓冲器及其制造方法 |
JP2019532483A JP6942185B2 (ja) | 2017-07-26 | 2018-07-09 | 緩衝器およびその製造方法 |
US16/630,890 US11796029B2 (en) | 2017-07-26 | 2018-07-09 | Shock absorber and method of manufacturing the same |
KR1020207002101A KR102462159B1 (ko) | 2017-07-26 | 2018-07-09 | 완충기 및 그 제조 방법 |
MX2020000551A MX2020000551A (es) | 2017-07-26 | 2018-07-09 | Amortiguador y metodo de fabricacion del mismo. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2017144245 | 2017-07-26 | ||
JP2017-144245 | 2017-07-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2019021797A1 true WO2019021797A1 (ja) | 2019-01-31 |
Family
ID=65040522
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2018/025874 WO2019021797A1 (ja) | 2017-07-26 | 2018-07-09 | 緩衝器およびその製造方法 |
Country Status (8)
Country | Link |
---|---|
US (1) | US11796029B2 (ja) |
JP (1) | JP6942185B2 (ja) |
KR (1) | KR102462159B1 (ja) |
CN (1) | CN110945263A (ja) |
CZ (1) | CZ309536B6 (ja) |
DE (1) | DE112018003791T5 (ja) |
MX (1) | MX2020000551A (ja) |
WO (1) | WO2019021797A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11293510B2 (en) * | 2019-05-09 | 2022-04-05 | Schaeffler Technologies AG & Co. KG | Rolling element spring |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7250400B2 (ja) | 2019-02-28 | 2023-04-03 | エルジー・ケム・リミテッド | 新規な化合物およびこれを利用した有機発光素子 |
JP2020197239A (ja) * | 2019-05-31 | 2020-12-10 | デルタ工業株式会社 | ダンパー及びシートサスペンション機構 |
US12025205B2 (en) * | 2021-04-22 | 2024-07-02 | DRiV Automotive Inc. | Hydraulic rebound stop pressure relief system |
CN114738422B (zh) * | 2022-03-18 | 2023-10-13 | 北京京西重工有限公司 | 阻尼器组件及用于阻尼器组件的活塞 |
DE102022106595A1 (de) * | 2022-03-21 | 2023-09-21 | Betterguards Technology Gmbh | Vorrichtung zur Stabilisierung von Körpergelenken und/oder zur Unterstützung von Sportgeräten |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011202801A (ja) * | 2010-03-03 | 2011-10-13 | Hitachi Automotive Systems Ltd | 緩衝器 |
JP2015021602A (ja) * | 2013-07-23 | 2015-02-02 | カヤバ工業株式会社 | 緩衝装置 |
Family Cites Families (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3540683A (en) * | 1967-11-07 | 1970-11-17 | Lockheed Aircraft Corp | Dual air chambered shock strut |
NL7108318A (ja) | 1970-07-04 | 1972-01-06 | ||
JPS5531134B2 (ja) | 1972-03-09 | 1980-08-15 | ||
US3991863A (en) * | 1973-06-22 | 1976-11-16 | Integrated Dynamics Incorporated | Metering shock absorber with manual adjustment |
JPS589801B2 (ja) | 1976-02-19 | 1983-02-23 | 川崎製鉄株式会社 | 低酸素、低炭素鉄系粉末の製造方法 |
JPS592341Y2 (ja) | 1979-06-27 | 1984-01-23 | カヤバ工業株式会社 | ガス封入式シヨツクアブソ−バのフリ−ピストン |
DE3027742A1 (de) * | 1980-07-22 | 1982-02-04 | Metzeler Kautschuk GmbH, 8000 München | Zweikammer-motorlager mit hydraulischer daempfung |
DE3826931A1 (de) | 1988-08-09 | 1990-02-22 | Kaco Gmbh Co | Kolbendichtung |
US6220409B1 (en) * | 1999-05-06 | 2001-04-24 | Tenneco Automotive Inc. | Stroke dependent bypass |
US20030015382A1 (en) * | 2001-07-20 | 2003-01-23 | Delphi Technologies, Inc. | Hydraulic rebound cut-off for monotube damper |
JP4402449B2 (ja) * | 2003-12-25 | 2010-01-20 | 日立オートモティブシステムズ株式会社 | 油圧緩衝器 |
KR101165057B1 (ko) * | 2008-04-08 | 2012-07-12 | 주식회사 만도 | 차량의 현가 시스템 |
US8065055B2 (en) | 2007-11-21 | 2011-11-22 | Mando Corporation | Shock absorber for controlling damping force characteristics |
DE102011012730B4 (de) * | 2010-03-02 | 2021-04-29 | Hitachi Automotive Systems, Ltd. | Stoßdämpfer |
US8746423B2 (en) | 2010-03-02 | 2014-06-10 | Hitachi Automotive Systems, Ltd. | Shock absorber |
JP5639865B2 (ja) | 2010-03-02 | 2014-12-10 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP5809801B2 (ja) | 2010-12-28 | 2015-11-11 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
DE102010050868B4 (de) * | 2010-11-09 | 2013-09-26 | Gkn Sinter Metals Holding Gmbh | Herstellung mehrteiliger, gefügter Ventilbauteile in hydraulischen Anwendungen mit Fügedichtprofilen |
JP5783771B2 (ja) * | 2011-03-31 | 2015-09-24 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP5793346B2 (ja) * | 2011-05-31 | 2015-10-14 | 日立オートモティブシステムズ株式会社 | シリンダ装置 |
KR101254287B1 (ko) | 2011-06-09 | 2013-04-12 | 주식회사 만도 | 가변유로를 갖는 쇽업소버의 밸브 구조 |
JP5894874B2 (ja) | 2012-06-29 | 2016-03-30 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
KR101594211B1 (ko) | 2012-08-14 | 2016-02-15 | 주식회사 만도 | 쇽 업소버의 밸브 조립체 |
JP2014092181A (ja) | 2012-10-31 | 2014-05-19 | Showa Corp | 圧力緩衝装置 |
US9062734B2 (en) * | 2013-02-25 | 2015-06-23 | Hitachi Automotive Systems, Ltd. | Shock absorber and vehicle using the same |
JP2014163512A (ja) | 2013-02-28 | 2014-09-08 | Kayaba Ind Co Ltd | ダンパ |
JP2015068439A (ja) * | 2013-09-30 | 2015-04-13 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP2017144245A (ja) | 2017-02-22 | 2017-08-24 | 株式会社イグチ | 炊飯用ネット |
-
2018
- 2018-07-09 MX MX2020000551A patent/MX2020000551A/es unknown
- 2018-07-09 WO PCT/JP2018/025874 patent/WO2019021797A1/ja active Application Filing
- 2018-07-09 CZ CZ2020-18A patent/CZ309536B6/cs unknown
- 2018-07-09 KR KR1020207002101A patent/KR102462159B1/ko active IP Right Grant
- 2018-07-09 US US16/630,890 patent/US11796029B2/en active Active
- 2018-07-09 DE DE112018003791.6T patent/DE112018003791T5/de active Pending
- 2018-07-09 CN CN201880049572.5A patent/CN110945263A/zh active Pending
- 2018-07-09 JP JP2019532483A patent/JP6942185B2/ja active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011202801A (ja) * | 2010-03-03 | 2011-10-13 | Hitachi Automotive Systems Ltd | 緩衝器 |
JP2015021602A (ja) * | 2013-07-23 | 2015-02-02 | カヤバ工業株式会社 | 緩衝装置 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11293510B2 (en) * | 2019-05-09 | 2022-04-05 | Schaeffler Technologies AG & Co. KG | Rolling element spring |
Also Published As
Publication number | Publication date |
---|---|
KR20200021512A (ko) | 2020-02-28 |
MX2020000551A (es) | 2020-09-10 |
JP6942185B2 (ja) | 2021-09-29 |
CZ309536B6 (cs) | 2023-03-29 |
US20200149608A1 (en) | 2020-05-14 |
KR102462159B1 (ko) | 2022-11-01 |
CN110945263A (zh) | 2020-03-31 |
JPWO2019021797A1 (ja) | 2020-04-23 |
US11796029B2 (en) | 2023-10-24 |
DE112018003791T5 (de) | 2020-04-23 |
CZ202018A3 (cs) | 2020-05-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2019021797A1 (ja) | 緩衝器およびその製造方法 | |
US9139065B2 (en) | Shock absorber | |
US9868331B2 (en) | Shock absorber | |
JP6838220B2 (ja) | 緩衝器 | |
US9062734B2 (en) | Shock absorber and vehicle using the same | |
JP6838768B2 (ja) | 緩衝器 | |
US10012283B2 (en) | Shock absorber and vehicle using the same | |
US11078982B2 (en) | Damper | |
US12038063B2 (en) | Shock absorber | |
CN112771284A (zh) | 缓冲器 | |
JP7206174B2 (ja) | 緩衝器 | |
JP7109293B2 (ja) | 緩衝器 | |
JP5894874B2 (ja) | 緩衝器 | |
JP6803924B2 (ja) | 緩衝器 | |
WO2016194548A1 (ja) | 緩衝器 | |
US20240151290A1 (en) | Shock absorber and frequency sensitive mechanism | |
US20230272835A1 (en) | Shock absorber | |
WO2021240936A1 (ja) | 緩衝器の製造方法および緩衝器 | |
JP7129937B2 (ja) | 緩衝器 | |
JP2023039001A (ja) | 緩衝器 | |
JP2013204779A (ja) | 緩衝器 | |
JP2022143217A (ja) | シリンダ装置 | |
JP2020159391A (ja) | 緩衝器 | |
JP5639882B2 (ja) | 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: 18839458 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2019532483 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 20207002101 Country of ref document: KR Kind code of ref document: A |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 18839458 Country of ref document: EP Kind code of ref document: A1 |