WO2020100793A1 - Amortisseur - Google Patents

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Publication number
WO2020100793A1
WO2020100793A1 PCT/JP2019/044068 JP2019044068W WO2020100793A1 WO 2020100793 A1 WO2020100793 A1 WO 2020100793A1 JP 2019044068 W JP2019044068 W JP 2019044068W WO 2020100793 A1 WO2020100793 A1 WO 2020100793A1
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WO
WIPO (PCT)
Prior art keywords
shock absorber
spring
throttle
liquid
main body
Prior art date
Application number
PCT/JP2019/044068
Other languages
English (en)
Japanese (ja)
Inventor
森　健
Original Assignee
Ｋｙｂモーターサイクルサスペンション株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2018214455A external-priority patent/JP2020085000A/ja
Priority claimed from JP2018214453A external-priority patent/JP2020084998A/ja
Priority claimed from JP2018214454A external-priority patent/JP7198053B2/ja
Application filed by Ｋｙｂモーターサイクルサスペンション株式会社 filed Critical Ｋｙｂモーターサイクルサスペンション株式会社
Publication of WO2020100793A1 publication Critical patent/WO2020100793A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
    • B62K25/00—Axle suspensions
    • B62K25/04—Axle suspensions for mounting axles resiliently on cycle frame or fork
    • B62K25/06—Axle suspensions for mounting axles resiliently on cycle frame or fork with telescopic fork, e.g. including auxiliary rocking arms
    • B62K25/08—Axle suspensions for mounting axles resiliently on cycle frame or fork with telescopic fork, e.g. including auxiliary rocking arms for front wheel

Definitions

  • the present invention relates to improvement of a shock absorber.
  • a shock absorber main body that exerts a main damping force and a tube member provided on the outer periphery thereof serve as a suspension spring.
  • the coil spring and the upper end of the coil spring is supported by a spring receiver provided on the outer circumference of the shock absorber body.
  • a liquid storage chamber that is formed between the shock absorber main body and the tube member and stores the liquid is vertically partitioned by a spring receiver, and when the liquid passes through the spring receiver, There is one that applies a resistance to the flow of the liquid to secondarily generate a damping force due to the resistance (for example, Patent Document 1).
  • the secondary damping force described above is a position-dependent damping force generated in a predetermined stroke region where the liquid passes through the spring receiver. Then, in the predetermined stroke region, the position-dependent damping force is added to the main damping force, and the damping force of the shock absorber as a whole can be increased.
  • the position-dependent damping force may change unintentionally. Furthermore, when trying to adjust the position-dependent damping force, the inner diameter of the coil at the upper end of the coil spring must be changed, which is complicated.
  • an object of the present invention is to provide a shock absorber that can easily obtain a desired position-dependent damping force.
  • a shock absorber that solves the above problems divides a liquid storage chamber formed between a shock absorber main body and a tube member around the shock absorber main body into an upper chamber and a lower chamber, and a flow path that connects them is provided in the shock absorber main body.
  • a coil spring housed in the lower chamber and having an upper end supported by the spring receiver.
  • the spring receiver has an annular throttle portion located below the opening on the upper chamber side in the flow path and forming a restriction passage between the shock absorber body and the shock absorber body, the restriction passage providing resistance to the flow of the liquid.
  • the inner diameter of the portion is smaller than the inner diameter of the coil at the upper end of the coil spring.
  • the position-dependent damping force due to the resistance of the restriction passage can be generated in a predetermined stroke region where the liquid passes through the spring receiver.
  • the position-dependent damping force can be prevented from being dominated by the resistance when the liquid passes between the upper end of the coil spring and the shock absorber body.
  • the position-dependent damping force can be adjusted in magnitude by changing the inner diameter of the throttle portion, it is not necessary to change the coil inner diameter at the upper end of the coil spring when adjusting the position-dependent damping force.
  • a main body part having a tubular spring mount mounted on the outer periphery of the main shock absorber body, a spring seat fitted to the lower end of the main body part and abutting the upper end of the coil spring, and the main body part and the spring.
  • a diaphragm member provided between the seat and the seat, and the diaphragm member may be a diaphragm portion.
  • the throttle portion is movable in the radial direction, when the shock absorber bends due to a lateral force from the outside, the throttle portion interferes with the shock absorber body and the shock absorber body is damaged. Can be suppressed.
  • the restriction passage may be a choke passage.
  • FIG. 1 is a partially cutaway front view of a shock absorber according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged vertical sectional view showing a part of FIG. 1 in an enlarged manner.
  • FIG. 3 is a partially enlarged vertical sectional view showing a first modified example of the spring bearing of the shock absorber according to the embodiment of the present invention, in which a changed portion thereof is enlarged.
  • FIG. 4 is a partially enlarged vertical cross-sectional view showing a second modified example of the spring bearing of the shock absorber according to the embodiment of the present invention, in which a changed portion is enlarged.
  • FIG. 1 is a partially cutaway front view of a shock absorber according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged vertical sectional view showing a part of FIG. 1 in an enlarged manner.
  • FIG. 3 is a partially enlarged vertical sectional view showing a first modified example of the spring bearing of the shock absorber according to the embodiment of the present invention, in which
  • FIG. 5 is a partially enlarged vertical cross-sectional view showing a third modified example of the spring bearing of the shock absorber according to the embodiment of the present invention, and showing the changed portion in an enlarged manner.
  • FIG. 6 is a partially enlarged vertical sectional view showing a third modified example of the spring bearing of the shock absorber according to the embodiment of the present invention, in which a changed portion is enlarged.
  • the shock absorber A according to the embodiment of the present invention shown in FIG. 1 is used for a front fork that suspends the front wheels of a saddle type vehicle.
  • the state in which the front fork is attached to the vehicle that is, the upper and lower sides of the shock absorber A in the attached state are simply referred to as “upper” and “lower” unless otherwise specified.
  • the shock absorber A includes a telescopic type tube member T configured to include an outer tube 1 and an inner tube 2 slidably inserted into the outer tube 1.
  • the tube member T is an inverted type in the present embodiment, and is attached to the vehicle with the outer tube 1 facing upward on the vehicle body side and the inner tube 2 facing downward on the front wheel side.
  • a vehicle body side bracket (not shown) is attached to the outer circumference of the outer tube 1 which is a vehicle body side tube, and a steering shaft fixed to this bracket is rotatably mounted in the vehicle body head pipe. Supported.
  • a wheel-side bracket 20 is attached to the outer periphery of the lower end portion of the inner tube 2 that serves as a wheel-side tube, and this bracket 20 is connected to the axle of the front wheel.
  • the tube member T is interposed between the vehicle body and the front wheel axle.
  • the inner tube 2 moves in and out of the outer tube 1 and the tube member T expands and contracts.
  • the expansion and contraction of the tube member T is also referred to as the expansion and contraction of the shock absorber A.
  • the tube member T may be an upright type, and the outer tube 1 may be the wheel side tube and the inner tube 2 may be the vehicle body side tube.
  • the use of the shock absorber A is not limited to the front fork, and can be changed appropriately.
  • the shock absorber A may be used for a rear cushion unit that suspends the rear wheels of a saddle-ride type vehicle, a suspension of an automobile, or other than the vehicle.
  • the upper end of the outer tube 1, which is the upper end of the tube member T, is closed by the cap 10.
  • the lower end of the inner tube 2, which is the lower end of the tube member T is closed by the bracket 20 on the wheel side.
  • an annular seal member 11 that is in sliding contact with the outer circumference of the inner tube 2 is provided, and a tubular gap between the overlapping portion of the outer tube 1 and the inner tube 2 is formed by the seal member 11. Is blocked by.
  • the inside of the tube member T is a closed space, and the shock absorber main body D and the suspension spring S are accommodated in the tube member T. Further, a liquid storage chamber R is provided between the tube member T in which the suspension spring S is arranged and the shock absorber body D. A liquid such as hydraulic oil is stored in the liquid storage chamber R, and a gas chamber G in which a gas such as air is sealed is formed above the liquid surface L.
  • the internal structure of the shock absorber main body D is not shown because it may be any structure, but the shock absorber main body D includes a cylinder 3 for accommodating a liquid such as hydraulic oil therein and a shaft inside the cylinder 3. Has a rod 4 movably inserted in the direction, and exerts a main damping force by giving a resistance to the flow of liquid moving in the cylinder 3 when the cylinder 3 and the rod 4 relatively move in the axial direction. ..
  • the shock absorber main body D is an inverted type, the rod 4 projects downward from the cylinder 3, and the lower end of the rod 4 is connected to the inner tube 2 via the bracket 20 on the wheel side. Has been done.
  • the upper end of the cylinder 3 is connected to the outer tube 1 via the cap 10.
  • the shock absorber body D is interposed between the outer tube 1 and the inner tube 2.
  • the rod 4 moves axially with respect to the cylinder 3 when the shock absorber A expands and contracts, and the shock absorber main body D expands and contracts, and the main damping force depends on the expansion and contraction speed.
  • the shock absorber body D is of an upright type, in which the rod 4 projects upward from the cylinder 3, the rod 4 is connected to the outer tube 1, and the cylinder 3 is connected to the inner tube 2. Good.
  • the shock absorber main body D is upright as described above, the liquid may move back and forth between the inside of the cylinder 3 and the liquid storage chamber R during expansion and contraction.
  • the liquid stored in the cylinder 3 and the liquid stored in the liquid storage chamber R become the same.
  • the liquid in the cylinder 3 and the liquid in the liquid storage chamber R may be different.
  • the suspension spring S is a coil spring.
  • the upper end of the suspension spring S is supported by a spring receiver B mounted on the outer periphery of the cylinder 3, and the lower end (not shown) of the suspension spring S is supported by a bracket 20 on the wheel side.
  • the wheel-side bracket 20 is connected to the inner tube 2, it can be said that the suspension spring S is interposed between the cylinder 3 and the inner tube (wheel-side tube) 2.
  • the suspension spring S is a compression spring, which elastically deforms when compressed and exhibits an elastic force commensurate with the amount of deformation.
  • the cylinder 3 penetrates into the inner tube 2 as the shock absorber A contracts.
  • the suspension spring S urges the shock absorber A in the extension direction by its elastic force to elastically support the vehicle body.
  • the spring receiver B that supports the upper end of the suspension spring S is an annular stopper 5 fixed to a snap ring 30 that fits on the outer periphery of the cylinder 3, and is provided below the stopper 5 and has a truncated cone cylindrical shape.
  • the upper end of the suspension spring S contacts the spring seat 7, and the body portion 6 is pressed against the stopper 5 by the urging force of the suspension spring S.
  • the stopper 5 and the main body portion 6 are integrated with each other by the urging force of the suspension spring S to form the spring receiver B.
  • the spring receiver B divides the liquid storage chamber R into an upper chamber r1 on the upper side and a lower chamber r2 on the lower side.
  • the stopper 5 may be omitted and the body 6 may be fixed to the outer circumference of the snap ring 30.
  • the spring bearing B may be attached to the outer circumference of the cylinder 3 by using a component other than the snap ring 30. As described above, the mounting structure of the spring receiver B to the shock absorber main body D can be appropriately changed.
  • the main body 6 of the spring receiver B is made of synthetic resin or the like, and has an annular support portion 6a which can be slidably contacted with the outer periphery of the cylinder 3 and whose upper end abuts on the stopper 5, and the lower end of this support portion 6a.
  • annular slide portion 6d connected to the lower end of the inner tube 2 and slidingly contacting the inner circumference of the inner tube 2, and connected to the lower end of the slide portion 6d, the outer diameter of which is smaller than the outer diameter of the slide portion 6d, and the spring seat 7 is fitted therein.
  • the annular small diameter portion 6e is included.
  • the spring seat 7 is made of metal or the like, and as shown in FIG. 2, an annular outer fitting portion 7a fitted to the outer circumference of the small-diameter portion 6e and a lower end of the outer fitting portion 7a that extends inward from the inner circumference. It includes an annular seat portion 7b which is extended.
  • the outer peripheral portion of the diaphragm member 8 is sandwiched and fixed between the upper surface of the seat portion 7b and the lower end of the small diameter portion 6e, while the upper end of the suspension spring S contacts the lower surface of the seat portion 7b.
  • the outer diameter of the outer fitting portion 7a is smaller than the outer diameter of the slide portion 6d, and the spring seat 7 does not interfere with the inner tube 2.
  • the diaphragm member 8 is an annular plate made of metal or synthetic resin.
  • the inner diameter of the throttle member 8 is larger than the outer diameter of the cylinder 3, and forms a restriction passage O between the throttle member 8 and the cylinder 3, which provides resistance to the flow of the liquid.
  • the throttle member 8 functions as a throttle portion that gives resistance to the flow of liquid.
  • the inner diameter of the throttle member 8 is smaller than the inner diameter of the lower portion of the body portion 6 below the window 6b and the inner diameter of the seat portion 7b of the spring seat 7, and the opening area (flow passage area) of the restricted passage O is all Is smaller than the total opening area of the window 6b.
  • the gap between 7b and the cylinder 3 forms a flow path 9 that connects the upper chamber r1 and the lower chamber r2.
  • the window 6b is an opening on the upper chamber r1
  • the gap between the seat portion 7b and the cylinder 3 is an opening on the lower chamber r2 side
  • the restriction passage O is the minimum throttle.
  • the inner diameter of the throttle member 8 is smaller than the inner diameter of the coil at the upper end of the suspension spring S.
  • the gap P between the upper end of the suspension spring S and the cylinder 3 serves as a connection port connected to the flow passage 9 in the lower chamber r2.
  • the opening area of the gap P is the restricted passage O. Larger than the opening area of. Therefore, the resistance (pressure loss) imparted to the flow of the liquid flowing between the upper chamber r1 and the lower chamber r2 through the spring receiver B is dominated by the resistance due to the restriction passage O.
  • the coil inner diameter at the upper end of the suspension spring S basically means the coil inner diameter of the first winding from the upper end of the wire material forming the suspension spring S.
  • the inner diameter of the end turn portion becomes the coil inner diameter of the upper end of the suspension spring S.
  • the upper end of the suspension spring S shown in FIGS. 1 and 2 is a closed end and is ground, the upper end shape of the suspension spring S may be an open end or may not be ground.
  • shock absorber A The operation of the shock absorber A according to the embodiment of the present invention will be described below.
  • the shock absorber A expands and contracts
  • the rod 4 moves axially with respect to the cylinder 3 and the shock absorber main body D expands and contracts to exert the main damping force.
  • the shock absorber A expands and contracts
  • the cylinder 3 moves in and out of the inner tube 2, and the spring receiver B moves up and down in the inner tube 2.
  • the suspension spring S expands and contracts to exert an elastic force commensurate with the amount of deformation.
  • the spring receiver B approaches the liquid level L of the liquid storage chamber R together with the cylinder 3, and when the cylinder 3 is submerged in the liquid, the liquid level L itself rises. The spring receiver B is immersed. In this way, when the shock absorber A expands and contracts, the spring receiver B and the liquid surface L of the liquid storage chamber R move relative to each other in the vertical direction.
  • the liquid passes through the flow passage 9 of the spring receiver B to form the upper chamber r1. While moving between the lower chamber r2 and the lower chamber r2, resistance is imparted to the flow of the liquid, and a damping force due to the resistance is secondarily generated. On the other hand, in the region outside the predetermined stroke region where the spring bearing B moves in the gas chamber G, the secondary damping force cannot be obtained.
  • the secondary damping force is a position-dependent damping force that is generated according to the positional relationship between the liquid surface L of the liquid reservoir R and the spring receiver B. Then, the secondary damping force is added to the main damping force only in a part of the stroke region (predetermined stroke region) of the entire stroke region of the shock absorber A, and the damping of the shock absorber A as a whole is performed. Power increases.
  • the restriction passage O formed on the inner circumference of the throttle member 8 is the minimum throttle.
  • the opening area of the gap P formed between the upper end of the suspension spring S located at the connection port to which the flow passage 9 is connected and the cylinder 3 is larger than the opening area of the restriction passage O. Therefore, the secondary damping force is dominated by the resistance when the liquid passes through the restriction passage O.
  • shock absorber A The operation and effect of the shock absorber A according to the embodiment of the present invention will be described below.
  • the shock absorber A is provided on a shock absorber main body D having a cylinder 3 and a rod 4 that is movably inserted in the cylinder 3 in the axial direction, and is provided on the outer periphery of the shock absorber main body D.
  • the tube member T that forms a liquid storage chamber R for storing the liquid between the liquid storage chamber R and the shock absorber main body D, and the liquid storage chamber R is divided into an upper chamber r1 and a lower chamber r2, and A spring receiver B in which a flow path 9 that connects the upper chamber r1 and the lower chamber r2 is formed, and a suspension spring (coil spring) S housed in the lower chamber r2 and supported at the upper end by the spring receiver B are provided.
  • the spring receiver B is located below the window 6b that is an opening on the upper chamber r1 side of the flow path 9 and provides a resistance to the flow of liquid between itself and the shock absorber body D. It has an annular throttle member (throttle portion) 8 that forms the restriction passage O. According to the configuration, in a predetermined stroke region where the liquid passes through the spring receiver B, a position-dependent damping force due to the resistance of the restriction passage O is secondarily generated, and the damping force of the shock absorber A as a whole is increased. Can be made bigger.
  • the inner diameter of the throttle member (throttle portion) 8 for forming the restricted passage O with the shock absorber body D is smaller than the coil inner diameter of the upper end of the suspension spring (coil spring) S. ..
  • the suspension spring S is replaced for the purpose of tuning the spring force of the shock absorber A, it is possible to prevent the magnitude of the position-dependent damping force generated from being changed unintentionally. Furthermore, by changing the inner diameter of the throttle member (throttle portion) 8, the generated position-dependent damping force can be adjusted in magnitude. In other words, it is not necessary to change the inner diameter of the coil at the upper end of the suspension spring (coil spring) S when adjusting the position-dependent damping force. Therefore, according to the above configuration, a desired position-dependent damping force can be easily obtained.
  • the spring receiver B of the present embodiment is fitted into the outer periphery of the shock absorber main body D in a tubular shape, and the main body portion 6 in which the window 6b is formed on the side portion, and the lower end of the main body portion 6.
  • the throttle member 8 serves as a throttle portion that forms a limiting passage O with the shock absorber body D.
  • the magnitude of the position-dependent damping force generated can be changed by replacing the diaphragm member 8 with a different inner diameter. Therefore, it is possible to inexpensively and easily adjust the position-dependent damping force. Further, according to the above configuration, it is easy to mount the diaphragm member 8 so as to be movable in the radial direction.
  • the outer diameter of the throttle member 8 is made larger than the inner diameter of the small diameter portion 6e and the inner diameter of the seat portion 7b of the spring bearing B, and the outer fitting portion 7a. It may be smaller than the inner diameter of the cylinder 3 so that the throttle member 8 can move in the radial direction with respect to the cylinder 3. Fitting the diaphragm member 8 with play is called loose fitting.
  • the throttle portion (throttle member 8) is provided on the spring bearing B1 so as to be movable in the radial direction, the opening area of the restricted passage O can be reduced. Therefore, the position-dependent damping force generated in the predetermined stroke region can be increased, and the adjustment range of the position-dependent damping force can be increased.
  • the configuration of the throttle portion that forms the restricted passage O with the shock absorber body D is not limited to the throttle member 8 and can be changed as appropriate.
  • the spring bearing may be configured as shown in FIGS. 4, 5 and 6.
  • the throttle member 8 is abolished, and the seat portion 7b of the spring seat 7 forms a restricted passage O between the seat body 7b and the shock absorber body D.
  • the spring seat 7 having the seat portion 7b having a different inner diameter is exchanged, the magnitude of the secondary position-dependent damping force can be changed, so that the position-dependent damping force can be adjusted. It is cheap and easy.
  • the diaphragm member 8 is abolished and an annular projection 6f is provided below the window 6b of the main body portion 6, and the projection 6f is provided in the shock absorber main body. It is used as a throttle portion that forms a restricted passage O with D.
  • the spring seat 7 may be eliminated and the upper end of the suspension spring (coil spring) S may directly abut against the lower end of the main body 6.
  • the restriction that the throttle member 12 is a choke passage between the throttle member 12 and the shock absorber body D as the throttle portion mounted on the inner periphery of the lower end of the body portion 6.
  • a passage O is formed.
  • a spring seat 7 with which the upper end of the suspension spring S abuts is fitted to the lower end of the main body 6 of the spring receiver B4, and the main body 6 is pressed against the stopper 5 by the urging force of the suspension spring S.
  • the main body 6 of the spring receiver B4 is made of synthetic resin or the like, is connected to the outer periphery of the cylinder 3 and has an annular support portion 6a whose upper end abuts the stopper 5, and a lower end of the support portion 6a.
  • the inner diameter and the outer diameter are gradually increased with increasing distance from the portion 6a, and the body portion 6c is formed with one or more windows 6b penetrating the wall thickness in the radial direction, and the lower end of the body portion 6c.
  • annular slide portion 6d that is continuous and is in sliding contact with the inner circumference of the inner tube 2, and an annular small diameter that is continuous with the lower end of the slide portion 6d and that has an outer diameter smaller than the outer diameter of the slide portion 6d and into which the spring seat 7 is fitted. And part 6e. Further, the diaphragm member 12 is fixed to the spring bearing B4 with the outer peripheral projection 12a of the diaphragm member 12 sandwiched between the step 6g formed on the inner periphery of the slide portion 6d and the upper surface of the seat portion 7b. .
  • the diaphragm member 12 has an annular shape and is provided inside the main body 6 and below the window 6b.
  • the throttle member 12 has an inner diameter larger than the outer diameter of the cylinder 3 and forms an annular choke passage (restriction passage O) between the throttle member 12 and the cylinder 3, which gives resistance to the flow of the liquid.
  • the inner diameter of the throttle member 12 is smaller than the inner diameter of the lower portion of the body portion 6 below the window 6b and the inner diameter of the seat portion 7b of the spring seat 7, and the opening area (flow passage area) of the choke passage is It is smaller than the total opening area of the window 6b.
  • the inner diameter of the throttle member 12 is smaller than the inner diameter of the coil at the upper end of the suspension spring S.
  • the throttle member 12 as the throttle portion is provided in the middle of the flow passage 9, and the annular choke passage is provided between the throttle member 12 and the cylinder 3 as the restricting passage O that gives resistance to the flow of the liquid. It is formed. For this reason, the resistance (pressure loss) imparted to the flow of the liquid passing through the spring receiver B4 is dominated by the resistance due to the choke passage.
  • the diaphragm member 12 is arranged so that its upper end does not come into contact with the window 6b. However, if the total opening area of the window 6b does not become smaller than the opening area of the choke passage, the upper end of the diaphragm member 12 may hang on the window 6b. Further, in the present embodiment, the diaphragm member 12 has the outer peripheral convex portion c1 sandwiched between the main body portion 6 and the spring seat 7. However, the method of attaching the diaphragm member 12 is not limited to this, and may be appropriately changed. For example, the diaphragm member 12 may be press-fitted into the inner circumference of the main body 6.
  • the restriction passage O that gives resistance to the flow of the liquid moving between the upper chamber r1 and the lower chamber r2 is the annular choke passage. Formed as.
  • the choke passage is a passage that is long in the axial direction, and the position-dependent damping force increases in proportion to the expansion and contraction speed of the shock absorber A. Further, when the opening area of the choke passage is equal to the opening area of the conventional orifice passage, the generated position-dependent damping force can be increased.
  • the opening area here is equal to a value obtained by subtracting the outer diameter of the shock absorber body facing the diaphragm member from the inner diameter of the throttle member (a gap amount between the diaphragm member and the shock absorber body).
  • the shock absorber A of the present embodiment it can be said that the position-dependent damping force generated compared to the orifice passage can be increased even if the amount of the gap between the throttle member and the shock absorber body is the same. In other words, even if the gap amount between the throttle member and the shock absorber body is larger than the gap amount of the orifice passage, the same position-dependent damping force can be obtained. Therefore, according to the shock absorber A of the present embodiment, it is possible to prevent the position-dependent damping force from becoming insufficient while securing the gap amount between the throttle member 12 and the shock absorber body D.
  • the throttle member 12 when the throttle member 12 is provided so as to be movable in the radial direction with respect to the spring receiver B4, the throttle member 12 moves toward the direction where the flow velocity becomes uniform, and the center of the throttle member 12 aligns with the center of the shock absorber body D. As described above, the centering is performed automatically, and the interference between the diaphragm member 12 and the shock absorber body D is suppressed. Therefore, if the throttle member 12 is provided on the spring receiver B4 so as to be movable in the radial direction, the opening area of the choke passage can be reduced. Therefore, the position-dependent damping force generated in the predetermined stroke region can be set to a larger value, and the adjustment range of the position-dependent damping force can be increased.
  • the throttle portion is formed at the lower end portions of the spring bearings B, B1, B2, B3, B4.
  • the position of the throttle portion can be freely changed as long as it is below the window 6b that is an opening on the upper chamber r1 side of the flow path 9.
  • the restriction passage O is formed between the throttle portion and the cylinder 3 of the shock absorber main body D.
  • the restricted passage O may be formed between the narrowed portion such as the members 8 and 12 and the rod 4. In this way, the configuration of the shock absorber main body D in which the restricted passage O is formed between the narrowed portion and the narrowed portion can be appropriately changed.

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

Abstract

L'invention concerne un amortisseur (A) pourvu : d'un siège de ressort (B) qui sépare, en une chambre supérieure (r1) et une chambre inférieure (r2), une chambre de stockage de liquide formée entre un corps d'amortisseur (D) et un élément de tube sur la périphérie externe de ce dernier, et dans lequel un passage d'écoulement (9) destiné à la communication entre les chambres supérieure et inférieure est ménagé entre le siège de ressort et le corps d'amortisseur (D) ; et un ressort de suspension (S) qui est logé dans la chambre inférieure (r2) et est supporté par le siège de ressort (B). Le siège de ressort (B) comporte une partie étranglement annulaire (8) qui est positionnée sous une fenêtre (6b) servant d'ouverture sur le côté chambre supérieure (r1) dans le trajet d'écoulement (9) et forme un trajet de restriction (O) qui confère une résistance au flux de liquide entre le corps d'amortisseur (D) et la partie d'étranglement, le diamètre interne de la partie étranglement (8) étant inférieur au diamètre interne d'une bobine sur l'extrémité supérieure du ressort de suspension (S).
PCT/JP2019/044068 2018-11-15 2019-11-11 Amortisseur WO2020100793A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2018214455A JP2020085000A (ja) 2018-11-15 2018-11-15 緩衝器
JP2018214453A JP2020084998A (ja) 2018-11-15 2018-11-15 緩衝器
JP2018-214453 2018-11-15
JP2018214454A JP7198053B2 (ja) 2018-11-15 2018-11-15 緩衝器
JP2018-214454 2018-11-15
JP2018-214455 2018-11-15

Publications (1)

Publication Number Publication Date
WO2020100793A1 true WO2020100793A1 (fr) 2020-05-22

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Application Number Title Priority Date Filing Date
PCT/JP2019/044068 WO2020100793A1 (fr) 2018-11-15 2019-11-11 Amortisseur

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Country Link
WO (1) WO2020100793A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06109054A (ja) * 1992-09-29 1994-04-19 Showa:Kk フロントフォークの油圧緩衝器
JP2004251364A (ja) * 2003-02-20 2004-09-09 Kayaba Ind Co Ltd フロントフォーク
JP2004286197A (ja) * 2003-03-25 2004-10-14 Kayaba Ind Co Ltd フロントフォーク
JP2006183690A (ja) * 2004-12-24 2006-07-13 Showa Corp 自動二輪車等のフロントフォーク

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06109054A (ja) * 1992-09-29 1994-04-19 Showa:Kk フロントフォークの油圧緩衝器
JP2004251364A (ja) * 2003-02-20 2004-09-09 Kayaba Ind Co Ltd フロントフォーク
JP2004286197A (ja) * 2003-03-25 2004-10-14 Kayaba Ind Co Ltd フロントフォーク
JP2006183690A (ja) * 2004-12-24 2006-07-13 Showa Corp 自動二輪車等のフロントフォーク

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