WO2018163868A1 - 緩衝器 - Google Patents
緩衝器 Download PDFInfo
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- WO2018163868A1 WO2018163868A1 PCT/JP2018/006759 JP2018006759W WO2018163868A1 WO 2018163868 A1 WO2018163868 A1 WO 2018163868A1 JP 2018006759 W JP2018006759 W JP 2018006759W WO 2018163868 A1 WO2018163868 A1 WO 2018163868A1
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- WIPO (PCT)
- Prior art keywords
- passage
- chamber
- disk
- damping force
- hole
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3482—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body the annular discs being incorporated within the valve or piston body
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/43—Filling or drainage arrangements, e.g. for supply of gas
- F16F9/437—Drainage arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/185—Bitubular units
Definitions
- the present invention relates to a shock absorber.
- This application claims priority on Japanese Patent Application No. 2017-046270 filed in Japan on March 10, 2017, the contents of which are incorporated herein by reference.
- Some shock absorbers have variable damping force in response to frequency (for example, see Patent Document 1).
- the present invention provides a shock absorber that can be miniaturized.
- a shock absorber is provided in a first passage through which a working fluid flows from one cylinder chamber by movement of a piston, a second passage provided in parallel with the first passage, and the first passage.
- a first damping force generating mechanism for generating a damping force, a bottomed cylindrical and annular case member penetrating through the shaft-shaped member and having at least a part of the second passage formed therein, and the shaft-shaped member
- an annular disk which is disposed to face the bottom of the case member in the case member and can be bent by the working fluid in the case member, and the case member is defined by the disk.
- the shock absorber can be reduced in size.
- the shock absorber 1 of the first embodiment is a so-called double cylinder type hydraulic shock absorber, and includes a cylinder 2 in which an oil liquid (not shown) as a working fluid is enclosed.
- the cylinder 2 includes a cylindrical inner cylinder 3, a bottomed cylindrical outer cylinder 4 having a larger diameter than the inner cylinder 3 and concentrically provided so as to cover the inner cylinder 3, and an upper opening of the outer cylinder 4.
- a cover 5 is provided so as to cover the side, and a reservoir chamber 6 is formed between the inner cylinder 3 and the outer cylinder 4.
- the outer cylinder 4 includes a cylindrical body member 11 and a bottom member 12 that is fitted and fixed to the lower side of the body member 11 and closes the lower portion of the body member 11.
- a mounting eye 13 is fixed to the bottom member 12 on the outer side opposite to the body member 11.
- the cover 5 has a cylindrical portion 15 and an inner flange portion 16 extending radially inward from the upper end side of the cylindrical portion 15.
- the cover 5 is covered with the barrel member 11 so that the upper end opening of the barrel member 11 is covered with the inner flange portion 16 and the outer peripheral surface of the barrel member 11 is covered with the cylindrical portion 15, and in this state, the cylindrical portion 15. Is fixed to the body member 11 by being crimped radially inward.
- the shock absorber 1 includes a piston 18 slidably fitted in the inner cylinder 3 of the cylinder 2.
- the piston 18 divides the inside of the inner cylinder 3 into two chambers, an upper chamber 19 (first cylinder chamber) and a lower chamber 20 (second cylinder chamber). Oil liquid as working fluid is sealed in the upper chamber 19 and the lower chamber 20 in the inner cylinder 3, and oil liquid and gas as working fluid are placed in the reservoir chamber 6 between the inner cylinder 3 and the outer cylinder 4. And are enclosed.
- the shock absorber 1 is provided with a piston rod 21 (shaft-shaped member) whose one end is disposed in the inner cylinder 3 of the cylinder 2 and connected to the piston 18 and whose other end extends to the outside of the cylinder 2.
- the piston 18 and the piston rod 21 move together.
- the piston rod 21 increases the protrusion amount from the cylinder 2
- the piston 18 moves to the upper chamber 19 side.
- the contraction stroke in which the piston rod 21 decreases the protrusion amount from the cylinder 2 the piston 18 moves downward. It will move to the chamber 20 side.
- a rod guide 22 is fitted to the upper end opening side of the inner cylinder 3 and the outer cylinder 4, and a seal member 23 is attached to the outer cylinder 4 on the upper side, which is the outer side of the cylinder 2, relative to the rod guide 22. Yes.
- a friction member 24 is provided between the rod guide 22 and the seal member 23.
- the rod guide 22, the seal member 23, and the friction member 24 all have an annular shape, and the piston rod 21 is slidably inserted into the rod guide 22, the friction member 24, and the seal member 23, respectively.
- the cylinder 2 extends from the inside to the outside.
- the rod guide 22 supports the piston rod 21 such that the piston rod 21 can move in the axial direction while restricting its radial movement, and guides the movement of the piston rod 21.
- the seal member 23 is in close contact with the outer cylinder 4 at the outer peripheral portion thereof, and is in sliding contact with the outer peripheral portion of the piston rod 21 that moves in the axial direction at the inner peripheral portion thereof. This prevents the high-pressure gas and oil liquid in the inner reservoir chamber 6 from leaking to the outside.
- the friction member 24 is in sliding contact with the outer peripheral portion of the piston rod 21 at the inner peripheral portion thereof, and generates frictional resistance on the piston rod 21. The friction member 24 is not intended for sealing.
- the rod guide 22 has a step shape in which the outer peripheral portion has a larger diameter at the upper portion than the lower portion. 4 is fitted to the inner periphery of the upper part.
- a base valve 25 that defines the lower chamber 20 and the reservoir chamber 6 is installed on the bottom member 12 of the outer cylinder 4, and the inner peripheral portion of the lower end of the inner cylinder 3 is fitted to the base valve 25. ing.
- a part (not shown) of the upper end portion of the outer cylinder 4 is caulked inward in the radial direction, and the caulking portion and the rod guide 22 sandwich the seal member 23.
- the piston rod 21 has a main shaft portion 27 and a mounting shaft portion 28 (shaft portion) having a smaller diameter.
- the attachment shaft portion 28 is disposed in the cylinder 2 and is attached with the piston 18 and the like.
- An end portion of the main shaft portion 27 on the mounting shaft portion 28 side is a shaft step portion 29 that spreads in the direction perpendicular to the axis.
- a passage groove 30 extending in the axial direction is formed at the outer peripheral portion of the mounting shaft portion 28 in the axial direction, and a male screw 31 is formed at the tip position opposite to the main shaft portion 27 in the axial direction. ing.
- a plurality of passage grooves 30 are formed at intervals in the circumferential direction of the mounting shaft portion 28, and the cross-sectional shape on the surface orthogonal to the central axis of the piston rod 21 is any one of a rectangle, a square, and a D-shape. It is formed to make.
- the piston rod 21 is provided with an annular stopper member 32 and a buffer 33 in the portion between the piston 18 and the rod guide 22 of the main shaft portion 27.
- the stopper member 32 is inserted through the piston rod 21 on the inner peripheral side, and is fixed to a fixing groove 34 that is crimped and recessed inward in the radial direction of the main shaft portion 27.
- the buffer 33 also has the piston rod 21 inserted inside, and is disposed between the stopper member 32 and the rod guide 22.
- a protruding portion of the piston rod 21 from the cylinder 2 is arranged at the top and supported by the vehicle body, and the mounting eye 13 on the cylinder 2 side is arranged at the bottom and connected to the wheel side.
- the cylinder 2 side may be supported by the vehicle body, and the piston rod 21 may be connected to the wheel side.
- the fluid resistance of the flow path formed in at least one of the piston 18 and the piston rod 21 is made different depending on the speed and amplitude of vibration. Is improved.
- inertial force and centrifugal force generated in the vehicle body as the vehicle travels also act.
- a centrifugal force is generated in the vehicle body when the traveling direction is changed by a steering operation, and a force based on the centrifugal force acts between the cylinder 2 and the piston rod 21.
- the shock absorber 1 has good characteristics with respect to vibration based on the force generated in the vehicle body as the vehicle travels, and high stability in vehicle travel can be obtained.
- the piston 18 is composed of a metal piston main body 35 supported by the piston rod 21 and an annular composite that is integrally mounted on the outer peripheral surface of the piston main body 35 and slides in the inner cylinder 3. And a sliding member 36 made of resin.
- the piston body 35 has a plurality of passage holes 37 for communicating the upper chamber 19 and the lower chamber 20 (only one location is shown in the cross-sectional view in FIG. 2), and a plurality for communicating the upper chamber 19 and the lower chamber 20.
- a passage hole 39 is provided (only one location is shown in FIG. 2 because of its cross section).
- the plurality of passage holes 37 are formed at an equal pitch in the circumferential direction of the piston body 35 with one passage hole 39 interposed therebetween, and constitute half of the passage holes 37, 39.
- one side of the piston 18 in the axial direction (upper side in FIG. 2) is opened radially outward
- the other side in the axial direction lower side in FIG. 2 is opened radially inward.
- the passage portions 38 in the passage holes 37 are provided with a damping force generation mechanism 41 (first damping force generation mechanism) that opens and closes the passage portions 38 to generate a damping force.
- the damping force generation mechanism 41 is disposed on the lower chamber 20 side in the axial direction, which is one end side in the axial direction of the piston 18, and is attached to the piston rod 21. By disposing the damping force generating mechanism 41 on the lower chamber 20 side, the plurality of passage portions 38 move from one upper chamber 19 to the other lower chamber 20 during the movement of the piston 18 toward the upper chamber 19 side, that is, the extension stroke. This is a passage through which oil liquid as a working fluid flows.
- the damping force generation mechanism 41 provided for these passage portions 38 suppresses the flow of oil from the extension side passage portion 38 to the lower chamber 20 and generates a damping force. It has become.
- the other half of the passage holes 39 shown in FIG. 2 are formed at equal pitches with one passage hole 37 between them in the circumferential direction, and the other side in the axial direction of the piston 18 (FIG. 2).
- the lower side is open radially outward and the one axial side (upper side in FIG. 2) is open radially inward.
- the passage part 40 in these passage holes 39 is provided with a damping force generation mechanism 42 that opens and closes the passage part 40 to generate a damping force.
- the damping force generating mechanism 42 is disposed on the axial upper chamber 19 side, which is the other end side of the piston 18 in the axial direction, and is attached to the piston rod 21.
- the damping force generating mechanism 42 By disposing the damping force generating mechanism 42 on the upper chamber 19 side, the plurality of passage portions 40 move oil from the lower chamber 20 toward the upper chamber 19 in the movement toward the lower chamber 20 side of the piston 18, that is, in the contraction stroke. It becomes a passage through which liquid flows.
- a damping force generation mechanism 42 provided for these passage portions 40 suppresses the flow of oil from the contraction side passage portion 40 to the upper chamber 19 and generates a damping force to generate a damping force. It has become.
- the passage portion 38 in the plurality of passage holes 37 and the passage portion 40 in the plurality of passage holes 39 cause the fluid that is the working fluid to move between the upper chamber 19 and the lower chamber 20 by the movement of the piston 18.
- the passage portion 38 communicates so that the fluid passes when the piston rod 21 and the piston 18 move to the extension side (the upper side in FIG. 2), and the passage portion 40 includes the piston rod 21 and the piston.
- the oil solution passes when 18 moves to the contraction side (the lower side in FIG. 2).
- the piston main body 35 has a substantially disc shape, and an insertion hole 44 is formed in the center in the radial direction so as to penetrate the mounting shaft portion 28 of the piston rod 21 through the axial direction.
- the insertion hole 44 has a small-diameter hole 45 on one side in the axial direction in which the mounting shaft part 28 of the piston rod 21 is fitted, and a large-diameter hole 46 on the other axial side larger in diameter than the small-diameter hole 45. is doing.
- An annular valve seat portion constituting a part of the damping force generation mechanism 41 is provided at an end portion on the lower chamber 20 side in the axial direction of the piston main body 35, radially outside the opening on the lower chamber 20 side of the passage hole 37. 47 is formed.
- the large-diameter hole portion 46 is provided closer to the valve seat portion 47 in the axial direction than the small-diameter hole portion 45.
- an annular valve constituting a part of the damping force generating mechanism 42 is provided at the end of the piston body 35 in the axial upper chamber 19 side, radially outside the opening of the passage hole 39 on the upper chamber 19 side.
- a sheet portion 48 is formed.
- the side opposite to the insertion hole 44 of the valve seat portion 47 has a stepped shape whose axial direction height is lower than that of the valve seat portion 47, and a shrinkage-side passage hole 39 is formed in this stepped portion.
- An opening on the lower chamber 20 side of the inner passage portion 40 is disposed.
- the side opposite to the insertion hole 44 of the valve seat portion 48 has a stepped shape whose axial direction is lower than the valve seat portion 48, and extends to this stepped portion.
- An opening on the upper chamber 19 side of the passage portion 38 in the side passage hole 37 is disposed.
- one disk 50, one disk 51, one pilot valve 52, and a plurality of sheets in order from the piston 18 side in the axial direction are provided by fitting the attachment shaft portions 28 of the piston rod 21 inside each.
- the disks 50, 51, 53, 55, 57 to 59, the spring disk 54, the case member 56, and the annular member 60 are all made of metal.
- Each of the disks 50, 51, 53, 55, 57 to 59 and the annular member 60 has a perforated circular flat plate shape with a fixed thickness to which the mounting shaft portion 28 of the piston rod 21 can be fitted.
- the spring disk 54, the pilot valve 52, and the case member 56 all have an annular shape in which the mounting shaft portion 28 of the piston rod 21 can be fitted.
- the case member 56 has a bottomed cylindrical shape and an annular shape, and includes a perforated disk-shaped bottom portion 71 in which a through-hole 70 penetrating in the thickness direction is formed, and an inner peripheral edge portion of the bottom portion 71.
- a cylindrical inner cylindrical portion 72 projecting to both sides along the outer periphery, a cylindrical outer cylindrical portion 73 projecting to one side along the axial direction of the bottom portion 71 from the outer peripheral edge portion of the bottom portion 71, and the bottom portion 71.
- an annular valve seat portion 74 protruding from the intermediate position in the radial direction to the opposite side of the outer cylindrical portion 73 along the axial direction of the bottom portion 71.
- the protruding amount of the outer cylindrical portion 73 from the bottom 71 is larger than the protruding amount of the inner cylindrical portion 72 on the outer cylindrical portion 73 side.
- the case member 56 passes through the attachment shaft portion 28 of the piston rod 21 through the through hole 70.
- a disc contact portion 62 having a flat annular seat surface 61 perpendicular to the central axis is formed on the bottom portion 71 on the outer cylindrical portion 73 side in the axial direction and the radial direction.
- An annular recess 64 having a stopper surface 63 that is recessed in the axial direction from the seat surface 61 is formed at a radial intermediate position of the portion 62.
- the concave portion 64 has a shape in which the radial width becomes narrower as the depth becomes deeper, and the cross section of the stopper surface 63 on the surface including the central axis of the bottom portion 71 has a constant arc shape regardless of the circumferential position. .
- the bottom portion 71 has a tapered portion 66 having a tapered surface 65 whose height from the sheet surface 61 increases toward the inner side in the radial direction inside the radial disk contact portion 62 on the outer cylindrical portion 73 side in the axial direction. Is formed.
- the tapered portion 66 is provided at the end portion on the inner cylindrical portion 72 side in the radial direction of the bottom portion 71.
- the bottom portion 71, the inner cylindrical portion 72, the outer cylindrical portion 73, the valve seat portion 74, the disk contact portion 62, the concave portion 64, and the tapered portion 66 are arranged coaxially, and their central axes are the case members 56.
- a through hole 67 (first through hole) penetrating along the axial direction of the bottom portion 71 is formed in the bottom portion 71 at the deepest bottom position of the recess portion 64, that is, the center position of the radial width of the recess portion 64. .
- a plurality of through holes 67 are formed in the bottom portion 71 at intervals in the circumferential direction of the bottom portion 71 (only one location is shown in FIG. 3 because of a partial cross section). Note that it is sufficient that at least one through hole 67 is provided in the bottom 71.
- the through hole 67 is disposed outside the valve seat portion 74 in the radial direction of the bottom portion 71.
- annular disk 69 is disposed so as to face the bottom 71 of the case member 56 in the case member 56.
- the disk 69 is a metal flat plate, and its outer diameter is slightly smaller than the maximum diameter of the sheet surface 61 of the disk contact portion 62, in other words, the inner diameter of the outer cylindrical portion 73 and larger than the maximum diameter of the stopper surface 63.
- the inner diameter is slightly larger than the minimum diameter of the seat surface 61 of the disk contact portion 62 and smaller than the minimum diameter of the stopper surface 63.
- the disk 69 is guided by the outer cylindrical portion 73 so as to restrict radial movement and is movable in the axial direction, and comes into surface contact with the sheet surface 61 to cover the entire stopper surface 63. ing.
- the disk 69 passes through the mounting shaft portion 28 of the piston rod 21.
- a through hole 67 formed at the deepest position of the concave portion 64 of the bottom 71 is provided so as to face the disc 69 in the axial direction with the radial position aligned.
- the disk 69 closes the through hole 67 by making surface contact with the sheet surface 61, and opens the through hole 67 by leaving the sheet surface 61.
- the disk 69 can be elastically deformed so as to enter the recess 64, and at that time, the disk 69 abuts against the boundary peripheral edge on both sides in the radial direction between the stopper surface 63 and the sheet surface 61 or the entire surface of the stopper surface 63. The closed state of the through hole 67 is maintained.
- a through hole 68 (second through hole) that penetrates along the axial direction of the case member 56 is formed at an intermediate position in the radial direction of the tapered portion 66.
- a plurality of through-holes 68 are formed at intervals in the circumferential direction of the bottom 71 (only one location is shown in FIG. 3 because of the partial cross section).
- the through hole 68 is disposed between the valve seat portion 74 and the inner cylindrical portion 72 in the radial direction of the bottom portion 71.
- the through hole 67 is provided outside the through hole 68 in the radial direction of the case member 56, that is, in the radial direction of the bottom portion 71.
- the through hole 70 on the inner periphery of the inner cylindrical portion 72 is formed with a small diameter hole 75 for fitting the mounting shaft portion 28 of the piston rod 21 on the valve seat portion 74 side in the axial direction.
- a large-diameter hole 76 having a larger diameter than the small-diameter hole 75 is formed on the side opposite to the sheet portion 74.
- the disk 50 has an outer diameter that is smaller than the inner diameter of the valve seat portion 47.
- the disc 50 is formed with a notch 81 extending radially outward from an inner peripheral edge that fits into the mounting shaft portion 28 of the piston rod 21.
- the passage portion 82 (introduction orifice) in the notch 81 is always in communication with the passage portion 38 of the piston 18, and the passage portion 38 is connected to the large-diameter hole portion of the piston 18 via the passage portion 82 in the notch 81. 46 and the passage portion 84 between the attachment shaft portion 28 and the passage portion 84 in the passage groove 30 of the piston rod 21 are always in communication.
- the disk 51 has an outer diameter larger than the outer diameter of the valve seat portion 47 of the piston 18.
- the disc 51 is in contact with the valve seat portion 47, and opens and closes the opening of the passage portion 38 in the passage hole 37 formed in the piston 18 by being separated from and in contact with the valve seat portion 47.
- the disc 51 has a notch 91 formed on the outer peripheral side, and the notch 91 crosses the valve seat portion 47 in the radial direction. Therefore, the inside of the notch 91 is a fixed orifice 92 that allows the passage portion 38 to always communicate with the lower chamber 20.
- the pilot valve 52 includes a metal disk 95 and a rubber seal member 96 fixed to the disk 95.
- the disk 95 has a perforated circular flat plate shape with a certain thickness capable of fitting the mounting shaft portion 28 of the piston rod 21 inside, and has an outer diameter slightly larger than the outer diameter of the disk 51.
- the seal member 96 is fixed to the outer peripheral side opposite to the piston 18 of the disk 95 and has an annular shape. In other words, the pilot valve 52 has an annular seal member 96 on the outer periphery thereof.
- the seal member 96 is slidably and liquid-tightly fitted to the inner peripheral surface of the outer cylindrical portion 73 of the case member 56 over the entire circumference, and the clearance between the pilot valve 52 and the outer cylindrical portion 73 is always kept at a constant level. Seal. In other words, the pilot valve 52 slidably and closely fits the seal member 96 to the outer cylindrical portion 73 of the case member 56.
- the space between the pilot valve 52, the case member 56, and the disc 69 is the back pressure chamber 101 (first chamber) communicating with the upper chamber 19, and the case A space between the bottom 71 of the member 56 and the disk 69 is a variable chamber 102 (second chamber) communicating with the lower chamber 20. Therefore, the two back pressure chambers 101 and the variable chamber 102 are defined by the disk 69 in the case member 56.
- the variable chamber 102 communicates with the passage portion 103 in the through hole 67 and always communicates with the lower chamber 20 via the passage portion 103 in the through hole 67.
- the disk 69 has a state in which the inner peripheral side and the outer peripheral side are in contact with the sheet surface 61 of the disk contact portion 62 over the entire periphery, and the inner peripheral side and the outer peripheral side of the sheet surface 61 and the stopper surface 63 are in the entire periphery. In the state where the both sides are in contact with the boundary edge and the state where the stopper surface 63 is in contact with the entire periphery, the fluid flow between the back pressure chamber 101 and the variable chamber 102 is blocked. In addition, the disk 69 allows oil fluid to flow between the back pressure chamber 101 and the variable chamber 102 in a state of being separated from the bottom 71.
- the spring disc 54 urges the disc 69 so as to abut against the seat surface 61.
- the spring disc 54, the disc 69, and the disc abutting portion 62 and the concave portion 64 of the case member 56 are connected to each other.
- the valve 105 is configured.
- the disc 69 which is the valve body of the check valve 105 is not clamped in the axial direction and is not fixed to any part.
- the disk 69 can be brought into contact with and separated from the abutting spring disk 54 and the bottom 71 of the case member 56.
- the disk 69 is a floating type free valve that is movable in the axial direction as a whole.
- the disc 69 is energized by only the spring disc 54 except for the hydraulic pressure, and is brought close to and away from the sheet surface 61.
- the disc 69 and the spring disc 54 of the check valve 105 are both made of metal only and do not use a rubber seal. Both the disk 69 and the spring disk 54 are integrally formed by pressing.
- the urging force of the spring disk 54 is set so that the disk 69 always blocks the flow of oil between the back pressure chamber 101 and the variable chamber 102 regardless of the pressure state of the back pressure chamber 101 and the variable chamber 102. You may do it. That is, the disk 69 may block the flow of the working fluid in at least one direction including the flow in both directions between the back pressure chamber 101 and the variable chamber 102.
- the disk 69 can be bent by the working fluid in the case member 56, and when the pressure in the back pressure chamber 101 becomes higher than the pressure in the variable chamber 102, the back pressure chamber 101. As described above, the back pressure chamber 101 is deformed so as to increase the volume of the back pressure chamber 101 and to decrease the volume of the variable chamber 102. Further, from this state, when the pressure difference between the pressure in the back pressure chamber 101 and the pressure in the variable chamber 102 becomes small, the disk 69 enters the recess 64 while blocking the communication between the back pressure chamber 101 and the variable chamber 102. The volume of the variable chamber 102 is increased by reducing the entry of the pressure, and the volume of the back pressure chamber 101 is decreased.
- variable chamber 102 When the pressure in the variable chamber 102 becomes higher than the pressure in the back pressure chamber 101 beyond the biasing force of the spring disk 54, the disk 69 moves away from the seat surface 61 against the biasing force of the spring disk 54. Thus, the variable chamber 102 and the back pressure chamber 101 are communicated.
- the plurality of discs 53 have the same outer diameter and an outer diameter smaller than the minimum inner diameter of the seal member 96 of the pilot valve 52.
- the plurality of disks 53 have an outer diameter that is smaller than the outer diameter of the inner cylindrical portion 72 of the case member 56 and larger than the large-diameter hole portion 76.
- the spring disk 54 has a flat plate-like substrate portion 111 having an outer diameter that is larger than the outer diameter of the disk 53 and smaller than the minimum inner diameter of the seal member 96 of the pilot valve 52, and a pressing plate that extends from the substrate portion 111.
- the substrate portion 111 has an annular shape, and the pressing plate portion 112 extends from the outer peripheral edge portion of the substrate portion 111 while being inclined in the axial direction and radially outward.
- a plurality of pressing plate portions 112 are formed at intervals in the circumferential direction of the substrate portion 111 (only one location is shown in FIG. 3 because of the cross section) and extends toward the disk 69 side. In the spring disc 54, the plurality of pressing plate portions 112 abut against the surface of the disc 69 on the pilot valve 52 side to urge the disc 69 toward the seat surface 61 and abut against the seat surface 61.
- the disk 55 has an outer diameter that is smaller than the substrate part 111 of the spring disk 54 and larger than the outer diameter of the inner cylindrical part 72 of the case member 56.
- the disc 55 is formed with a notch 115 extending radially outward from an inner peripheral edge portion that fits into the mounting shaft portion 28 of the piston rod 21.
- the passage 116 (introduction orifice) in the notch 115 is always in communication with the back pressure chamber 101, and the back pressure chamber 101 is connected to the large-diameter hole portion of the case member 56 through the passage 116 in the notch 115.
- the passage portion 118 between the shaft 76 and the mounting shaft portion 28 and the passage portion 84 in the passage groove 30 of the piston rod 21 are always in communication.
- the disc 51 can be seated on the valve seat 47 of the piston 18 as described above.
- the disc 51 and the pilot valve 52 constitute a damping valve 121.
- the damping valve 121 is provided in the passage portion 38 in the passage hole 37 formed in the piston 18, and suppresses the flow of oil and liquid caused by sliding the piston 18 toward the extension side (upper side in FIG. 3) to reduce the damping force. Is generated.
- the damping valve 121 constitutes a damping force generating mechanism 41 together with the valve seat portion 47 of the piston 18.
- the damping valve 121 When the damping valve 121 is opened by separating the disk 51 from the valve seat portion 47, the fluid from the passage portion 38 spreads radially between the piston 18 and the outer cylindrical portion 73 of the case member 56. It flows into the lower chamber 20 through the part 125.
- a passage portion 38 formed inside each of the plurality of passage holes 37, between the damping valve 121 and the valve seat portion 47, and between the piston 18 and the outer cylindrical portion 73 of the case member 56. Constitutes a passage 130 (first passage). As shown in FIG. 2, the passage 130 moves from one upper chamber 19 to the other in the movement toward the upper chamber 19 side of the piston 18, that is, in the extension stroke.
- the extension-side damping force generating mechanism 41 including the valve seat portion 47 and the damping valve 121 is provided in the passage 130, and is attenuated by opening and closing the passage 130 with the damping valve 121 to suppress the flow of oil. Generate power.
- the back pressure chamber 101 between the pilot valve 52, the case member 56, and the disk 69 closes the damping valve 121 in the direction of the piston 18, that is, the disk 51 is seated on the valve seat 47. Apply internal pressure in the valve direction.
- the valve opening of the damping valve 121 is adjusted by the pressure in the back pressure chamber 101. That is, the opening of the damping force generation mechanism 41 including the damping valve 121 is adjusted by the pressure in the back pressure chamber 101.
- the passage portion 82 in the notch 81 of the disc 51, the passage portion 83 between the large-diameter hole portion 46 of the piston 18 and the mounting shaft portion 28, the passage portion 84 in the passage groove 30 of the piston rod 21, and the disc 55 A back pressure chamber inflow passage portion 123 that constantly connects the passage portion 38 of the piston 18 and the back pressure chamber 101 and introduces oil from the passage portion 38 to the back pressure chamber 101. It has become.
- the case member 56, the disk 50, the damping valve 121, the plurality of disks 53, the spring disk 54, the disk 55, and the disk 69 have the back pressure chamber 101 and the back pressure chamber inflow passage portion 123.
- a mechanism portion 127 which is a valve opening control mechanism for applying pressure and controlling the valve opening is configured.
- the damping force generation mechanism 41 including the damping valve 121 and the mechanism unit 127 constitute a valve mechanism 128.
- the plurality of discs 57 have the same outer diameter and are slightly larger than the outer diameter of the valve seat portion 74.
- a plurality of discs 57 constitute a disc valve 131 that can be detachably seated on the valve seat portion 74.
- the disc valve 131 is separated from the valve seat portion 74 to allow the back pressure chamber 101 and the lower chamber 20 to communicate with each other via the passage portion 135 (bypass passage) in the through hole 68 and the fluid between them.
- the damping force is generated by suppressing the flow of the gas.
- a through hole 68 is provided in the bottom 71 of the case member 56 so as to face the disc valve 131.
- the passage portion 135 is provided in parallel with the first through hole 67 and communicates the back pressure chamber 101 and the lower chamber 20.
- the outer diameter of the disc 58 is smaller than that of the valve seat portion 74, and the outer diameter of the disc 59 is the same as that of the valve seat portion 74.
- the annular member 60 has an outer diameter larger than that of the disk valve 131 and has higher rigidity than the disk valve 131. The disk 59 and the annular member 60 abut against the disk valve 131 when the disk valve 131 is deformed in the opening direction, and restrict deformation beyond the regulation of the disk valve 131 in the opening direction.
- the passage portion 135 in the through hole 68, the space between the disc valve 131 and the valve seat portion 74, the variable chamber 102, and the passage portion 103 in the through hole 67 constitute a passage 140 (second passage). ing. Therefore, at least a part of the passage 140 is formed in the case member 56 having the back pressure chamber 101 therein.
- the passage 140 connects the upper chamber 19 and the lower chamber 20 through a route different from the passage 130.
- the passage portion 38 on the upper chamber 19 side is common to the passage 130, and the lower chamber 20 side is provided in parallel with the passage 130 from the passage portion 38. That is, the parallel passage 141 including the back pressure chamber inflow passage portion 123, the back pressure chamber 101, the passage portion 103, and the passage portion 135 of the passage 140 and the passage portion 125 of the passage 130 are arranged in parallel.
- a back pressure chamber inflow passage portion 123 including a passage portion 82 and a passage portion 116 is provided between the passage 130 and the back pressure chamber 101 so as to communicate with each other.
- the passage portion 82 and the passage portion 116 are introduction orifices provided in the back pressure chamber inflow passage portion 123 for introducing the oil liquid from the passage 130 into the back pressure chamber 101.
- a plurality of The passage portion 82 and the passage portion 116 are provided in series.
- the check valve 105 including the spring disk 54, the disk 69, and the bottom portion 71 of the case member 56 is provided in the parallel path 141 of the path 140 to restrict the flow of oil from the back pressure chamber 101 to the lower chamber 20. On the other hand, the flow of oil from the lower chamber 20 to the back pressure chamber 101 is allowed.
- the disc valve 131 is separated from the valve seat portion 74 when the pressure in the back pressure chamber 101 reaches a predetermined pressure.
- the disc valve 131 together with the valve seat portion 74, constitutes a damping force generating mechanism 145 (second damping force generating mechanism) that opens when the pressure in the back pressure chamber 101 reaches a predetermined pressure to generate a damping force.
- the damping force generation mechanism 145 is provided in the parallel passage 141 parallel to the passage 130 of the passage 140, and is provided in the passage portion 135 that communicates the back pressure chamber 101 and the lower chamber 20.
- the damping force generating mechanism 145 is provided outside the case member 56, and the disk valve 131 is disposed to face the bottom portion 71.
- a through hole 68 is provided in the bottom portion 71 of the case member 56 so as to face the disc valve 131 of the damping force generation mechanism 145.
- the contraction-side damping force generation mechanism 42 includes, in order from the axial piston 18 side, one disk 161, one disk 162, a plurality of disks 163, and a plurality of sheets. It has a disk 164, a single disk 165, a single disk 166, and a single annular member 167.
- the disks 161 to 166 and the annular member 167 are made of metal, and each of them has a perforated circular flat plate shape with a fixed thickness to which the mounting shaft portion 28 of the piston rod 21 can be fitted.
- the disk 161 has an outer diameter smaller than the inner diameter of the valve seat portion 48 of the piston 18.
- the disk 162 has an outer diameter slightly larger than the outer diameter of the valve seat portion 48 of the piston 18 and can be seated on the valve seat portion 48.
- the disc 162 has a notch 171 formed on the outer peripheral side, and the notch 171 crosses the valve seat portion 48 in the radial direction.
- the plurality of disks 163 have the same outer diameter and the same outer diameter as the disk 162.
- the plurality of disks 164 have the same outer diameter and an outer diameter that is smaller than the outer diameter of the disk 163.
- the disk 165 has an outer diameter that is smaller than the outer diameter of the disk 164.
- the disk 166 has an outer diameter larger than the outer diameter of the disk 164 and smaller than the outer diameter of the disk 163.
- the annular member 167 has an outer diameter smaller than the outer diameter of the disk 166, and is thicker and more rigid than the disks 161-166. The annular member 167 is in contact with the shaft step portion 29 of the piston rod 21.
- the discs 162 to 164 constitute a disc valve 172 that can be attached to and detached from the valve seat portion 48.
- the disc valve 172 is separated from the valve seat portion 48 to allow the passage portion 40 in the passage hole 39 to communicate with the upper chamber 19 and suppress the flow of oil between them to generate a damping force.
- Inside the notch 171 of the disk 162 is a fixed orifice 173 that allows the upper chamber 19 and the lower chamber 20 to communicate with each other even when the disk 162 is in contact with the valve seat portion 48.
- the disk 166 and the annular member 167 restrict deformation beyond the regulation in the opening direction of the disk valve 172.
- the extension side disk valve 131 and the contraction side disk valve 172 are both examples of inner side clamp disk valves.
- the present invention is not limited thereto, and any mechanism that generates a damping force may be used.
- the disk valve may be a lift-type valve that urges the disk valve with a coil spring, or may be a poppet valve.
- the mechanism portion 127 including the case member 56, the disk 50, the damping valve 121, the plurality of disks 53, the spring disk 54, the disk 55, and the disk 69 constitutes the valve opening control mechanism described above.
- a damping force variable mechanism that changes the damping force in response to the frequency of reciprocation of the piston 18 (hereinafter referred to as piston frequency) is also configured.
- the mechanism portion 127 is deformed in accordance with the reciprocating frequency of the piston 18 so that the capacity of the back pressure chamber 101 that always communicates with the upper chamber 19 and the variable chamber 102 that always communicates with the lower chamber 20. Change the capacity.
- the piston rod 21 is inserted with the attachment shaft portions 28 inside thereof, and the shaft step portion 29 is inserted into the annular member 167, the disk 166, the disk 165, the plurality of disks 164, the plurality of sheets.
- Disc 163, disc 162, disc 161, piston 18, disc 50, disc 51, pilot valve 52, plural discs 53, spring disc 54, disc 55, case member 56, plural discs 57, disc 58, disc 59 and the annular member 60 are stacked in this order.
- the disk 69 is disposed between the bottom 71 of the case member 56 and the spring disk 54.
- the case member 56 fits the seal member 96 of the pilot valve 52 into the outer cylindrical portion 73.
- a nut 185 is screwed to the male screw 31 of the mounting shaft portion 28 protruding from the annular member 60 in a state where the components are arranged in this way.
- the components from the annular member 167 to the annular member 60 stacked as described above are clamped in the axial direction, with the inner peripheral side or the whole being sandwiched between the shaft step portion 29 and the nut 185 of the piston rod 21.
- the disk 69 is not clamped in the axial direction and is sandwiched between the spring disk 54 and the case member 56.
- the nut 185 is a general-purpose hex nut.
- the base valve 25 described above is provided between the bottom member 12 of the outer cylinder 4 and the inner cylinder 3.
- the base valve 25 includes a base valve member 191 that partitions the lower chamber 20 and the reservoir chamber 6, a disk 192 provided on the lower side of the base valve member 191, that is, the reservoir chamber 6, and an upper side or lower side of the base valve member 191.
- a disk 193 provided on the chamber 20 side and a mounting pin 194 for attaching the disk 192 and the disk 193 to the base valve member 191 are provided.
- the base valve member 191 has an annular shape, and a mounting pin 194 is inserted in the center in the radial direction.
- the base valve member 191 includes a plurality of passage holes 195 through which oil is circulated between the lower chamber 20 and the reservoir chamber 6, and the lower chamber 20, the reservoir chamber 6, and the outside of the passage holes 195 in the radial direction.
- a plurality of passage holes 196 through which the oil liquid flows are formed.
- the disk 192 on the reservoir chamber 6 side allows the flow of oil from the lower chamber 20 to the reservoir chamber 6 through the passage hole 195, while the flow of oil from the reservoir chamber 6 to the lower chamber 20 through the passage hole 195. Suppress.
- the disk 193 permits the flow of oil from the reservoir chamber 6 to the lower chamber 20 through the passage hole 196, while suppressing the flow of oil from the lower chamber 20 to the reservoir chamber 6 through the passage hole 196.
- the disk 192 and the base valve member 191 constitute a contraction-side damping valve mechanism 197 that opens in the contraction stroke of the shock absorber 1 to flow oil from the lower chamber 20 to the reservoir chamber 6 and generate a damping force.
- the disc 193 and the base valve member 191 constitute a suction valve mechanism 198 that opens in the expansion stroke of the shock absorber 1 and flows oil from the reservoir chamber 6 into the lower chamber 20.
- the suction valve mechanism 198 allows the liquid to flow from the reservoir chamber 6 to the lower chamber 20 without substantially generating a damping force so as to compensate for the shortage of the liquid mainly caused by the extension of the piston rod 21 from the cylinder 2. Fulfills the function.
- the moving speed of the piston 18 (hereinafter referred to as piston speed) is At a later time, the oil from the upper chamber 19 flows from the passage portion 38 in the passage hole 37 shown in FIG. 3 to the fixed orifice 92 of the damping valve 121 of the damping force generating mechanism 41, the outer cylinder of the piston 18 and the case member 56. It flows into the lower chamber 20 through the passage 130 including the passage portion 125 between the shape portion 73 and a damping force having an orifice characteristic (a damping force is approximately proportional to the square of the piston speed) is generated. For this reason, as for the characteristic of the damping force with respect to the piston speed, the rate of increase of the damping force becomes relatively high as the piston speed increases.
- the fluid from the upper chamber 19 opens the damping valve 121 of the damping force generation mechanism 41, which is the main valve, from the passage portion 38 in the passage hole 37, while the valves of the damping valve 121 and the piston 18 are opened. It flows into the lower chamber 20 through the passage 130 including the gap with the seat portion 47 and the passage portion 125, and a damping force having a valve characteristic (a damping force is substantially proportional to the piston speed) is generated. For this reason, as for the characteristic of the damping force with respect to the piston speed, the rate of increase of the damping force decreases with an increase in the piston speed.
- the oil liquid from the upper chamber 19 flows into the lower chamber 20 through the passage 130 including the damping valve 121 and the valve seat portion 47 and the gaps of the damping force generating mechanism 41, While opening the disc valve 131 of the damping force generation mechanism 145, which is a hard valve, from the back pressure chamber inflow passage portion 123 and the back pressure chamber 101, the gap between the disc valve 131 and the valve seat portion 74 and the back pressure chamber inflow passage.
- the flow passes through the passage 140 including the portion 123 and the back pressure chamber 101 and flows into the lower chamber 20, thereby further suppressing an increase in damping force. For this reason, in the characteristic of the damping force with respect to the piston speed, the rate of increase of the damping force is further lowered as the piston speed increases.
- the damping valve 121 of the damping force generating mechanism 41 opens away from the valve seat portion 47 of the piston 18 while deforming the disc 51 and the pilot valve 52.
- the passage 140 including the passage portion 38 in the passage hole 37, the back pressure chamber inflow passage portion 123, the back pressure chamber 101, and the clearance between the disk valve 131 and the valve seat portion 74 of the damping force generation mechanism 145 is formed.
- the oil introduced from the lower chamber 20 into the passage portion 40 in the passage hole 39 on the contraction side basically opens the disc valve 172 of the damping force generation mechanism 42 and the disc valve 172. It flows to the upper chamber 19 through the space between the valve seat portion 48 and a damping force having a valve characteristic (a damping force is substantially proportional to the piston speed) is generated. For this reason, in the characteristic of the damping force with respect to the piston speed, the rate of increase of the damping force decreases with an increase in the piston speed.
- the mechanism unit 127 does not function as a damping force variable mechanism but functions as a valve opening control mechanism.
- the piston frequency It functions as a damping force variable mechanism that makes the damping force variable according to the above.
- the oil liquid is introduced from the upper chamber 19 into the back pressure chamber 101 while the disk 69 is deformed.
- the damping force generating mechanism passes from the upper chamber 19 through the passage portion 38 in the passage hole 37. While opening 41, the flow rate of the oil liquid flowing into the lower chamber 20 decreases.
- the damping valve 121 of the damping force generation mechanism 41 is easily opened. As a result, the damping force on the extension side becomes soft. At this time, the damping force generation mechanism 145 that is a hard valve does not open.
- the piston frequency when the piston frequency is high, the amount of oil introduced from the upper chamber 19 into the back pressure chamber 101 is small, so that the deformation of the disk 69 is small and the deformation is restricted by contacting the stopper surface 63. It will not be. Therefore, the damping force becomes soft at each extension stroke.
- the pressure of the back pressure chamber 101 increases by the rigidity (spring reaction force) of the disk 69.
- the piston frequency since the piston frequency is high and the deflection of the disk 69 is small, the pressure of the back pressure chamber 101 is low. The rise can be suppressed, and the influence on the ease of opening the damping valve 121 can be suppressed.
- the amplitude of the piston 18 is large.
- the oil is transferred from the upper chamber 19 to the back pressure chamber 101 in the same manner as described above.
- the liquid flows, the amount of oil flowing into the back pressure chamber 101 is large and the deformation of the disk 69 is large. Thereafter, the disk 69 comes into contact with the stopper surface 63 and further deformation is restricted, and the upper chamber The oil no longer flows from 19 to the back pressure chamber 101. Since the oil liquid does not flow from the upper chamber 19 into the back pressure chamber 101, the pressure in the back pressure chamber 101 rises and the valve opening of the damping valve 121 of the damping force generation mechanism 41 is suppressed.
- the damping force generation mechanism 41 is in a state where the damping valve 121 does not open and the oil liquid flows from the upper chamber 19 to the lower chamber 20 through the fixed orifice 92, and the damping force on the expansion side becomes hard.
- the oil liquid opens the disc valve 131 of the damping force generation mechanism 145 that is a hard valve, and the gap between the disc valve 131 and the valve seat portion 74 and the back pressure chamber inflow passage portion 123. And the back pressure chamber 101 through the passage 140 to the lower chamber 20.
- the mechanism 127 when the mechanism 127 is in the contraction stroke, the pressure in the lower chamber 20 becomes higher, and the pressure in the variable chamber 102 becomes higher than the pressure in the back pressure chamber 101.
- the disc 69 of the check valve 105 is separated from the seat surface 61 against the biasing force of the spring disc 54.
- the check valve 105 opens the passage 140 including the passage portion 103 in the through hole 67, and the oil liquid flows from the lower chamber 20 toward the upper chamber 19.
- the disc 69 is separated from the seat surface 61 so that there is no differential pressure, and further movement is suppressed.
- the urging force of the spring disk 54 is sufficient if the disk 69 is in contact with the seat surface 61 in the absence of a load pressure.
- the spring disk 54 functions as the check valve 105, the preload is applied excessively. It is not preferable.
- FIG. 4 shows the characteristics of the damping force with respect to the frequency when swept with constant maximum piston speed obtained by simulation. It can be seen from FIG. 4 that the damping force can be varied sufficiently between when the piston frequency is low and when it is high.
- FIG. 5 shows a Lissajous waveform showing the relationship between the piston stroke and the damping force obtained by the simulation
- FIG. 6 is an enlarged view of the range X in FIG. 5 and 6, it can be seen that the Lissajous waveform becomes smooth and the riding comfort is improved.
- Patent Document 1 The one described in Patent Document 1 described above has a large damping force variable mechanism, and there is room for improvement in terms of miniaturization.
- the mechanism portion 127 as a damping force variable mechanism has an annular disc 69 facing the bottom portion 71 of the case member 56 in the bottomed cylindrical case member 56. Is provided to define the back pressure chamber 101 and the variable chamber 102, and the through hole 67 is provided in the bottom 71 of the case member 56 so as to face the disk 69, so that the size, weight, simplification, and number of parts are reduced. Reduction and cost reduction.
- the mechanism 127 is structured to be attached to the piston rod 21, the basic length of the shock absorber 1 can be shortened by downsizing the mechanism 127.
- the mechanism unit 127 serves both as a damping force variable mechanism and a valve opening control mechanism, it is smaller, lighter, simplified, reduced in the number of parts, lower in cost and basic compared to the case where these are provided separately.
- the length can be shortened.
- the disk 69 is a floating type biased by the spring disk 54, it functions well as the check valve 105.
- a damping force generation mechanism 145 different from the damping force generation mechanism 41 is disposed outside the case member 56 so as to face the bottom portion 71, and the bottom portion 71 of the case member 56 faces the damping force generation mechanism 145. Since the through hole 68 is provided, the damping force generating mechanism 145 can be arranged in a compact manner.
- the damping force generating mechanism 145 facing the through hole 68 can be reduced in the radial direction.
- the rigidity increases and the valve opening pressure increases. Therefore, for example, by forming the through hole 67 obliquely, that is, by arranging it obliquely so that the lower chamber 20 side end of the through hole 67 is on the inner cylinder 3 side, the diameter of the valve seat portion 74 is increased, and the disk The rigidity of the valve 131 can be reduced by increasing the diameter.
- the outer diameters of the disk contact portion 62 and the disk 69 are arranged so that the large diameter portion and the small diameter portion are alternately arranged, that is, like a petal shape, and the disk contact portion 62 has a shape matching the shape.
- the through hole 67 can be disposed on the outer diameter side, the valve seat 74 can be increased in diameter, and the disk valve 131 can also be increased in diameter, thereby reducing the rigidity.
- the opening of the damping force generation mechanism 41 is adjusted by the pressure of the back pressure chamber 101, the opening of the damping force generation mechanism 41 can be adjusted by the pressure.
- passage portions 82 and 116 are provided in series as introduction orifices between the passage 130 and the back pressure chamber 101, even if the passage area of each of the passage portions 82 and 116 is relatively large, The flow rate can be reduced sufficiently. Therefore, the passage portions 82 and 116 can be easily formed.
- the case member 56, the disk 69, and the disk valve 131 are partially different from the first embodiment.
- the case member 56 of the second embodiment is similar to the first embodiment in that the disc contact portion 62 having the seat surface 61, the recess portion 64 having the stopper surface 63, and the bottom portion 71 are pivoted.
- a through hole 67 penetrating along the direction is formed not on the outer cylindrical portion 73 side in the radial direction of the bottom portion 71 but on the inner cylindrical portion 72 side.
- the through hole 67 is disposed between the valve seat portion 74 and the inner cylindrical portion 72 in the radial direction of the bottom portion 71.
- annular valve seat portion 201 protruding from the bottom portion 71 along the axial direction of the bottom portion 71 to the same side as the valve seat portion 74 is provided on the radially outer side of the valve seat portion 74 of the bottom portion 71.
- the through hole 68 is disposed between the valve seat portion 74 and the valve seat portion 201 in the radial direction of the bottom portion 71. Accordingly, the through hole 67 is provided on the inner side of the through hole 68 in the radial direction of the case member 56, that is, in the radial direction of the bottom 71.
- the disc 69 of the second embodiment is more inward and outward than the first embodiment in conformity with the disc contact portion 62, the concave portion 64 and the through hole 67 being arranged on the inner cylindrical portion 72 side in the radial direction of the bottom portion 71. Both diameters are small.
- the disc 69 of the second embodiment is also configured so that the inner and outer peripheral sides thereof are in surface contact with the sheet surface 61 of the disc contact portion 62 over the entire circumference.
- the disk valve 131 has an outer diameter disk 205 slightly larger than the outer diameter of the valve seat 201 in order from the axial case member 56 side.
- a plurality of disks 206 having a small outer diameter and a spring disk 207 are held between the case member 56 and the disk 58.
- the disc 205 can be detached from and seated on the valve seat portion 201, and is separated from the valve seat portion 201 by the pressure of the back pressure chamber 101 received through the passage portion 135 in the through hole 68.
- the back pressure chamber 101 and the lower chamber 20 are communicated with each other through the passage portion 135, and the flow of the oil liquid therebetween is suppressed to generate a damping force.
- a through-hole 211 is formed in the disk 205 along the axial direction to form a passage portion 210 that allows the variable chamber 102 and the lower chamber 20 to always communicate with each other via the passage portion 103 in the through-hole 67.
- the spring disk 207 has a flat plate-like substrate part 215 having an outer diameter larger than the outer diameter of the disk 206, and a pressing plate part 216 extending obliquely from the substrate part 215.
- the substrate portion 215 has an annular shape, and the pressing plate portion 216 extends from the outer peripheral edge portion of the substrate portion 215 so as to be inclined in the axial direction and radially outward.
- the pressing plate portion 216 is inclined so as to be closer to the disk 205 toward the extended tip side, and a plurality of the pressing plate portions 216 are formed at intervals in the circumferential direction of the substrate portion 215 (only one location is shown in FIG. 8 because of the cross section).
- a plurality of pressing plate portions 216 are in contact with the outer diameter side of the disk 205 opposite to the case member 56 to press the disk 205 against the valve seat portions 74 and 201.
- the through hole 67 is provided inside the through hole 68 of the bottom portion 71, in other words, the through hole 68 is located outside the through hole 67 of the bottom portion 71. Therefore, the diameter of the disc valve 131 of the damping force generation mechanism 145 facing the through hole 68 can be increased, and the valve opening pressure of the disc valve 131 can be easily adjusted.
- the spring disk 54 is not provided, and the case member 56 and the disk 69 are partially different from the second embodiment.
- the case member 56 of the third embodiment has no portion protruding to the same side as the outer cylindrical portion 73 of the inner cylindrical portion 72, and the sheet surface 61 extends to the through hole 70. Further, no large-diameter hole 76 is formed on the inner peripheral side of the inner cylindrical portion 72.
- the disc 69 has the mounting shaft portion 28 of the piston rod 21 fitted on the inner peripheral side thereof. Further, the number of the disks 53 is smaller than that in the second embodiment, and the disk 55 having the notch 115 forming the passage portion 116 is in contact with the disk 53.
- the disc 69 of the third embodiment is a clamp type in which the inner peripheral side is clamped so as not to move in the axial direction with respect to the piston rod 21.
- a small-diameter hole 235 for fitting the mounting shaft portion 28 of the piston rod 21 is formed on the inner periphery of the annular member 231 on the axial disk 232 side.
- the small-diameter hole 235 is formed on the axial disk 55 side.
- a large-diameter hole 236 having a large diameter is formed.
- the back pressure chamber inflow passage portion 123 introduces oil from the passage portion 38 to the back pressure chamber 101 by always communicating with the passage 101.
- the valve rigidity of the disk 69 is increased, the variable characteristic of the damping force with respect to the frequency is reduced, and the soft side The damping force increases slightly. Further, since the valve rigidity of the disk 69 is increased, the non-linearity when contacting the stopper surface 63 is weakened accordingly, and the Lissajous waveform becomes smoother.
- the damping force generation mechanism 145 is not provided outside the case member 56 but is provided inside the piston rod 21.
- the mounting shaft portion 28 of the piston rod 21 of the fourth embodiment is formed with a hole portion 241 that opens to the opposite side to the main shaft portion 27 in the axial direction.
- the hole 241 has a small-diameter hole 242, a tapered hole 243, an intermediate hole 244, and a screw hole 245 in order from the bottom side.
- the intermediate hole portion 244 has a larger diameter than the small diameter hole portion 242, and the tapered hole portion 243 has a tapered shape with a larger diameter toward the intermediate hole portion 244 side so as to connect them.
- the mounting shaft portion 28 is formed with a radial hole 248 that forms a passage portion 247 that opens the passage portion 84 in the passage groove 30 into the small diameter hole portion 242.
- valve body 252 Inside the hole portion 241, a valve body 252 that contacts the valve seat portion 251 at the boundary between the small-diameter hole portion 242 and the tapered hole portion 243 over the entire circumference, and the valve body 252 is biased in a direction to contact the valve seat portion 251 And a cover member 254 that holds the spring 253 between the valve body 252 and is screwed into the screw hole portion 245.
- the lid member 254 is formed with a through hole 255 penetrating in the axial direction. The valve body 252 can be separated from the valve seat portion 251 while the spring 253 is contracted.
- the passage portion 84 in the passage groove 30, the passage portion 247 in the radial hole 248, the passage portion 256 in the hole portion 241, and the passage portion 257 in the through hole 255 are partially in parallel with the passage 130.
- the passage 140 can communicate with the upper chamber 19 and the lower chamber 20.
- the passage 260 is configured to allow the back pressure chamber 101 to communicate with the passage 140.
- the valve seat portion 251, the valve body 252 and the spring 253 are the damping force generating mechanism 145 that opens when the pressure in the back pressure chamber 101 reaches a predetermined pressure to generate a damping force. ing.
- the damping force generation mechanism 145 When the damping force generation mechanism 145 is opened, the oil from the upper chamber 19 flows into the passage portion 38 of the piston 18, the passage portion 82 of the disk 50, the passage portion 83 in the large-diameter hole portion 46 of the piston 18, A disk which flows from the upper chamber 19 to the lower chamber 20 through the passage portion 84, the passage portion 247 and the passage portion 256 of the piston rod 21 and the passage portion 257 of the lid member 254, and is an introduction orifice on the back pressure chamber 101 side. 55 passage portions 116 do not pass.
- the damping force generating mechanism 145 is provided in the piston rod 21, the valve seat portions 74 and 201 and the through hole 68 of the case member 56 are not provided, and the disc valve 131 and the disc 59 are not provided. Instead of the disk valve 131 and the disk 59, a plurality of disks 58 are provided.
- the damping force generating mechanism 145 is provided in the piston rod 21, the structure around the piston rod 21 can be simplified.
- the present invention is not limited to this, and the outer cylinder is eliminated, and the upper chamber 19 of the lower chamber 20 in the cylinder 2 is slid to the opposite side. It may be used for a monotube type hydraulic shock absorber that forms a gas chamber with a movable partition body, and may be used for any shock absorber including a pressure control valve using a packing valve having a structure in which a seal member is provided on a disk. it can.
- a packing valve having a structure in which a seal member is provided on a disk. it can.
- the present invention is also applicable to the case where an oil passage communicating with the inside of the cylinder 2 is provided outside the cylinder 2 and a damping force generating mechanism is provided in the oil passage.
- a damping force generating mechanism is provided in the oil passage.
- the hydraulic shock absorber was shown as an example, water and air can also be used as a fluid.
- the shock absorber is slidably fitted in the cylinder in which the working fluid is sealed, and the first cylinder chamber, A piston partitioned into two cylinder chambers, a piston rod having one end connected to the piston and the other end extending to the outside of the cylinder, and a first fluid that flows from one of the cylinder chambers by movement of the piston.
- Working fluid An annular disc capable of bending, a first chamber defined by the disc in the case member, and a second chamber communicating with the first cylinder chamber and a second chamber communicating with the second cylinder chamber, A first through hole provided in the bottom portion of the case member and communicating with the second chamber; a bypass passage provided in parallel with the first through hole and communicating the first chamber and the second cylinder chamber; And a second damping force generating mechanism that is provided in the bypass passage and opens when the pressure in the first chamber reaches a predetermined pressure to generate a damping force.
- the disc is a floating type biased by a spring means.
- the disk functions well as a check valve.
- the disc is a clamp type that is partially clamped. As a result, the valve rigidity of the disk increases, and the damping force variation with respect to the frequency becomes gradual.
- the second damping force generation mechanism is disposed outside the case member so as to face the bottom, and the bottom includes A second through hole is provided opposite to the second damping force generation mechanism.
- the 2nd damping force generation mechanism can be arranged compactly.
- the first through hole is provided outside the second through hole in the bottom portion.
- the second damping force generation mechanism facing the first through hole can be made compact in the radial direction.
- the first through hole is provided inside the second through hole in the bottom portion. Therefore, the diameter of the second damping force generation mechanism facing the second through hole can be increased, and the valve opening pressure can be easily adjusted.
- the first damping force generation mechanism is adjusted to open by the pressure of the case chamber, and the first passage and An introduction orifice is provided between the case chamber and the case chamber. Thereby, the valve opening of the first damping force generation mechanism can be adjusted by the pressure in the case chamber.
- a plurality of the introduction orifices are provided in series. Thereby, even if the passage area of each introduction orifice is relatively large, the oil liquid can be sufficiently squeezed, and the formation becomes easy.
- the shock absorber can be reduced in size.
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
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- Fluid-Damping Devices (AREA)
Abstract
Description
本願は、2017年3月10日に日本に出願された特願2017-046270号について優先権を主張し、その内容をここに援用する。
本発明に係る第1実施形態を図1~図6に基づいて説明する。なお、以下においては、説明の便宜上、図面における上側を「上」とし、図面における下側を「下」として説明する。
次に、第2実施形態を主に図7,図8に基づいて第1実施形態との相違部分を中心に説明する。なお、第1実施形態と共通する部位については、同一称呼、同一の符号で表す。
次に、第3実施形態を主に図9,図10に基づいて第2実施形態との相違部分を中心に説明する。なお、第1実施形態と共通する部位については、同一称呼、同一の符号で表す。
次に、第4実施形態を主に図11,図12に基づいて第2実施形態との相違部分を中心に説明する。なお、第2実施形態と共通する部位については、同一称呼、同一の符号で表す。
2 シリンダ
18 ピストン
19 上室(第1シリンダ室)
20 下室(第2シリンダ室)
21 ピストンロッド(軸状部材)
28 軸部(取付軸部)
41 減衰力発生機構(第1減衰力発生機構)
54 バネディスク(バネ手段)
56 ケース部材
67 貫通穴(第1貫通穴)
68 貫通穴(第2貫通穴)
69 ディスク
71 底部
82,116 通路部(導入オリフィス)
101 背圧室(第1室)
102 可変室(第2室)
130 通路(第1通路)
135 通路部(バイパス通路)
140 通路(第2通路)
145 減衰力発生機構(第2減衰力発生機構)
Claims (8)
- 作動流体が封入されるシリンダと、
前記シリンダ内に摺動可能に嵌装され、該シリンダ内を第1シリンダ室、第2シリンダ室に区画するピストンと、
一端側が前記ピストンに連結されると共に他端側が前記シリンダの外部に延出されるピストンロッドと、
前記ピストンの移動により一方の前記シリンダ室から作動流体が流れ出す第1通路と、
前記第1通路と並列に設けられる第2通路と、
前記第1通路に設けられて減衰力を発生させる第1減衰力発生機構と、
軸状部材に貫通し、内部に前記第2通路の少なくとも一部が形成される有底筒状で環状のケース部材と、
前記軸状部材に貫通し、前記ケース部材内の該ケース部材の底部に対向して配置され、前記ケース部材内の作動流体により撓み可能な環状のディスクと、
前記ケース部材内を前記ディスクにより画成されて設けられ、前記第1シリンダ室と連通する第1室および前記第2シリンダ室と連通する第2室と、
前記ケース部材の前記底部に設けられ、前記第2室と連通する第1貫通穴と、
該第1貫通穴と並列に設けられ、前記第1室と前記第2シリンダ室とを連通するバイパス通路と、
該バイパス通路に設けられ、第1室内の圧力が所定圧力に達した時に開弁して減衰力を発生させる第2減衰力発生機構と、
を有する緩衝器。 - 前記ディスクは、バネ手段で付勢されるフローティングタイプである請求項1記載の緩衝器。
- 前記ディスクは、部分的にクランプされるクランプタイプである請求項1記載の緩衝器。
- 前記第2減衰力発生機構は、前記ケース部材外に前記底部に対向して配置されており、
前記底部には、前記第2減衰力発生機構と対向して第2貫通穴が設けられている請求項1乃至3のいずれか一項記載の緩衝器。 - 前記第1貫通穴は、前記底部の前記第2貫通穴よりも外側に設けられている請求項4記載の緩衝器。
- 前記第1貫通穴は、前記底部の前記第2貫通穴よりも内側に設けられている請求項4記載の緩衝器。
- 前記第1減衰力発生機構は、前記ケース室の圧力により開弁が調整されることになり、
前記第1通路と前記ケース室との間に導入オリフィスが設けられている請求項1乃至6のいずれか一項記載の緩衝器。 - 前記導入オリフィスが直列に複数設けられている請求項7記載の緩衝器。
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KR1020197024222A KR102232127B1 (ko) | 2017-03-10 | 2018-02-23 | 완충기 |
JP2019504474A JP6838220B2 (ja) | 2017-03-10 | 2018-02-23 | 緩衝器 |
US16/491,657 US11199241B2 (en) | 2017-03-10 | 2018-02-23 | Damper |
CN201880008761.8A CN110214239B (zh) | 2017-03-10 | 2018-02-23 | 缓冲器 |
DE112018001280.8T DE112018001280T5 (de) | 2017-03-10 | 2018-02-23 | Stoßdämpfer |
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DE112022002771T5 (de) | 2021-05-27 | 2024-03-07 | Hitachi Astemo, Ltd. | Stossdämpfer und Frequenzabhängiger Mechanismus |
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