WO2014148599A1 - 緩衝装置 - Google Patents
緩衝装置 Download PDFInfo
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- WO2014148599A1 WO2014148599A1 PCT/JP2014/057711 JP2014057711W WO2014148599A1 WO 2014148599 A1 WO2014148599 A1 WO 2014148599A1 JP 2014057711 W JP2014057711 W JP 2014057711W WO 2014148599 A1 WO2014148599 A1 WO 2014148599A1
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- WIPO (PCT)
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- chamber
- pressure
- free piston
- shock absorber
- piston
- Prior art date
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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
- B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
- B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
- B60G15/061—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper with a coil spring being mounted inside the damper
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
- F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—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
- F16F9/187—Bitubular units with uni-directional flow of damping fluid through the valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—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
- F16F9/5165—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 by use of spherical valve elements or like free-moving bodies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
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- 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
- B60G2202/10—Type of spring
- B60G2202/12—Wound spring
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- 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
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- 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
- B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
- B60G2204/424—Mechanisms for force adjustment, e.g. constant force mechanisms
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- 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
- B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
- B60G2204/45—Stops limiting travel
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
- B60G2600/18—Automatic control means
- B60G2600/182—Active control means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
- B60G2600/44—Vibration noise suppression
Definitions
- the present invention relates to a shock absorber.
- a shock absorber As a conventional shock absorber, a cylinder, a piston slidably inserted into the cylinder, a piston rod inserted into the cylinder and connected to the piston, an extension side chamber and a pressure side chamber defined by the piston in the cylinder
- An intermediate cylinder that covers the outer periphery of the cylinder and forms a discharge passage with the cylinder, an outer cylinder that covers the outer periphery of the intermediate cylinder and forms a reservoir with the intermediate cylinder, and an operation toward the pressure side chamber from the reservoir
- a suction passage that allows only an oil flow
- a rectification passage that is provided in the piston and that allows only a flow of hydraulic oil from the pressure side chamber to the extension side chamber, and a damping force variable valve provided between the discharge passage and the reservoir.
- a solenoid is used to adjust the damping force with the damping force variable valve.
- the thrust that the solenoid gives to the pilot valve body that controls the valve opening pressure of the damping force variable valve the resistance that the damping force variable valve gives to the flow of hydraulic oil is adjusted.
- a damping force adjusting unit capable of changing the resistance applied to the flow of liquid, a housing having a pressure chamber therein, and slidably inserted into the pressure chamber.
- a free piston that forms an expansion side pressure chamber and a pressure side pressure chamber in the pressure chamber, and a biasing force that positions the free piston at a neutral position in the pressure chamber and suppresses displacement from the neutral position of the free piston.
- a spring element wherein the extension side chamber communicates with the extension side pressure chamber so as to press the free piston in one of the sliding directions, and the compression side pressure presses the free piston in the other of the sliding directions.
- the pressure receiving area of the free piston on which the pressure side chamber communicates with the chamber and the pressure of the pressure side pressure chamber acts is larger than the pressure receiving area of the free piston on which the pressure of the expansion side pressure chamber acts.
- the shock absorber D1 further includes a piston rod 21 having one end 21a connected to the piston 1 and the other end (upper end side in FIG. 1) protruding to the outside of the cylinder 1.
- the piston rod 21 is slidably supported by an annular rod guide 8 that seals the upper end of the cylinder 1.
- a bottom member 11, a cylinder 1, an intermediate cylinder 9, a rod guide 8, and a seal member 12 are accommodated in the outer cylinder 10, and the upper end of the outer cylinder 10 in FIG.
- the bottom member 11, the cylinder 1, the intermediate cylinder 9, the rod guide 8, and the seal member 12 are sandwiched between 10 a and the bottom portion 10 b of the outer cylinder 10, and these are fixed to the outer cylinder 10.
- the bottom member 11, the cylinder 1, the intermediate cylinder 9, the rod guide 8, and the seal member 12 are sandwiched between a cap screwed to the outer cylinder 10 and the bottom portion 10 b. It may be.
- the shock absorber D1 When the shock absorber D1 is contracted, the piston 2 moves downward in FIG. 1 to compress the compression side chamber R2, and the hydraulic oil in the compression side chamber R2 flows to the expansion side chamber R1 through the rectifying passage 4. At the time of this contraction operation, the piston rod 21 enters the cylinder 1, so that the hydraulic oil corresponding to the rod entry volume becomes excessive in the cylinder 1, and the excess hydraulic oil is pushed out of the cylinder 1 and is discharged to the reservoir R through the discharge passage 7. Discharged.
- the shock absorber D1 applies a resistance to the hydraulic oil flowing through the discharge passage 7 and flowing to the reservoir R by the damping force variable valve V, thereby increasing the pressure in the cylinder 1 and exerting a compression side damping force.
- the free piston 5 is formed in a stepped shape.
- the small piston portion 5b of the free piston 5 is erected from the lower end in FIG. 1 of the base portion 5a, is formed in a cylindrical shape, and is slidably inserted into the small cross-sectional area portion 14a.
- the large piston portion 5c is erected from the outer periphery of the upper end in FIG. 1 of the base portion 5a, is formed in a cylindrical shape, and is slidably inserted into the large cross-sectional area portion 14b.
- the free piston 5 moves in the pressure chamber 14 in the axial direction of the shock absorber D1.
- the free piston 5 is sandwiched from both the upper and lower sides by the compression side spring 6a and the extension side spring 6b, and is positioned at a predetermined neutral position in the pressure chamber 14.
- the neutral position does not indicate the center of the pressure chamber 14 in the axial direction but is a position where the free piston 5 is positioned by the spring element 6.
- the free piston 5 is set to be larger than the expansion side pressure receiving area B1 of the free piston 5 on which the acting pressure acts 5 can be operated to function as an apparent flow path.
- the amplitude of the input vibration is small and the amplitude of the piston 2 is small.
- the flow rate discharged from the cylinder 1 to the reservoir R is small and the amplitude of the free piston 5 is also small, the urging force that the free piston 5 receives from the spring element 6 is small. Therefore, regardless of whether the shock absorber D1 is in the expansion stroke or the contraction stroke, the ratio of the flow rate that passes through the pressure chamber 14 that functions as an apparent flow path with respect to the flow rate that passes through the damping force variable valve V is low. More than during frequency oscillation. Therefore, the damping force generated by the shock absorber D1 is reduced.
- the damping characteristic of the shock absorber D1 changes as shown in FIG.
- Each solid line in FIG. 2 shows the damping characteristics when the damping force on the expansion side and the compression side of the shock absorber D1 is set to soft, medium, and hard by the damping force variable valve V, and the broken line indicates soft, medium, and hard
- the damping characteristic is set, the characteristic when the damping force is reduced by inputting high frequency vibration to the shock absorber D1 is shown.
- the change of the damping force can be made to depend on the input vibration frequency, and a high damping force is applied to the input of the low frequency vibration in the resonance frequency band of the sprung member of the vehicle. Occurrence can stabilize the posture of the vehicle body (sprung member) and prevent the passenger from feeling uneasy when the vehicle turns.
- a low damping force is always generated to transmit the vibration on the wheel side (unsprung member side) to the vehicle body side (sprung member side). Insulation can improve the ride comfort in the vehicle.
- the shock absorbing device D1 it is possible to suppress the occurrence of the hitting sound of the free piston 5 and the bottom member 11 and to prevent a sudden change in the damping force, thereby improving the riding comfort in the vehicle.
- the frequency band for reducing the damping force includes the pressure side pressure receiving area A1, the extension side pressure receiving area B1, and the pressure receiving area C1 of the free piston 5, the flow path resistance of the passage 18, the pressure side passage 19, and the orifice passage 20, and the spring element 6.
- the spring constant (the combined spring constant of the compression side spring 6a and the extension side spring 6b) can be arbitrarily determined. Therefore, instead of or in addition to the orifice passage 20, one or both of the passage 18 and the pressure side passage 19 may be used as the orifice passage, and if it is not necessary to provide the orifice passage, all the passages 18, 19 and 20 may not be provided with an orifice.
- the passages 18, 19, and 20 may be provided with a choke throttle instead of an orifice.
- the extension side cushion 5 f is not disposed in the outer peripheral chamber 17, but instead of the base portion 5 a of the free piston 5. It may be provided on the lower end surface and disposed in the small piston portion 5b, or may be disposed on the lower end surface of the small piston portion 5b and disposed in the small chamber 15. Further, the compression side cushion 5e and the extension side cushion 5f are provided not on the free piston 5 but on the bottom member 11, and when the free piston 5 is displaced to the vicinity of the stroke end, the compression side cushion 5e and the extension side cushion 5f are brought into contact with the free piston 5. May be.
- the case member 22 is a substantially columnar member having a hollow portion 22a inside, and has three step portions on the outer periphery. The three steps are formed with a diameter reduced stepwise upward in FIG.
- the outer circumference of the first stage is fitted to the inner circumferential surface of the cylinder 1
- the outer circumference of the third stage is fitted to the inner circumferential surface of the intermediate cylinder 9, and the outer diameter of the lower end is larger than the inner diameter of the intermediate cylinder 9.
- a seal ring 24 is attached to the outer peripheral surface of the third stage, and the seal ring 24 prevents the discharge passage 7 and the reservoir R from communicating with each other through the outer periphery of the case member 22.
- the lower end portion of the case member 22 is formed in a cylindrical shape, and a plurality of notches 22b that communicate between the inside and the outside are formed at the lower end portion.
- the free piston 5, the compression side spring 6a, and the extension side spring 6b are accommodated in the hollow portion 22a of the case member 22.
- the compression side spring 6a and the extension side spring 6b are compressed, and the free piston 5 is positioned at the neutral position.
- FIG. 4 shows a modification of the first embodiment.
- the inner periphery of the cylindrical portion at the tip of the case member 22 is press-fitted into the lid member 23, and an annular groove 23 d that communicates with the port 23 c is formed in the lid member 23.
- the change of the damping force can be made to depend on the input vibration frequency, and a high damping force is generated for the input of the low frequency vibration in the resonance frequency band of the sprung member of the vehicle. It is possible to stabilize the posture of the (sprung member) and prevent the passenger from feeling uneasy when the vehicle turns.
- a low damping force is always generated to transmit the vibration on the wheel side (unsprung member side) to the vehicle body side (sprung member side). Insulation can improve the ride comfort in the vehicle.
- the extension side spring 6b can be a gas spring.
- the outer peripheral chamber 17 is open to the atmosphere or air chamber, it is not necessary to connect the outer peripheral chamber 17 to the reservoir R, so the bottom member 11 forming the pressure chamber 14 is fixed to the piston rod 21 or the piston It can also be provided in the rod 21.
- the pressure chamber 14 can be completely accommodated in the shock absorber D2 and gas mixing from the outer peripheral chamber 17 into the small chamber 15 or the large chamber 16 can be prevented. There are benefits.
- the bolt 38 is inserted into the bolt insertion hole 33d.
- the bolt 38 includes a shaft portion 38a having a screw portion at the tip, and a head portion 38b having a larger diameter than the shaft portion 38a.
- a disc-shaped check valve 39 is mounted on the outer periphery of the shaft portion 38 a of the bolt 38.
- the check valve 39 is fixed to the lid member 33 by a nut 40 that is screwed to a screw portion formed on the bolt 38 and the shaft portion 38a, and opens and closes the port 33c.
- the inside of the pressure chamber 36 is divided into a small chamber 15, a large chamber 16, and an outer peripheral chamber 17 by the free piston 5.
- the small chamber 15 communicates with the expansion side chamber R1 through the orifice passage 34, the through hole 33i, and the discharge passage 7.
- the large chamber 16 communicates with the pressure side chamber R2 through the groove 38c and the passage 38d of the bolt 38. It communicates with the reservoir R through the through hole 35 and the notch 33j. Since the through hole 35 opens to the stepped portion 32b, the communication between the outer peripheral chamber 17 and the reservoir R is not interrupted until the free piston 5 is completely in close contact with the stepped portion 32b.
- the pressure chambers 14, 25, and 36 are formed so that the free piston 5 can move in the vertical direction in the figure.
- the pressure chambers 14, 25, and 36 can be formed so that the free piston 5 can move in the horizontal direction and the diagonal direction, not in the vertical direction in the figure.
- D2 can be made less susceptible to vertical vibrations.
- the pressure chambers 14, 25, and 36 so that the free piston 5 can move in the vertical direction in the figure, it is easy to secure the stroke amount of the free piston 5 and a large free piston 5 can be adopted. it can.
- the compression side cushion 51 may be interposed between the compression side spring 6a and the lid member 23 and fixed to the bottom member 11. That is, the compression side cushion 51 is fixed to one of the free piston 5 and the bottom member 11 by the compression side spring 6a.
- the compression side cushion 51 is fixed using the compression side spring 6a, there exists an advantage that the fixation by welding or adhesion
- the cushion member 60 is a rubber member that penetrates the base portion 5a of the free piston 5.
- the cushion member 60 according to the modification shown in FIG. Hereinafter, the cushion member 60 will be described in detail.
- the upper end portion 60a of the cushion member 60 is hemispherical and protrudes toward the large chamber 16 so as to be opposed to the lower surface of the head portion 26b of the bolt 26 to constitute a compression side cushion.
- the lower end portion 60b of the cushion member 60 is hemispherical, protrudes toward the small chamber 15 and is provided to face the bottom portion of the pressure chamber 25, and constitutes an extension side cushion.
- the expansion side cushion 70 is fitted and fixed to the small cross-sectional area 25a formed on the case member 22 and is laminated on the bottom surface of the small cross-sectional area 25a, and the small chamber of the small piston portion 5b which is the side surface of the small chamber of the free piston 5. 15 is opposed to the end face (the lower end face in FIG. 8) facing 15.
- the compression side cushion 71 is fitted and fixed in an annular recess 25d provided at the open end of the hollow portion of the case member 22, and is an end surface facing the large chamber 16 of the large piston portion 5c that is the large chamber side surface of the free piston 5. (Upper end surface in FIG. 8).
- the stretch side cushion 70 and the compression side cushion 71 may be, for example, a rubber ring made of a resin such as rubber, or may be a wave washer. Further, one of the extension side cushion 70 and the pressure side cushion 71 may be a wave washer and the other may be a rubber ring. Moreover, the cross-sectional shape of the extension side cushion 70 and the compression side cushion 71 is arbitrary, and various shapes can be adopted in addition to the square ring and the O-ring.
- the shock absorber provided with the expansion side cushion 70 and the pressure side cushion 71, the collision between the free piston 5 and the bottom member 11 can be prevented, as in the case of the shock absorber D1, to generate the hitting sound of both. While being able to suppress, the sudden change of damping force can be prevented and the riding comfort in a vehicle can be improved.
- the extension side cushion 70 and the compression side cushion 71 are also applicable to the shock absorber D2.
- the shock absorber it is possible to suppress the occurrence of the hitting sound of the free piston 5 and the bottom member 11 and to prevent a sudden change in the damping force, and to improve the riding comfort in the vehicle. . *
- the shock absorber D3 will be described with reference to FIG. Below, it demonstrates centering on a different point from the buffering device D1 shown in FIG.
- the flow passage area may be decreased immediately after the free piston 5 is displaced from the neutral position by setting it to 0, or from the neutral position of the free piston 5 where the variable throttle valve starts to decrease the flow passage area. May be set to be different on both sides in the moving direction of the free piston 5.
- the free piston 5 moves upward in FIG. 10 as described in the first embodiment.
- the variable throttle valve as the hydraulic cushion mechanism L decreases the flow path area, so that the hydraulic oil does not easily flow into the outer circumferential chamber 17.
- the free piston 5 and the bottom member 11 are prevented from colliding vigorously, and the hitting sound when they come into contact with each other can be reduced.
- the shock absorber D3 when the shock absorber D3 is contracted, the free piston 5 moves downward in FIG. 10 as described in the first embodiment. At this time, if the free piston 5 is displaced by a predetermined amount or more from the neutral position, the variable throttle valve as the hydraulic cushion mechanism L decreases the flow path area, so that it is difficult for the hydraulic oil to be discharged from the outer peripheral chamber 17. 5 is decelerated, and the free piston 5 and the bottom member 11 are prevented from colliding vigorously, so that the hitting sound when they come into contact with each other can be reduced.
- the shock absorbing device D3 it is possible to suppress the occurrence of the hitting sound of the free piston 5 and the bottom member 11 and to prevent a sudden change in the damping force, thereby improving the riding comfort in the vehicle.
- the frequency band for reducing the damping force includes the pressure side pressure receiving area A1, the expansion side pressure receiving area B1, and the pressure receiving area C1 of the free piston 5, and the flow path of the variable throttle valve as the passage 18, the pressure side passage 19, and the hydraulic cushion mechanism L. It can be arbitrarily determined by setting the resistance and the spring constant of the spring element 6 (the combined spring constant of the compression side spring 6a and the extension side spring 6b). Therefore, instead of the hydraulic cushion mechanism L or in addition to the hydraulic cushion mechanism L, a variable throttle valve may be provided in one or both of the passage 18 and the pressure side passage 19.
- the orifice passage 20 includes a first orifice passage 20a that opens to the outer periphery of the second step from the front end side of the case member 22 and leads to the vicinity of the step portion 25c on the inner periphery of the large cross-sectional area portion 25b, and the front end side of the case member 22 And a second orifice passage 20b that opens to the outer periphery of the second stage and communicates with the inner periphery of the large cross-sectional area portion 25b.
- the small chamber 15 communicates with the reservoir R through the passage 22d of the case member 22, and the large chamber 16 communicates with the pressure side chamber R2 through the passage 26d of the bolt 26.
- the outer peripheral chamber 17 communicates with the expansion side chamber R1 through the first orifice passage 20a and the discharge passage 7, and in the state where the annular groove 5h faces the second orifice passage 20b, the hole 5i, the annular groove 5h, and the second orifice passage. 20b and the discharge passage 7 are also communicated with the extension side chamber R1. Therefore, in the shock absorber D3 shown in FIG.
- the flow area may be decreased as soon as the free piston 5 is displaced from the neutral position by setting it to 0, and the variable throttle valve starts to decrease the flow area from the neutral position of the free piston 5.
- the amount of displacement may be set so as to be different on both sides in the moving direction of the free piston 5.
- the frequency band for reducing the damping force includes the pressure side pressure receiving area A2, the extension side pressure receiving area B2, and the pressure receiving area C2 of the free piston 5, the pressure side passage 19, the passage 31, and the variable throttle valve as the hydraulic cushion mechanism L1.
- the spring constant of the spring element 6 (the combined spring constant of the compression side spring 6a and the extension side spring 6b) can be arbitrarily determined. Therefore, instead of the hydraulic cushion mechanism L1, or in addition to the hydraulic cushion mechanism L1, a variable throttle valve may be provided in one or both of the pressure side passage 19 and the passage 31.
- the hydraulic pressure cushion mechanism restricts the flow passage area of the pressure side passage, and the free piston 5 moves from the neutral position to the small chamber.
- the compression side passage restriction portion is constituted by the compression side plunger 80
- the expansion side passage restriction portion is constituted by the expansion side plunger 81.
- the shock absorber D5 when the free piston 5 is displaced from the neutral position in the pressure direction or the extending direction by a predetermined amount or more, the moving speed of the free piston 5 can be reduced, and the free piston 5 and the bottom member 11 are vigorously moved. Since the collision can be prevented, the hitting sound caused by the collision between the free piston 5 and the bottom member 11 is reduced, so that the vehicle occupant is not uncomfortable or uneasy. Further, since the free piston 5 does not stop suddenly, the damping force reducing effect is not suddenly lost, and the damping force generated by the shock absorber D5 does not change suddenly. Either the pressure side passage restriction portion or the extension side passage restriction portion may constitute the hydraulic cushion mechanism L2 or may be used in combination with the hydraulic cushion mechanism L1.
- the shock absorber D6 when the free piston 5 is displaced from the neutral position in the pressure direction or the extending direction by a predetermined amount or more, the moving speed of the free piston 5 can be reduced, and the free piston 5 and the bottom member 11 are vigorously moved. Since the collision can be prevented, the hitting sound caused by the collision between the free piston 5 and the bottom member 11 is reduced, so that the vehicle occupant is not uncomfortable or uneasy. Further, since the free piston 5 does not stop suddenly, the damping force reducing effect is not suddenly lost, and the damping force generated by the shock absorber D6 does not change suddenly.
- the pressure side passage restriction portion of the shock absorber D6 can also be used in combination with the extension side passage restriction portion and the hydraulic cushion mechanisms L and L1 of the shock absorber D5.
- the compression side cushion chamber 90 and the extension side cushion chamber 91 may be formed by other than the above structure, and the compression side cushion chamber 90 is closed by the free piston 5 when the free piston 5 is displaced by a predetermined amount or more in the pressure direction.
- the side cushion chamber 91 may have any structure as long as it is configured to be closed by the free piston 5 when the free piston 5 is displaced by a predetermined amount or more in the extending direction.
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Abstract
Description
まず、本発明の第1実施形態に係る緩衝装置D1について説明する。
図5に第2実施形態に係る緩衝装置D2を示す。
次に、本発明の第3実施形態に係る緩衝装置D3について説明する。以下では、上記第1及び第2実施形態と同様の構成には図中に同一の符号を付して詳しい説明は省略し、第1及び第2実施形態と異なる点を中心に説明する。
図13に第4実施形態に係る緩衝装置D4を示す。
Claims (18)
- 緩衝装置であって、
液体が封入されたシリンダと、
前記シリンダ内に摺動自在に挿入され前記シリンダ内を伸側室と圧側室に区画するピストンと、
一端が前記ピストンに連結され、他端が前記シリンダの外部へと突出するピストンロッドと、
前記シリンダに対する前記ピストンロッドの進入及び退出に伴う前記シリンダ内の容積変化の補償を行うリザーバと、
前記リザーバから前記圧側室へと向かう液体の流れのみを許容する吸込通路と、
前記圧側室から前記伸側室へ向かう液体の流れのみを許容する整流通路と、
前記伸側室から前記リザーバへ向かう液体の流れのみを許容するとともに液体の流れに与える抵抗を変更可能な減衰力調整部と、
内部に圧力室を有するハウジングと、
前記圧力室内に摺動自在に挿入され、前記圧力室内に伸側圧力室と圧側圧力室を形成するフリーピストンと、
前記フリーピストンを前記圧力室内で中立位置に位置決めすると共に前記フリーピストンの中立位置からの変位を抑制する付勢力を発揮するばね要素と、を備え、
前記フリーピストンを摺動方向の一方に押圧するよう前記伸側圧力室に前記伸側室が連通すると共に、前記フリーピストンを摺動方向の他方に押圧するよう前記圧側圧力室に前記圧側室が連通し、
前記圧側圧力室の圧力が作用する前記フリーピストンの受圧面積は、前記伸側圧力室の圧力が作用する前記フリーピストンの受圧面積よりも大きい緩衝装置。 - 請求項1に記載の緩衝装置であって、
前記フリーピストンは、前記圧力室の小断面積部内に摺動自在に挿入される小ピストン部と、前記圧力室の大断面積部内に摺動自在に挿入される大ピストン部と、を備え、
前記小断面積部内に前記小ピストン部にて小室が区画され、前記大断面積部内であって前記小ピストン部の外周に外周室が区画され、前記大断面積部内に前記大ピストン部にて大室が区画され、
前記小室及び前記外周室の一方が前記伸側圧力室であり、前記大室が前記圧側圧力室である緩衝装置。 - 請求項2に記載の緩衝装置であって、
前記小室及び前記外周室の他方は前記リザーバに連通する緩衝装置。 - 請求項1に記載の緩衝装置であって、
前記シリンダの外側に設けられた外筒と、
前記シリンダと前記外筒との間に設けられた中間筒と、
前記シリンダと前記中間筒との間に形成され、前記伸側室と前記リザーバとを連通する排出通路と、をさらに備え、
前記ハウジングは、前記シリンダと前記中間筒の端部に嵌合して設けられ、
前記リザーバは、前記中間筒と前記外筒との間に形成され、
前記減衰力調整部は、前記排出通路と前記リザーバとの間に設けられ、
前記伸側室は、前記排出通路を通じて前記伸側圧力室に連通する緩衝装置。 - 請求項4に記載の緩衝装置であって、
前記ハウジングは、
前記フリーピストンが上下方向に移動可能に挿入される中空部を有するケース部材と、
前記ケース部材の前記中空部を閉塞して前記圧力室を形成する蓋部材と、を備える緩衝装置。 - 請求項1に記載の緩衝装置であって、
前記ハウジングへの前記フリーピストンの衝突を防止するクッション部材をさらに備える緩衝装置。 - 請求項6に記載の緩衝装置であって、
前記フリーピストンは、前記圧力室の小断面積部内に摺動自在に挿入される小ピストン部と、前記圧力室の大断面積部内に摺動自在に挿入される大ピストン部と、を備え、
前記小断面積部内に前記小ピストン部にて小室が区画され、前記大断面積部内であって前記小ピストン部の外周に外周室が区画され、前記大断面積部内に前記大ピストン部にて大室が区画され、
前記小室及び前記外周室の一方が前記伸側圧力室であり、前記大室が前記圧側圧力室であり、
前記クッション部材は、
前記フリーピストンが前記小室を圧縮する方向へ移動する際における前記フリーピストンの前記ハウジングへの衝突を防止する伸側クッションと、
前記フリーピストンが前記大室を圧縮する方向へ移動する際における前記フリーピストンの前記ハウジングへの衝突を防止する圧側クッションと、を備える緩衝装置。 - 請求項7に記載の緩衝装置であって、
前記ばね要素は、前記小室内に収容されて前記フリーピストンと前記ハウジングとの間に介装される伸側ばねと、前記大室内に収容されて前記フリーピストンと前記ハウジングとの間に介装される圧側ばねと、を備え、
前記伸側クッションは、前記伸側ばねによって前記フリーピストン及び前記ハウジングの一方に固定され、前記圧側クッションは、前記圧側ばねによって前記フリーピストン及び前記ハウジングの一方に固定される緩衝装置。 - 請求項7に記載の緩衝装置であって、
前記フリーピストンを貫通するゴム部材をさらに備え、
前記ゴム部材の小室側端が前記伸側クッションであり、前記ゴム部材の大室側端が前記圧側クッションである緩衝装置。 - 請求項7に記載の緩衝装置であって、
前記伸側クッションは、前記ハウジングに固定されて前記フリーピストンの前記小室側面に対向する環状の第一弾性体であり、
前記圧側クッションは、前記ハウジングに固定されて前記フリーピストンの前記大室側面に対向する環状の第二弾性体である緩衝装置。 - 請求項10に記載の緩衝装置であって、
前記第一弾性体及び前記第二弾性体は、ウェーブワッシャ又はゴムリングである緩衝装置。 - 請求項1に記載の緩衝装置であって、 前記ハウジングへの前記フリーピストンの衝突を抑制する液圧クッション機構をさらに備える緩衝装置。
- 請求項12に記載の緩衝装置であって、
前記フリーピストンは、前記圧力室の小断面積部内に摺動自在に挿入される小ピストン部と、前記圧力室の大断面積部内に摺動自在に挿入される大ピストン部と、を備え、
前記小断面積部内に前記小ピストン部にて小室が区画され、前記大断面積部内であって前記小ピストン部の外周に外周室が区画され、前記大断面積部内に前記大ピストン部にて大室が区画され、
前記小室及び前記外周室の一方が前記伸側圧力室であり、前記大室が前記圧側圧力室であり、
前記伸側圧力室と前記伸側室とを連通する伸側通路と、
前記圧側圧力室と前記圧側室とを連通する圧側通路と、をさらに備え、
前記液圧クッション機構は、前記フリーピストンの変位によって前記伸側通路及び前記圧側通路の一方又は両方の流路面積を減じる可変絞り弁である緩衝装置。 - 請求項12に記載の緩衝装置であって、
前記フリーピストンは、前記圧力室の小断面積部内に摺動自在に挿入される小ピストン部と、前記圧力室の大断面積部内に摺動自在に挿入される大ピストン部と、を備え、
前記小断面積部内に前記小ピストン部にて小室が区画され、前記大断面積部内であって前記小ピストン部の外周に外周室が区画され、前記大断面積部内に前記大ピストン部にて大室が区画され、
前記小室及び前記外周室の一方が前記伸側圧力室であり、前記大室が前記圧側圧力室であり、
前記伸側圧力室と前記伸側室とを連通する伸側通路と、
前記圧側圧力室と前記圧側室とを連通する圧側通路と、をさらに備え、
前記液圧クッション機構は、前記フリーピストンが中立位置から前記大室を圧縮する圧方向へ所定量以上変位すると前記圧側通路の流路面積を減少させる圧側通路制限部と、前記フリーピストンが中立位置から前記小室を圧縮する伸方向へ所定量以上変位すると前記伸側通路の流路面積を減少させる伸側通路制限部と、を備える緩衝装置。 - 請求項14に記載の緩衝装置であって、
前記伸側通路制限部は、前記フリーピストンに設けられて前記伸側通路内に進入可能な伸側プランジャを備え、前記フリーピストンが中立位置から前記伸方向へ所定量以上変位すると前記伸側プランジャが前記伸側通路へ進入して前記伸側通路の流路面積を減少させる緩衝装置。 - 請求項14に記載の緩衝装置であって、
前記圧側通路制限部は、前記フリーピストンに設けられて前記圧側通路内に進入可能な圧側プランジャを備え、前記フリーピストンが中立位置から前記圧方向へ所定量以上変位すると前記圧側プランジャが前記圧側通路へ進入して前記圧側通路の流路面積を減少させる緩衝装置。 - 請求項14に記載の緩衝装置であって、
前記ハウジングは、前記大室へ臨む環状壁を備え、
前記圧側通路は、前記環状壁内を通じて前記圧側室へ連通し、
前記圧側通路制限部は、前記フリーピストンの前記大室側に形成され内部への前記環状壁の進入を許容する環状突起を備え、
前記フリーピストンが中立位置から前記大室を圧縮する圧方向へ所定量以上変位すると前記環状壁が前記環状突起内に進入して前記圧側通路の流路面積を減少させる緩衝装置。 - 請求項12に記載の緩衝装置であって、
前記液圧クッション機構は、前記フリーピストンが中立位置から前記大室を圧縮する圧方向へ所定量以上変位すると前記フリーピストンによって閉鎖されて前記フリーピストンのそれ以上の変位を抑制する圧側クッション室と、
前記フリーピストンが中立位置から前記小室を圧縮する伸方向へ所定量以上変位すると前記フリーピストンによって閉鎖されて前記フリーピストンのそれ以上の変位を抑制する伸側クッション室と、を備える緩衝装置。
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Also Published As
Publication number | Publication date |
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US9840123B2 (en) | 2017-12-12 |
CN105051404B (zh) | 2016-11-02 |
EP2977643A4 (en) | 2017-01-25 |
US20160288605A1 (en) | 2016-10-06 |
KR101728266B1 (ko) | 2017-04-18 |
EP2977643B1 (en) | 2018-09-26 |
KR20150121085A (ko) | 2015-10-28 |
CN105051404A (zh) | 2015-11-11 |
EP2977643A1 (en) | 2016-01-27 |
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