WO2020100793A1 - Shock absorber - Google Patents

Shock absorber Download PDF

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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
French (fr)
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/en
Priority claimed from JP2018214453A external-priority patent/JP2020084998A/en
Priority claimed from JP2018214454A external-priority patent/JP7198053B2/en
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/en

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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

This shock absorber (A) is provided with: a spring seat (B) which partitions, into an upper chamber (r1) and a lower chamber (r2), a liquid storage chamber formed between a shock absorber body (D) and a tube member on the outer periphery thereof, and in which a flow passage (9) for communication between the upper and lower chambers is formed between the spring seat and the shock absorber body (D); and a suspension spring (S) which is accommodated in the lower chamber (r2) and is supported by the spring seat (B). The spring seat (B) has an annular throttle part (8) which is positioned under a window (6b) serving as an opening on the upper chamber (r1) side in the flow path (9) and forms a restricting path O that imparts resistance to the flow of liquid between the shock absorber body (D) and the throttle part, wherein the inner diameter of the throttle part (8) is smaller than the inner diameter of a coil on the upper end of the suspension spring (S).

Description

緩衝器Shock absorber
　本発明は、緩衝器の改良に関する。 The present invention relates to improvement of a shock absorber.
　例えば、鞍乗型車両の前輪を懸架するフロントフォークに利用される緩衝器の中には、メインの減衰力を発揮する緩衝器本体と、その外周に設けられるチューブ部材との間に懸架ばねとしてのコイルばねを収容し、そのコイルばねの上端を緩衝器本体の外周に設けたばね受けで支えるものがある。 For example, in a shock absorber used for a front fork that suspends the front wheels of a saddle-ride type vehicle, 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. Of 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.
　さらに、そのような緩衝器の中には、緩衝器本体とチューブ部材との間に形成されて液体を貯留する液溜室をばね受けで上下に仕切り、このばね受けを液体が通過する際にその液体の流れに抵抗を与えて、この抵抗に起因する減衰力を二次的に発生させるものがある（例えば、特許文献１）。 Further, in such a shock absorber, 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).
　このように、上記した二次的な減衰力は、液体がばね受けを通過する所定のストローク領域で発生する位置依存の減衰力である。そして、その所定のストローク領域では、メインの減衰力に位置依存の減衰力が付加されて、緩衝器全体としての減衰力を大きくできる。 As described above, 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.
ＪＰ２０１０－２６１４７７ＡJP2010-261477A
　上記従来の緩衝器において、収容される懸架ばね等のコイルばねの上端と緩衝器本体との間にできる隙間の開口面積が狭い場合には、位置依存の減衰力がその隙間を液体が通過する際の抵抗に支配されることがある。 In the above conventional shock absorber, when the opening area of the gap formed between the upper end of the coil spring such as the accommodated suspension spring and the shock absorber body is small, the position-dependent damping force causes the liquid to pass through the gap. Sometimes it is dominated by resistance.
　そして、そのような場合には、緩衝器のばね力のチューニング等を目的としてコイルばねを交換すると、位置依存の減衰力が意図せずに変更されてしまうことがある。さらに、位置依存の減衰力を調整しようとすると、コイルばねの上端のコイル内径を変更しなければならず、煩雑である。 In such a case, if the coil spring is replaced for the purpose of tuning the spring force of the shock absorber, etc., 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.
　このため、従来の緩衝器では、所望の位置依存の減衰力を得るのが難しい。そこで、本発明は、所望の位置依存の減衰力を容易に得られる緩衝器の提供を目的とする。 Therefore, it is difficult to obtain a desired position-dependent damping force with a conventional shock absorber. Therefore, an object of the present invention is to provide a shock absorber that can easily obtain a desired position-dependent damping force.
　上記課題を解決する緩衝器は、緩衝器本体とその外周のチューブ部材との間に形成される液溜室を上室と下室とに区画するとともに、これらを連通する流路が緩衝器本体との間に形成されるばね受けと、下室に収容されて上端がばね受けで支持されるコイルばねとを備える。そして、ばね受けが、流路における上室側の開口よりも下方に位置して緩衝器本体との間に液体の流れに抵抗を与える制限通路を形成する環状の絞り部を有し、この絞り部の内径がコイルばねの上端のコイル内径より小さくなっている。 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. And 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.
　上記構成によれば、液体がばね受けを通過する所定のストローク領域で、制限通路の抵抗に起因する位置依存の減衰力を発生できる。そして、その位置依存の減衰力が、コイルばねの上端と緩衝器本体との間を液体が通過する際の抵抗に支配されてしまうのを防止できる。さらには、絞り部の内径の変更により位置依存の減衰力を大小調節できるので、位置依存の減衰力を調節する際にコイルばねの上端のコイル内径を変更する必要もない。 According to the above configuration, 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. Further, since 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.
　また、上記緩衝器では、ばね受けが筒状で緩衝器本体の外周に装着される本体部と、本体部の下端に嵌合されてコイルばねの上端が当接するばね座と、本体部とばね座との間に設けられた絞り部材とを有し、この絞り部材が絞り部となっているとよい。当該構成によれば、内径の異なる絞り部材に交換すれば位置依存の減衰力の大きさを変更できるので、位置依存の減衰力の調整を安価且つ容易にできる。 Further, in the above shock absorber, 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. According to this configuration, the magnitude of the position-dependent damping force can be changed by exchanging the diaphragm member with a different inner diameter, so that the position-dependent damping force can be adjusted inexpensively and easily.
　さらに、絞り部を径方向へ移動可能にした場合には、緩衝器が外部からの横力を受けて撓んだときに、絞り部が緩衝器本体に干渉して緩衝器本体が傷付くのを抑制できる。 Further, in the case where 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.
　また、上記緩衝器では、ばね受けが筒状で緩衝器本体の外周に装着される本体部と、本体部の下端部外周に嵌合される環状の外嵌部、及びその下端から内周側へ張り出してコイルばねの上端が当接する環状のシート部を含むばね座とを有し、そのシート部が絞り部となっているとよい。当該構成によれば、内径の異なるシート部をもつばね座に交換すれば位置依存の減衰力の大きさを変更できるので、位置依存の減衰力の調整を安価且つ容易にできる。 Further, in the above shock absorber, a main body part having a cylindrical spring receiver mounted on the outer circumference of the shock absorber main body, an annular outer fitting part fitted to the outer circumference of the lower end part of the main body part, and an inner circumference side from the lower end thereof. It is preferable to have a spring seat including an annular seat portion that projects toward the upper end of the coil spring and abuts on the upper end of the coil spring, and the seat portion serves as a throttle portion. With this configuration, the magnitude of the position-dependent damping force can be changed by replacing the spring seat with a seat having a different inner diameter, so that the position-dependent damping force can be adjusted inexpensively and easily.
　さらに、上記緩衝器では、制限通路がチョーク通路であってもよい。当該構成によれば、液体が絞り部を通過する所定のストローク領域で、チョーク通路の抵抗に起因する位置依存の減衰力を発生できる。また、この場合、絞り部と緩衝器本体との間の隙間量がオリフィス通路と同等であっても、発生する位置依存の大きさを大きくできる。 Furthermore, in the above-mentioned shock absorber, the restriction passage may be a choke passage. With this configuration, a position-dependent damping force due to the resistance of the choke passage can be generated in a predetermined stroke region where the liquid passes through the throttle portion. Further, in this case, even if the gap amount between the throttle portion and the shock absorber main body is equal to the orifice passage, the generated position-dependent size can be increased.
　本発明に係る緩衝器によれば、所望の位置依存の減衰力を容易に得られる。 According to the shock absorber according to the present invention, a desired position-dependent damping force can be easily obtained.
図1は、本発明の一実施の形態に係る緩衝器の一部を部分的に切欠いて示した正面図である。FIG. 1 is a partially cutaway front view of a shock absorber according to an embodiment of the present invention. 図２には、図１の一部を拡大して示した部分拡大縦断面図である。FIG. 2 is a partially enlarged vertical sectional view showing a part of FIG. 1 in an enlarged manner. 図３は、本発明の一実施の形態に係る緩衝器のばね受けの第一の変形例を示し、その変更部を拡大して示した部分拡大縦断面図である。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. 図４は、本発明の一実施の形態に係る緩衝器のばね受けの第二の変形例を示し、その変更部を拡大して示した部分拡大縦断面図である。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. 図５は、本発明の一実施の形態に係る緩衝器のばね受けの第三の変形例を示し、その変更部を拡大して示した部分拡大縦断面図である。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. 図６は、本発明の一実施の形態に係る緩衝器のばね受けの第三の変形例を示し、その変更部を拡大して示した部分拡大縦断面図である。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.
　以下に本発明の実施の形態の緩衝器について、図面を参照しながら説明する。いくつかの図面を通して付された同じ符号は、同じ部品か対応する部品を示す。 A buffer device according to an embodiment of the present invention will be described below with reference to the drawings. The same reference numerals allotted throughout the several figures refer to the same or corresponding parts.
　図１に示す本発明の一実施の形態に係る緩衝器Ａは、鞍乗型車両の前輪を懸架するフロントフォークに利用されている。以下の説明では、フロントフォークが車両に取り付けられた状態、即ち、取付状態での緩衝器Ａの上下を、特別な説明がない限り、単に「上」「下」という。 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. In the following description, 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.
　緩衝器Ａは、アウターチューブ１と、このアウターチューブ１内に摺動自在に挿入されるインナーチューブ２とを有して構成されるテレスコピック型のチューブ部材Ｔを備える。そのチューブ部材Ｔは、本実施の形態では倒立型であり、アウターチューブ１を車体側となる上側へ、インナーチューブ２を前輪側となる下側へ向けて車両に取り付けられる。 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.
　より詳しくは、車体側チューブとなるアウターチューブ１の外周には、車体側のブラケット（図示せず）が装着されており、このブラケットに固定されるステアリングシャフトが車体のヘッドパイプ内に回転自在に支持される。その一方、車輪側チューブとなるインナーチューブ２の下端部外周には、車輪側のブラケット２０が装着されており、このブラケット２０が前輪の車軸に連結される。 More specifically, 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. On the other hand, 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.
　このようにしてチューブ部材Ｔは車体と前輪の車軸との間に介装される。そして、車両が凹凸のある路面を走行する等して前輪が上下に振動すると、インナーチューブ２がアウターチューブ１に出入りしてチューブ部材Ｔが伸縮する。このように、チューブ部材Ｔが伸縮することを緩衝器Ａが伸縮するともいう。 In this way, the tube member T is interposed between the vehicle body and the front wheel axle. When the front wheel vibrates up and down as the vehicle travels on an uneven road surface, 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.
　なお、チューブ部材Ｔは、正立型になっていて、アウターチューブ１を車輪側チューブ、インナーチューブ２を車体側チューブとしてもよい。さらに、緩衝器Ａの用途はフロントフォークに限られず、適宜変更できる。例えば、緩衝器Ａを鞍乗型車両の後輪を懸架するリアクッションユニット、自動車のサスペンション、又は車両以外に利用してもよい。 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. Further, the use of the shock absorber A is not limited to the front fork, and can be changed appropriately. For example, 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.
　つづいて、チューブ部材Ｔの上端となるアウターチューブ１の上端は、キャップ１０で塞がれている。その一方、チューブ部材Ｔの下端となるインナーチューブ２の下端は、車輪側のブラケット２０で塞がれている。さらに、アウターチューブ１の下端部には、インナーチューブ２の外周に摺接する環状のシール部材１１が設けられ、アウターチューブ１とインナーチューブ２の重複部の間の筒状の隙間がそのシール部材１１で塞がれている。 Next, the upper end of the outer tube 1, which is the upper end of the tube member T, is closed by the cap 10. On the other hand, 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. Further, at the lower end portion of the outer tube 1, 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.
　このようにしてチューブ部材Ｔ内は密閉空間とされており、そのチューブ部材Ｔ内に緩衝器本体Ｄと懸架ばねＳが収容されている。さらに、懸架ばねＳが配置されるチューブ部材Ｔと緩衝器本体Ｄとの間は液溜室Ｒとされている。この液溜室Ｒには、作動油等の液体が貯留されるとともに、その液面Ｌ上側にエア等の気体が封入されたガス室Ｇが形成されている。 In this way, 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.
　緩衝器本体Ｄの内部構造については、如何なる構造であってもよいので図示を省略するが、緩衝器本体Ｄは、内部に作動油等の液体を収容するシリンダ３と、このシリンダ３内に軸方向へ移動可能に挿入されるロッド４とを有し、シリンダ３とロッド４が軸方向へ相対移動する際にシリンダ３内を移動する液体の流れに抵抗を与えてメインの減衰力を発揮する。 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. ..
　また、本実施の形態において、緩衝器本体Ｄは倒立型となっており、ロッド４がシリンダ３から下方へ突出して、そのロッド４の下端が車輪側のブラケット２０を介してインナーチューブ２に連結されている。その一方、シリンダ３の上端がキャップ１０を介してアウターチューブ１に連結されている。 Further, in the present embodiment, 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. On the other hand, the upper end of the cylinder 3 is connected to the outer tube 1 via the cap 10.
　このようにして緩衝器本体Ｄは、アウターチューブ１とインナーチューブ２との間に介装されている。そして、インナーチューブ２がアウターチューブ１に出入りする緩衝器Ａの伸縮時にロッド４がシリンダ３に対して軸方向へ移動して緩衝器本体Ｄが伸縮するとともに、伸縮速度に依存するメインの減衰力を発揮する。 In this way, the shock absorber body D is interposed between the outer tube 1 and the inner tube 2. When the inner tube 2 moves in and out of the outer tube 1, 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. Exert.
　なお、緩衝器本体Ｄは、正立型になっていて、ロッド４がシリンダ３から上方へ突出し、そのロッド４がアウターチューブ１に連結されるとともに、シリンダ３がインナーチューブ２に連結されていてもよい。そして、このように緩衝器本体Ｄが正立型の場合には、伸縮時に液体がシリンダ３内と液溜室Ｒとの間を行き来するようにしてもよい。 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. When 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.
　また、このようにシリンダ３内と液溜室Ｒとの間で液体のやり取りがある場合には、シリンダ３内に収容される液体と、液溜室Ｒに貯留される液体は同じになる。しかし、シリンダ３内と液溜室Ｒとの間で液体のやり取りがない場合には、シリンダ３内の液体と液溜室Ｒの液体が異なっていてもよい。 Further, when liquid is exchanged between the cylinder 3 and the liquid storage chamber R as described above, the liquid stored in the cylinder 3 and the liquid stored in the liquid storage chamber R become the same. However, when there is no liquid exchange between the cylinder 3 and the liquid storage chamber R, the liquid in the cylinder 3 and the liquid in the liquid storage chamber R may be different.
　つづいて、懸架ばねＳは、コイルばねである。そして、この懸架ばねＳの上端がシリンダ３の外周に装着されたばね受けＢで支持されるとともに、懸架ばねＳの下端（図示せず）が車輪側のブラケット２０で支持されている。前述の通り、車輪側のブラケット２０はインナーチューブ２に連結されているので、懸架ばねＳはシリンダ３とインナーチューブ（車輪側チューブ）２との間に介装されているといえる。 Next, 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. As described above, since 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.
　また、懸架ばねＳは圧縮ばねであり、圧縮されると弾性変形して、その変形量に見合った弾性力を発揮する。緩衝器Ａでは、その収縮作動に伴いシリンダ３がインナーチューブ２内へと侵入するようになっており、緩衝器Ａの収縮時には懸架ばねＳの変形量が大きくなって、発生する弾性力も大きくなる。そして、懸架ばねＳは、その弾性力によって緩衝器Ａを伸長方向へ付勢して、車体を弾性支持するようになっている。 Also, the suspension spring S is a compression spring, which elastically deforms when compressed and exhibits an elastic force commensurate with the amount of deformation. In the shock absorber A, the cylinder 3 penetrates into the inner tube 2 as the shock absorber A contracts. When the shock absorber A contracts, the amount of deformation of the suspension spring S increases and the elastic force generated also increases. .. Then, the suspension spring S urges the shock absorber A in the extension direction by its elastic force to elastically support the vehicle body.
　その懸架ばねＳの上端を支持するばね受けＢは、シリンダ３の外周に嵌合するスナップリング３０に固定される環状のストッパ５と、このストッパ５の下側に設けられ、円錐台形筒状で内側にシリンダ３が挿通される本体部６と、この本体部６の下端に嵌合する環状のばね座７と、このばね座７と本体部６との間に介装される絞り部材８とを有する。 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. A body portion 6 into which the cylinder 3 is inserted, an annular spring seat 7 fitted to the lower end of the body portion 6, and a diaphragm member 8 interposed between the spring seat 7 and the body portion 6. Have.
　ばね座７には、懸架ばねＳの上端が当接し、本体部６が懸架ばねＳの付勢力によりストッパ５に押し付けられる。このように、本実施の形態では、懸架ばねＳの付勢力によりストッパ５と本体部６とが一体となってばね受けＢが構成される。そして、このばね受けＢによって液溜室Ｒが上側の上室ｒ１と下側の下室ｒ２とに仕切られる。 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. As described above, in this embodiment, 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.
　なお、ストッパ５を廃し、本体部６をスナップリング３０の外周に固定してもよい。また、スナップリング３０以外を利用してばね受けＢをシリンダ３の外周に装着してもよい。このように、ばね受けＢの緩衝器本体Ｄへの取付構造は、適宜変更できる。 Note that the stopper 5 may be omitted and the body 6 may be fixed to the outer circumference of the snap ring 30. Alternatively, 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.
　つづいて、ばね受けＢの本体部６は、合成樹脂等で形成されており、シリンダ３の外周に摺接可能で上端がストッパ５に突き当たる環状の支持部６ａと、この支持部６ａの下端に連なり、支持部６ａから離れるに従って内径及び外径が徐々に拡径されるとともに、側部に肉厚を径方向へ貫通する一以上の窓６ｂが形成される胴部６ｃと、この胴部６ｃの下端に連なり、インナーチューブ２の内周に摺接する環状のスライド部６ｄと、このスライド部６ｄの下端に連なり、外径がスライド部６ｄの外径よりも小さく、ばね座７が嵌合する環状の小径部６ｅとを含む。 Subsequently, 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. A body portion 6c in which the inner diameter and the outer diameter are gradually increased as the distance from the support portion 6a increases, and one or more windows 6b penetrating the wall thickness in the radial direction are formed, and the body portion 6c. And an 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.
　ばね座７は、金属等で形成されており、図２に示すように、小径部６ｅの外周に嵌合する環状の外嵌部７ａと、この外嵌部７ａの下端から内周側へ張り出す環状のシート部７ｂとを含む。そして、シート部７ｂの上面と小径部６ｅの下端との間に絞り部材８の外周部が挟まれて固定される一方、シート部７ｂの下面には懸架ばねＳの上端が当接する。また、外嵌部７ａの外径は、スライド部６ｄの外径よりも小さく、ばね座７がインナーチューブ２に干渉しない。 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. Further, 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.
　絞り部材８は、金属又は合成樹脂等で形成された環状板である。その絞り部材８の内径は、シリンダ３の外径よりも大きく、シリンダ３との間に液体の流れに抵抗を与える制限通路Ｏを形成する。このように、絞り部材８は液体の流れに抵抗を与える絞り部として機能する。さらに、絞り部材８の内径は、本体部６における窓６ｂより下側部分の内径、及びばね座７のシート部７ｂの内径よりも小さく、制限通路Ｏの開口面積（流路面積）は、全ての窓６ｂの総開口面積よりも小さい。 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. In this way, the throttle member 8 functions as a throttle portion that gives resistance to the flow of liquid. Further, 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.
　上記構成によれば、本体部６の窓６ｂ、本体部６の胴部６ｃから下側部分とシリンダ３との間の隙間、絞り部材８とシリンダ３との間の制限通路Ｏ、及びシート部７ｂとシリンダ３との間の隙間によって上室ｒ１と下室ｒ２とを連通する流路９が形成される。そして、その流路９において、窓６ｂが上室ｒ１側の開口、シート部７ｂとシリンダ３との間の隙間が下室ｒ２側の開口、制限通路Ｏが最小絞りとなる。 According to the above configuration, the window 6b of the body portion 6, the gap between the lower portion of the body portion 6c of the body portion 6 and the cylinder 3, the restricted passage O between the throttle member 8 and the cylinder 3, and the seat portion. The gap between 7b and the cylinder 3 forms a flow path 9 that connects the upper chamber r1 and the lower chamber r2. In the flow passage 9, 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, and the restriction passage O is the minimum throttle.
　さらに、絞り部材８の内径は、懸架ばねＳの上端のコイル内径よりも小さい。この懸架ばねＳの上端とシリンダ３との間の隙間Ｐは、下室ｒ２において流路９に接続される接続口となるが、上記構成によれば、その隙間Ｐの開口面積が制限通路Ｏの開口面積よりも大きくなる。このため、ばね受けＢを通って上室ｒ１と下室ｒ２との間を行き来する液体の流れに付与される抵抗（圧力損失）は、制限通路Ｏによる抵抗が支配的となる。 Further, 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. According to the above configuration, 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.
　ここでいう懸架ばねＳの上端のコイル内径とは、基本的に、懸架ばねＳを構成する線材の上端から一巻目のコイル内径のことをいう。そして、懸架ばねＳが上端部に一巻以上の座巻部を有する場合、その座巻部の内径が懸架ばねＳの上端のコイル内径となる。なお、図１，２に示す懸架ばねＳの上端は、クローズドエンドとなっていて研削されているが、懸架ばねＳの上端形状は、オープンエンドであっても、研削されていなくてもよい。 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. When the suspension spring S has one or more end turn portions at the upper end, the inner diameter of the end turn portion becomes the coil inner diameter of the upper end of the suspension spring S. Although 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.
　以下に、本発明の一実施の形態に係る緩衝器Ａの作動について説明する。 The operation of the shock absorber A according to the embodiment of the present invention will be described below.
　緩衝器Ａの伸縮時には、ロッド４がシリンダ３に対して軸方向へ移動して緩衝器本体Ｄが伸縮し、メインの減衰力を発揮する。さらに、緩衝器Ａの伸縮時には、シリンダ３がインナーチューブ２に出入りして、ばね受けＢがインナーチューブ２内を上下に移動する。すると、懸架ばねＳが伸縮して変形量に見合った弾性力を発揮する。 When 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. Further, when 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. Then, the suspension spring S expands and contracts to exert an elastic force commensurate with the amount of deformation.
　また、緩衝器Ａが最伸長状態から収縮していくと、ばね受けＢがシリンダ３とともに液溜室Ｒの液面Ｌに接近し、シリンダ３が液中に浸かると液面Ｌ自体が上昇してばね受けＢが浸漬される。このように、緩衝器Ａの伸縮時には、ばね受けＢと液溜室Ｒの液面Ｌとが上下方向に相対移動するようになっている。 Further, when the shock absorber A contracts from the most extended state, 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.
　そして、緩衝器Ａの最伸長状態からの収縮量が所定よりも大きくなってばね受けＢが液中に浸かる所定のストローク領域では、液体がばね受けＢの流路９を通って上室ｒ１と下室ｒ２との間を移動するとともに、この液体の流れに対して抵抗が付与されて、その抵抗に起因する減衰力が二次的に発生する。その一方、ばね受けＢがガス室Ｇ内を移動する所定のストローク領域外の領域では、その二次的な減衰力を得られない。 Then, in a predetermined stroke region in which the amount of contraction of the shock absorber A from the most expanded state is larger than a predetermined amount and the spring receiver B is submerged in the liquid, 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.
　このように、二次的な減衰力は、液溜室Ｒの液面Ｌとばね受けＢの位置関係に応じて発生する位置依存の減衰力である。そして、緩衝器Ａにおける全ストローク領域のうちの、一部のストローク領域（所定のストローク領域）においてのみ、メインの減衰力に二次的な減衰力が付加されて、緩衝器Ａ全体としての減衰力が大きくなる。 In this way, 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.
　また、上室ｒ１と下室ｒ２とを行き交う液体の流れを許容するばね受けＢの流路９において、絞り部材８の内周に形成される制限通路Ｏが最小絞りとなっている。さらに、下室ｒ２において、その流路９が接続される接続口に位置する懸架ばねＳの上端とシリンダ３との間にできる隙間Ｐの開口面積は、制限通路Ｏの開口面積よりも大きい。このため、二次的な減衰力は、制限通路Ｏを液体が通過する際の抵抗により支配される。 Further, in the flow path 9 of the spring receiver B that allows the flow of liquid to and from the upper chamber r1 and the lower chamber r2, the restriction passage O formed on the inner circumference of the throttle member 8 is the minimum throttle. Further, in the lower chamber r2, 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.
　以下に、本発明の一実施の形態に係る緩衝器Ａの作用効果について説明する。 The operation and effect of the shock absorber A according to the embodiment of the present invention will be described below.
　本実施の形態において、緩衝器Ａは、シリンダ３と、このシリンダ３内に軸方向へ移動可能に挿入されるロッド４とを有する緩衝器本体Ｄと、この緩衝器本体Ｄの外周に設けられてその緩衝器本体Ｄとの間に液体を貯留する液溜室Ｒを形成するチューブ部材Ｔと、液溜室Ｒを上室ｒ１と下室ｒ２とに区画するとともに、緩衝器本体Ｄとの間に上室ｒ１と下室ｒ２とを連通する流路９が形成されるばね受けＢと、下室ｒ２に収容されて上端をばね受けＢで支持される懸架ばね（コイルばね）Ｓとを備える。 In the present embodiment, 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. Prepare
　さらに、本実施の形態において、そのばね受けＢは、流路９の上室ｒ１側の開口となる窓６ｂよりも下方に位置して緩衝器本体Ｄとの間に液体の流れに抵抗を与える制限通路Ｏを形成する環状の絞り部材（絞り部）８を有する。当該構成によれば、液体がばね受けＢを通過する所定のストローク領域で、制限通路Ｏの抵抗に起因する位置依存の減衰力を二次的に発生し、緩衝器Ａ全体としての減衰力を大きくできる。 Further, in the present embodiment, 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.
　また、本実施の形態において、緩衝器本体Ｄとの間に制限通路Ｏを形成するための絞り部材（絞り部）８の内径は、懸架ばね（コイルばね）Ｓの上端のコイル内径よりも小さい。当該構成によれば、位置依存の減衰力が懸架ばねＳの上端と緩衝器本体Ｄとの間にできる隙間Ｐを液体が通過する際の抵抗に支配されてしまうのを防止できる。 Further, in the present embodiment, 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. .. With this configuration, it is possible to prevent the position-dependent damping force from being dominated by the resistance when the liquid passes through the gap P formed between the upper end of the suspension spring S and the shock absorber body D.
　このため、緩衝器Ａのばね力のチューニング等を目的として、懸架ばねＳを交換したとしても、発生する位置依存の減衰力の大きさが意図せずに変更されてしまうのを抑制できる。さらには、絞り部材（絞り部）８の内径を変更すれば、発生する位置依存の減衰力を大小調節できる。換言すると、位置依存の減衰力を調節する際に、懸架ばね（コイルばね）Ｓの上端のコイル内径を変更する必要もない。このため、上記構成によれば、所望の位置依存の減衰力を容易に得られる。 Therefore, even if 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.
　また、本実施の形態のばね受けＢは、筒状で緩衝器本体Ｄの外周に装着されるとともに側部に窓６ｂが形成される本体部６と、この本体部６の下端に嵌合されて懸架ばね（コイルばね）Ｓの上端が当接するばね座７と、本体部６とばね座７との間に挟まれて保持される絞り部材８とを有する。そして、この絞り部材８が緩衝器本体Ｄとの間に制限通路Ｏを形成する絞り部となっている。 Further, 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. A spring seat 7 with which the upper end of a suspension spring (coil spring) S abuts, and a diaphragm member 8 sandwiched and held between the main body 6 and the spring seat 7. The throttle member 8 serves as a throttle portion that forms a limiting passage O with the shock absorber body D.
　上記構成によれば、内径の異なる絞り部材８に交換すれば、発生する位置依存の減衰力の大きさを変更できる。このため、位置依存の減衰力の調整を安価且つ容易にできる。さらに、上記構成によれば、絞り部材８を径方向へ移動可能に装着するのも容易である。 According to the above configuration, 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.
　なお、図３に示す第一の変形例に係るばね受けＢ１ように、絞り部材８の外径をばね受けＢにおける小径部６ｅの内径及びシート部７ｂの内径よりも大きくするとともに外嵌部７ａの内径よりも小さくし、絞り部材８がシリンダ３に対して径方向へ移動できるようにしてもよい。絞り部材８が遊びをもった状態で嵌ることを遊嵌という。 As in the spring bearing B1 according to the first modification shown in FIG. 3, 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.
　緩衝器Ａが外部からの横力を受けて撓み、絞り部材８とシリンダ３との間にできる環状の制限通路Ｏの径方向幅が周方向で変わると、その幅が狭い部分と広い部分とで通過する液体の流速が変わる。すると、絞り部材８がその速度が均等になる方へ動いて、絞り部材８の中心が緩衝器本体Ｄの中心と合うように自動で調心される。 When the shock absorber A bends by receiving a lateral force from the outside and the radial width of the annular restriction passage O formed between the throttle member 8 and the cylinder 3 changes in the circumferential direction, a narrow portion and a wide portion are formed. The flow velocity of the liquid passing through changes. Then, the throttle member 8 moves toward the direction where the speed becomes uniform, and the center of the throttle member 8 is automatically aligned so as to match the center of the shock absorber body D.
　これにより、緩衝器Ａが外部からの横力を受けて撓んだとしても、制限通路Ｏを流れる液体の流速の周方向でのバラつきが抑制されて、発生する位置依存の減衰力が安定する。また、制限通路Ｏを形成する絞り部材８のシリンダ３への干渉が抑制されるとともに、仮に絞り部材８がシリンダ３に干渉したとしても接触時の面圧が低減される。このため、絞り部材８によってシリンダ３が傷付くのが抑制される。 As a result, even if the shock absorber A is bent by receiving a lateral force from the outside, variation in the flow velocity of the liquid flowing through the restriction passage O in the circumferential direction is suppressed, and the generated position-dependent damping force is stabilized. .. Further, the interference of the throttle member 8 forming the restricted passage O with the cylinder 3 is suppressed, and even if the throttle member 8 interferes with the cylinder 3, the surface pressure at the time of contact is reduced. Therefore, it is possible to prevent the cylinder 3 from being damaged by the diaphragm member 8.
　よって、絞り部（絞り部材８）をばね受けＢ１に径方向へ移動可能に設けると、制限通路Ｏの開口面積を小さくできる。このため、所定のストローク領域で発生する位置依存の減衰力を大きくできるとともに、位置依存の減衰力の調整幅を大きくできる。 Therefore, if 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.
　なお、緩衝器本体Ｄとの間に制限通路Ｏを形成する絞り部の構成は、絞り部材８に限らず、適宜変更できる。例えば、ばね受けは、図４，図５および図６に示すように構成されてもよい。 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. For example, the spring bearing may be configured as shown in FIGS. 4, 5 and 6.
　具体的に、図４に示す第二の変形例に係るばね受けＢ２では、絞り部材８を廃し、ばね座７のシート部７ｂを緩衝器本体Ｄとの間に制限通路Ｏを形成する絞り部として利用する。このような場合においても、内径の異なるシート部７ｂをもつばね座７に交換すれば、二次的に発生する位置依存の減衰力の大きさを変更できるので、位置依存の減衰力の調整を安価且つ容易にできる。 Specifically, in the spring receiver B2 according to the second modified example shown in FIG. 4, 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. To use as. Even in such a case, if 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.
　その一方、図５に示す第二の変形例に係るばね受けＢ３では、絞り部材８を廃するとともに本体部６の窓６ｂより下側に環状の突起６ｆを設け、当該突起６ｆを緩衝器本体Ｄとの間に制限通路Ｏを形成する絞り部として利用する。このような場合には、ばね座７を廃し、懸架ばね（コイルばね）Ｓの上端を本体部６の下端に直接突き当ててもよい。 On the other hand, in the spring receiver B3 according to the second modified example shown in FIG. 5, 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. In such a case, 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.
　また、図６に示す第三の変形例に係るばね受けＢ４では、本体部６の下端の内周に装着される絞り部として絞り部材１２が緩衝器本体Ｄとの間にチョーク通路でなる制限通路Ｏを形成している。なお、ばね受けＢ４における本体部６の下端には、懸架ばねＳの上端が当接するばね座７が嵌合されており、本体部６が懸架ばねＳの付勢力によりストッパ５に押し付けられる。 Further, in the spring receiver B4 according to the third modification shown in FIG. 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.
　ばね受けＢ４の本体部６は、合成樹脂等で形成されており、シリンダ３の外周に摺接可能で上端がストッパ５に突き当たる環状の支持部６ａと、この支持部６ａの下端に連なり、支持部６ａから離れるに従って内径及び外径が徐々に拡径されるとともに、側部に肉厚を径方向へ貫通する一以上の窓６ｂが形成される胴部６ｃと、この胴部６ｃの下端に連なり、インナーチューブ２の内周に摺接する環状のスライド部６ｄと、このスライド部６ｄの下端に連なり、外径がスライド部６ｄの外径よりも小さく、ばね座７が嵌合する環状の小径部６ｅとを含む。さらに、スライド部６ｄの内周に形成された段差６ｇとシート部７ｂの上面との間に絞り部材１２の外周凸部１２ａが挟まれた状態で、絞り部材１２がばね受けＢ４に固定される。 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. An 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. .
　絞り部材１２は、環状であり、本体部６の内側であって窓６ｂより下方に設けられている。そして、その絞り部材１２の内径は、シリンダ３の外径よりも大きく、シリンダ３との間に液体の流れに抵抗を与える環状のチョーク通路（制限通路Ｏ）を形成する。さらに、絞り部材１２の内径は、本体部６における窓６ｂより下側部分の内径、及びばね座７のシート部７ｂの内径よりも小さく、チョーク通路の開口面積（流路面積）は、全ての窓６ｂの総開口面積よりも小さい。さらに、絞り部材１２の内径は、懸架ばねＳの上端のコイル内径よりも小さい。 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. Further, 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. Further, 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.
　上記構成によれば、流路９の途中に絞り部としての絞り部材１２が設けられ、この絞り部材１２とシリンダ３との間に液体の流れに抵抗を与える制限通路Ｏとして環状のチョーク通路が形成される。このため、ばね受けＢ４を通過する液体の流れに付与される抵抗（圧力損失）は、チョーク通路による抵抗が支配的となる。 According to the above configuration, 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.
　また、絞り部材１２は、その上端が窓６ｂにかからないように配置されている。しかし、窓６ｂの総開口面積がチョーク通路の開口面積よりも小さくならなければ、絞り部材１２の上端が窓６ｂにかかっていてもよい。また、本実施の形態では、絞り部材１２がその外周凸部ｃ１を本体部６とばね座７とで挟まれているが、絞り部材１２の取付方法もこの限りではなく、適宜変更できる。例えば、絞り部材１２は、本体部６の内周に圧入されていてもよい。 Further, 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.
　そして、本実施の形態では、その絞り部材１２と緩衝器本体Ｄとの間に、上室ｒ１と下室ｒ２との間を移動する液体の流れに抵抗を与える制限通路Ｏが環状のチョーク通路として形成される。当該構成によれば、液体がチョーク通路を通過する所定のストローク領域で、チョーク通路の抵抗に起因する位置依存の減衰力を二次的に発生し、緩衝器Ａ全体としての減衰力を大きくできる。 Further, in the present embodiment, between the throttle member 12 and the shock absorber body D, 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. With this configuration, in a predetermined stroke region where the liquid passes through the choke passage, a position-dependent damping force due to the resistance of the choke passage is secondarily generated, and the damping force of the shock absorber A as a whole can be increased. ..
　また、チョーク通路は、軸方向に長い通路であり、位置依存の減衰力が緩衝器Ａの伸縮速度に比例して大きくなる。さらに、チョーク通路の開口面積が従来のオリフィス通路の開口面積と同等である場合には、発生する位置依存の減衰力を大きくできる。ここでいう開口面積とは、絞り部材の内径から、この絞り部材に対向する緩衝器本体の外径を減じた値（絞り部材と緩衝器本体との間の隙間量）に等しい。 Also, 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).
　つまり、本実施の形態の緩衝器Ａでは、絞り部材と緩衝器本体との間の隙間量が同じであっても、オリフィス通路に比較して発生する位置依存の減衰力を大きくできるといえる。換言すると、絞り部材と緩衝器本体との間の隙間量がオリフィス通路の隙間量より大きくても、同等の位置依存の減衰力を得られる。よって、本実施の形態の緩衝器Ａによれば、絞り部材１２と緩衝器本体Ｄとの間の隙間量を確保しつつ、位置依存の減衰力が不足するのを防止できる。 That is, in 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.
　また、絞り部材１２をばね受けＢ４に対して径方向へ移動可能に設ける場合、その流速が均等になる方へ絞り部材１２が動いて、絞り部材１２の中心が緩衝器本体Ｄの中心と合うように自動調心され、絞り部材１２と緩衝器本体Ｄとの干渉が抑制される。よって、絞り部材１２をばね受けＢ４に径方向へ移動可能に設けると、チョーク通路の開口面積を小さくできる。このため、所定のストローク領域で発生する位置依存の減衰力をより大きく設定できるとともに、位置依存の減衰力の調整幅を大きくできる。 Further, 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.
　さらに、本実施の形態では、絞り部がばね受けＢ，Ｂ１，Ｂ２，Ｂ３，Ｂ４の下端部に形成されている。しかし、絞り部の位置は、流路９の上室ｒ１側の開口となる窓６ｂよりも下方であれば、自由に変更できる。 Further, in the present embodiment, the throttle portion is formed at the lower end portions of the spring bearings B, B1, B2, B3, B4. However, 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.
　また、本実施の形態では、絞り部と緩衝器本体Ｄのシリンダ３との間に制限通路Ｏが形成されているが、例えば、緩衝器本体Ｄを正立型にした場合等には、絞り部材８，１２等の絞り部とロッド４との間に制限通路Ｏを形成してもよい。このように、絞り部との間に制限通路Ｏが形成される緩衝器本体Ｄの構成は、適宜変更できる。 Further, in the present embodiment, the restriction passage O is formed between the throttle portion and the cylinder 3 of the shock absorber main body D. However, for example, when the shock absorber main body D is an upright type, the restriction is reduced. 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.
　以上、本発明の好ましい実施の形態を詳細に説明したが、特許請求の範囲から逸脱しない限り、改造、変形、及び変更が可能である。 The preferred embodiments of the present invention have been described above in detail, but modifications, variations, and changes can be made without departing from the scope of the claims.
Ａ・・・緩衝器、Ｂ，Ｂ１，Ｂ２，Ｂ３，Ｂ４・・・ばね受け、Ｄ・・・緩衝器本体、Ｏ・・・制限通路、Ｒ・・・液溜室、ｒ１・・・上室、ｒ２・・・下室、Ｓ・・・懸架ばね（コイルばね）、Ｔ・・・チューブ部材、３・・・シリンダ、４・・・ロッド、６・・・本体部、６ｂ・・・窓（流路の上室側の開口）、７・・・ばね座、７ａ・・・外嵌部、７ｂ・・・シート部、８，１２・・・絞り部材（絞り部）、９・・・流路
  A ... shock absorber, B, B1, B2, B3, B4 ... spring receiver, D ... shock absorber body, O ... limiting passage, R ... liquid storage chamber, r1 ... upper Chamber, r2 ... Lower chamber, S ... Suspension spring (coil spring), T ... Tube member, 3 ... Cylinder, 4 ... Rod, 6 ... Main body, 6b ... Window (opening on upper chamber side of flow path), 7 ... Spring seat, 7a ... External fitting portion, 7b ... Seat portion, 8, 12 ... Throttling member (throttle portion), 9 ...・ Flow path

Claims (5)

  1. 　緩衝器であって、
    　シリンダと、前記シリンダ内に軸方向へ移動可能に挿入されるロッドとを有する緩衝器本体と、
    　前記緩衝器本体の外周に設けられて前記緩衝器本体との間に液体を貯留する液溜室を形成するチューブ部材と、
    　前記液溜室を上室と下室とに区画するとともに、前記緩衝器本体との間に前記上室と前記下室とを連通する流路が形成されるばね受けと、
    　前記下室に収容されて上端が前記ばね受けで支持されるコイルばねとを備え、
    　前記ばね受けは、前記流路の上室側の開口よりも下方に位置して前記緩衝器本体との間に液体の流れに抵抗を与える制限通路を形成する環状の絞り部を有し、
    　前記絞り部の内径は、前記コイルばねの上端のコイル内径より小さい
    　緩衝器。     A shock absorber,
    A shock absorber body having a cylinder and a rod movably inserted in the cylinder in the axial direction;
    A tube member which is provided on the outer periphery of the shock absorber body and forms a liquid storage chamber for storing a liquid between the shock absorber body and the shock absorber body,
    A spring receiver that divides the liquid reservoir into an upper chamber and a lower chamber, and a flow path that connects the upper chamber and the lower chamber is formed between the buffer body and 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 that is located below an opening on the upper chamber side of the flow path and forms 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 narrowed portion is smaller than the inner diameter of the coil at the upper end of the coil spring.
  2. 　請求項１に記載の緩衝器であって、
    　前記ばね受けは、
    　筒状で前記緩衝器本体の外周に装着されるとともに、前記流路の上室側の開口となる窓が形成される本体部と、
    　前記本体部の下端に嵌合されて前記コイルばねの上端が当接するばね座と、
    　前記本体部と前記ばね座との間に設けた絞り部材とを有し、
    　前記絞り部材が前記絞り部となっている
    　ことを特徴とする請求項１に記載の緩衝器。     The shock absorber according to claim 1,
    The spring bearing is
    A body part that is attached to the outer periphery of the shock absorber body in a tubular shape and has a window that is an opening on the upper chamber side of the flow path,
    A spring seat, which is fitted to the lower end of the main body portion and abuts on the upper end of the coil spring,
    A throttle member provided between the main body and the spring seat,
    The shock absorber according to claim 1, wherein the throttle member is the throttle portion.
  3. 　請求項１に記載の緩衝器であって、
    　前記絞り部は、径方向へ移動可能とされている
    　緩衝器。     The shock absorber according to claim 1,
    The shock absorber is capable of moving in the radial direction.
  4. 　請求項１に記載の緩衝器であって、
    　前記ばね受けは、
    　筒状で前記緩衝器本体の外周に装着されるとともに、前記流路の上室側の開口となる窓が形成される本体部と、
    　前記本体部の下端部外周に嵌合される環状の外嵌部と、前記外嵌部の下端から内周側へ張り出して前記コイルばねの上端が当接する環状のシート部とを含むばね座とを有し、
    　前記シート部が前記絞り部となっている
    　緩衝器。     The shock absorber according to claim 1,
    The spring bearing is
    A body part that is attached to the outer periphery of the shock absorber body in a tubular shape, and has a window that forms an opening on the upper chamber side of the flow path,
    A spring seat including an annular outer fitting portion fitted to the outer circumference of the lower end portion of the main body portion, and an annular seat portion protruding from the lower end of the outer fitting portion to the inner circumferential side and in contact with the upper end of the coil spring. Have
    A shock absorber in which the seat portion serves as the throttle portion.
  5. 　請求項１に記載の緩衝器であって、
    　前記制限通路は、チョーク通路である
    　緩衝器。
          The shock absorber according to claim 1,
    The limiter passage is a choke passage.
PCT/JP2019/044068 2018-11-15 2019-11-11 Shock absorber WO2020100793A1 (en)

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JP2004251364A (en) * 2003-02-20 2004-09-09 Kayaba Ind Co Ltd Front fork
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JP2006183690A (en) * 2004-12-24 2006-07-13 Showa Corp Front fork for motorcycle or the like

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Publication number Priority date Publication date Assignee Title
JPH06109054A (en) * 1992-09-29 1994-04-19 Showa:Kk Hydraulic buffer for front fork
JP2004251364A (en) * 2003-02-20 2004-09-09 Kayaba Ind Co Ltd Front fork
JP2004286197A (en) * 2003-03-25 2004-10-14 Kayaba Ind Co Ltd Front fork
JP2006183690A (en) * 2004-12-24 2006-07-13 Showa Corp Front fork for motorcycle or the like

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