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WO2019031405A1 - Amortisseur - Google Patents

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Publication number
WO2019031405A1
WO2019031405A1 PCT/JP2018/029233 JP2018029233W WO2019031405A1 WO 2019031405 A1 WO2019031405 A1 WO 2019031405A1 JP 2018029233 W JP2018029233 W JP 2018029233W WO 2019031405 A1 WO2019031405 A1 WO 2019031405A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
disc
piston
sheet
disk
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2018/029233
Other languages
English (en)
Japanese (ja)
Inventor
島崎　聡
幹郎 山下
定知 松村
吉田　豊
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
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
Application filed by Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Priority to DE112018004049.6T priority Critical patent/DE112018004049T5/de
Priority to JP2019535174A priority patent/JP6921201B2/ja
Priority to CN201880051425.1A priority patent/CN110998130B/zh
Publication of WO2019031405A1 publication Critical patent/WO2019031405A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—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
    • F16F9/3484—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 characterised by features of the annular discs per se, singularly or in combination

Definitions

  • the present invention relates to a shock absorber.
  • Priority is claimed on Japanese Patent Application No. 2017-154817, filed Aug. 9, 2017, the content of which is incorporated herein by reference.
  • the present invention provides a shock absorber capable of reducing the rate of increase in damping force to increase in piston speed with a simple structure.
  • the shock absorber is connected to the cylinder in which the working fluid is enclosed, the piston slidably inserted in the cylinder to define the inside of the cylinder into two chambers, and the piston And a passage through which the working fluid flows by sliding of the piston, and a damping force generating mechanism provided in the passage to control the flow of the working fluid to generate a damping force.
  • the damping force generation mechanism includes: a valve body having the passage extending therethrough; a substantially circular outer sheet formed to protrude from the valve body so as to surround an opening of the passage; and the outer sheet on the valve body And a disk-shaped disc valve which is seated on the outer sheet and the inner sheet and which is seated on the outer peripheral sheet by bending on the outer peripheral side.
  • the outer sheet has at least one of an inner-peripheral-side tapered portion whose inner-peripheral side expands as it faces the seat surface on which the disc valve is seated, or an outer-peripheral-side tapered portion whose outer peripheral side shrinks.
  • the disc valve has at least one of an inner protrusion radially opposed to the inner tapered portion or an outer protrusion radially opposed to the outer tapered portion in a valve closed state seated on the outer seat.
  • the shock absorber 10 of the first embodiment is a fluid pressure shock absorber that uses liquid or gas as a working fluid.
  • the shock absorber 10 is a hydraulic shock absorber that uses oil as a working fluid.
  • the shock absorber 10 has a cylinder 11 in which a working fluid is enclosed.
  • the cylinder 11 has a bottomed cylindrical shape whose one end side (upper side in FIG. 1) is open but the other end side (lower side in FIG. 1) is closed.
  • a piston 12 is slidably inserted into the cylinder 11.
  • the piston rod 13 is inserted into the cylinder 11.
  • the piston 12 is connected to one end side (lower side in FIG. 1) of the piston rod 13 by a nut 14.
  • the other end side (upper side in FIG. 1) of the piston rod 13 extends to the outside of the cylinder 11.
  • the other end of the piston rod 13, one end of which is connected to the piston 12, is inserted into the rod guide 15 and the oil seal 16 attached to the opening of the cylinder 11 and extends outside the cylinder 11.
  • the piston 12 has a first chamber 19 between the inside of the cylinder 11 and the free piston 18 on the bottom 17 side (lower side in FIG. 1) of the cylinder 11 and an opening side (FIG. 1) from which the piston rod 13 extends.
  • Upper chamber and the second chamber 20.
  • the piston rod 13 has a main shaft 25 and an attachment shaft 26 at the end of the piston rod 13 in the cylinder 11 and smaller in diameter than the main shaft 25.
  • the main shaft portion 25 is formed with an end surface 27 which spreads in the direction orthogonal to the axial direction at an end portion on the mounting shaft portion 26 side.
  • An external screw 28 is formed on the mounting shaft 26 so as to screw the female screw 30 of the nut 14 in a predetermined range opposite to the main shaft 25.
  • the piston 12 has an annular piston main body 31 (valve main body), and an annular band-like sliding contact member 33 mounted on the outer peripheral surface of the piston main body 31 and in sliding contact with the inner peripheral surface of the cylinder 11.
  • the piston 12 formed of the piston main body 31 and the sliding contact member 33 has an annular shape.
  • the piston body 31 is made of metal.
  • the piston body 31 is integrally formed by sintering.
  • the sliding contact member 33 is made of synthetic resin. The central axis line of the piston main body 31 and the piston 12 to which the sliding contact member 33 is integrally mounted are made to coincide with each other.
  • the axial direction which is a direction along a central axis line corresponds with piston main body 31 and piston 12
  • the radial direction which is a direction which intersects perpendicularly with a central axis line corresponds
  • the circumferential direction which is a direction around a central axis line corresponds.
  • An insertion hole 35 through which the mounting shaft portion 26 of the piston rod 13 is inserted without a gap is formed at the center in the radial direction of the piston main body 31 so as to penetrate in the axial direction.
  • a first passage hole 41 and a second passage hole 42 extending in the axial direction of the piston main body 31 are formed in the piston main body 31 at positions outside the radial direction insertion hole 35.
  • the first passage hole 41 is disposed on the inner peripheral side in the radial direction of the piston main body 31 with respect to the first chamber 19 side than the second chamber 20 side.
  • the second passage hole 42 is arranged on the inner peripheral side in the radial direction of the piston main body 31 with respect to the second chamber 20 side than the first chamber 19 side.
  • the piston main body 31 is provided with a plurality of first passage holes 41 (shown only at one place in FIG. 2 as a cross section).
  • the second passage holes 42 are also provided in the same plurality as the first passage holes 41 (only one place is shown in FIG. 2 in cross section).
  • the first passage holes 41 and the second passage holes 42 are alternately arranged in the circumferential direction of the piston main body 31.
  • an opening surface 52 On the side of the first chamber 19 in the piston main body 31 is formed an opening surface 52 in which the opening 51 on the first chamber 19 side of all the first passage holes 41 is opened.
  • An opening surface 54 is formed outside the opening surface 52 in the radial direction of the piston main body 31 so as to open the openings 53 on the first chamber 19 side of all the second passage holes 42.
  • the piston main body 31 is formed substantially in the axial direction of the piston main body 31 so as to protrude from the opening surfaces 52 and 54 so as to surround the entire opening 51 in the radial direction of the piston main body 31 on the first chamber 19 side.
  • a circular first outer sheet 61 (outer sheet) is provided.
  • the first outer sheet 61 has an inner tapered surface 62, an outer tapered surface 63, and a tip surface 64.
  • the radially inner side of the inner tapered surface 62 has a larger diameter (the inner diameter is enlarged) as the protruding tip side (toward the sheet surface) protrudes.
  • the outer tapered surface 63 has a smaller diameter toward the tip end side (toward the sheet surface) protruding radially outward (the outer diameter is reduced).
  • the end surface 64 is a flat surface which spreads in a direction orthogonal to the axial direction on the protruding end side.
  • a projecting distal end side of the first outer sheet 61 has these tapered surfaces 62 and 63 and a distal end surface (seat surface) 64, and a first width gradually decreasing portion 65 (a width gradually decreases toward the projecting distal end Gradually declining
  • An opening surface 52 is disposed radially inward of the tapered surface 62.
  • An opening surface 54 is disposed radially outside the tapered surface 63.
  • the piston main body 31 is provided with a substantially circular first inner sheet 71 (inner sheet) on the side of the first chamber 19.
  • the first inner sheet 71 is disposed radially inward of the piston main body 31 than the first outer sheet 61.
  • the first inner sheet 71 is formed to protrude in the axial direction of the piston main body 31 more than the opening surface 52.
  • the first inner sheet 71 is formed inside the first outer sheet 61 in the piston main body 31 so as to protrude from the opening surface 52.
  • the first inner sheet 71 has a tapered surface 72 and a tip surface 73.
  • the tapered surface 72 has a diameter smaller outward in the radial direction toward the protruding tip side.
  • the end surface 73 is a flat surface which spreads in a direction orthogonal to the axial direction on the protruding end side.
  • the inner peripheral side of the first inner sheet 71 is an insertion hole 35.
  • the outer diameter of the end surface 73 is substantially equal to the outer diameter of the end surface 27 of the piston rod 13.
  • annular first annular passage 75 communicating all the first passage holes 41. It has become. All of the first passage holes 41 and the first annular passage 75 constitute a first passage 76 (passage) penetrating the piston 12 in the axial direction. Working fluid flows in the first passage 76 by sliding of the piston 12 against the cylinder 11.
  • a first opening 77 (opening) on the first chamber 19 side of the first passage 76 is the space between the end surface 64 of the first outer sheet 61 and the end surface 73 of the first inner sheet 71.
  • the substantially circular first outer sheet 61 is formed on the piston body 31 so as to protrude from the opening surface 52 so as to surround the first opening 77 of the first passage 76.
  • the first opening 77 of the first passage 76 is disposed between the first outer sheet 61 and the first inner sheet 71.
  • the piston main body 31 is formed with an opening surface 82 on the second chamber 20 side, in which the opening 81 on the second chamber 20 side of all the second passage holes 42 is opened.
  • An opening surface 84 is formed on the outer side of the opening surface 82 in the radial direction of the piston main body 31 so as to open the openings 83 on the second chamber 20 side of all the first passage holes 41.
  • the piston body 31 has a substantially circular second outer sheet 91 on the second chamber 20 side.
  • the second outer sheet 91 is formed to surround all the openings 81 at the radially outer side of the piston main body 31.
  • the second outer sheet 91 is formed to project in the axial direction of the piston main body 31 more than the opening faces 82 and 84.
  • the second outer sheet 91 has a tapered surface 92, a tapered surface 93, and a tip surface 94.
  • the tapered surface 92 radially inwards has a larger diameter toward the tip end side.
  • the tapered surface 93 has a diameter decreasing outward in the radial direction toward the tip end side.
  • the end surface 94 is a flat surface which spreads in a direction orthogonal to the axial direction on the protruding end side.
  • the protruding front end side of the second outer sheet 91 is a second width gradual reduction portion 95 having these tapered surfaces 92 and 93 and a front end surface 94 and whose radial width gradually decreases toward the protruding front end side.
  • An opening surface 82 is disposed radially inward of the tapered surface 92.
  • An opening surface 84 is disposed radially outward of the tapered surface 93.
  • the piston body 31 is provided with a substantially circular second inner sheet 101 on the second chamber 20 side.
  • the second inner sheet 101 is disposed more radially inward of the piston main body 31 than the second outer sheet 91.
  • the second inner sheet 101 is formed to project in the axial direction of the piston main body 31 more than the opening surface 82.
  • the opening surface 82 and the entire opening 81 are disposed between the second outer sheet 91 and the second inner sheet 101.
  • the second inner sheet 101 has a tapered surface 102 and a tip surface 103.
  • the tapered surface 102 has a diameter decreasing outward in the radial direction toward the tip end side.
  • the end surface 103 is a flat surface which spreads in a direction orthogonal to the axial direction on the protruding end side.
  • the inner peripheral side of the second inner sheet 101 is an insertion hole 35.
  • the outer diameter of the tip end surface 103 is substantially equal to the outer diameter of the end surface 27 of the piston rod 13.
  • annular second annular passage 105 communicating all the second passage holes 42. It has become. All the second passage holes 42 and the second annular passage 105 constitute a second passage 106 axially penetrating the piston 12. Working fluid flows in the second passage 106 by the sliding of the piston 12 against the cylinder 11.
  • a second opening 107 on the second chamber 20 side of the second passage 106 is between the tip end surface 94 of the second outer sheet 91 and the tip end surface 103 of the second inner sheet 101.
  • the substantially circular second outer sheet 91 is formed on the piston main body 31 so as to protrude from the opening surface 82 so as to surround the second opening 107 of the second passage 106.
  • the second opening 107 of the second passage 106 is disposed between the second outer sheet 91 and the second inner sheet 101.
  • the piston body 31 is shaped so that there is no distinction between the front and back. Therefore, even if the piston main body 31 is mounted on the piston rod 13 upside down, the above configuration is obtained.
  • the end face 27 of the main shaft 25 of the piston rod 13 is made of metal and formed in an annular shape, one restriction member 111, two small diameter disks 112, one large diameter disk 113, and one Contact disc 114, piston 12, one contact disc 115 (disk), two large-diameter discs 116, one intermediate-diameter disc 117, and one intermediate-diameter disc 118;
  • the two small diameter disks 119 and the one restriction member 120 are stacked in this order in a state in which the mounting shaft portion 26 is fitted to the inside of each. In this state, the nut 14 is screwed in the female screw 30 with the male screw 28 protruding from the regulating member 120 of the mounting shaft 26.
  • the large-diameter disc 113, the abutting disc 114, the abutting disc 115, the two large-diameter discs 116, and the intermediate-diameter discs 117 and 118 can not move in the axial direction with respect to the piston rod 13 Clamped on.
  • the outer diameter of the restricting member 111 is larger than the outer diameter of the end surface 27 and the outer diameter of the distal end surface 103.
  • the small diameter disc 112 is flat and has an outer diameter equal to the outer diameter of the end face 27.
  • the large-diameter disk 113 is flat and has an outer diameter larger than the outer diameter of the small-diameter disk 112 and substantially the same as the outer diameter of the front end surface 94 of the second outer sheet 91.
  • the abutting disc 114 is flat and has an outer diameter equal to that of the large-diameter disc 113.
  • the abutting disc 114 abuts on and is seated on the leading end surface 94 of the second outer sheet 91 and the leading end surface 103 of the second inner sheet 101.
  • the contact disc 114 and the large diameter disc 113 constitute a disc valve 127.
  • the disc valve 127 is axially clamped at its inner peripheral side by the small diameter disc 112 and the second inner sheet 101, and a portion radially outward of the small diameter disc 112 is deformed away from the piston main body 31 to form a second outer sheet 91 Away from the tip surface 94 of the
  • the abutment disk 115 has a base portion 131, an inner protruding plate portion 132, a tip end plate portion 133, an outer protruding plate portion 134, and an outer end plate portion 135. .
  • the substrate portion 131 spreads in the radial direction.
  • the inner protruding plate portion 132 protrudes from the outer peripheral edge portion of the substrate portion 131 to one side in the plate thickness direction.
  • the tip end plate portion 133 extends radially outward from the end edge portion of the inner protruding plate portion 132 opposite to the substrate portion 131.
  • the outer protruding plate portion 134 protrudes from the outer peripheral edge of the tip end plate portion 133 in the same direction as the protruding direction of the inner protruding plate portion 132 with respect to the tip end plate portion 133.
  • the outer end plate portion 135 extends radially outward from an end edge portion of the outer protruding plate portion 134 opposite to the tip end plate portion 133.
  • the substrate portion 131 is an annular flat plate spreading radially outward from the inner end position of the contact disk 115.
  • the outer end plate portion 135 is an annular flat plate positioned at an outer end position of the abutting disk 115 in the radial direction.
  • the substrate portion 131 and the outer end plate portion 135 are disposed on the same plane.
  • the inner projecting plate portion 132 has a tapered cylindrical shape having a larger diameter as it is separated from the substrate portion 131 in the axial direction.
  • the outer projecting plate portion 134 has a tapered cylindrical shape with a smaller diameter as it is separated from the outer end plate portion 135 in the axial direction.
  • the inner protruding plate portion 132 protrudes from the substrate portion 131 and the outer end plate portion 135 while expanding in diameter.
  • the outer protruding plate portion 134 protrudes from the substrate portion 131 and the outer end plate portion 135 while reducing the diameter.
  • the tip end plate portion 133 is an annular flat plate, and is disposed in parallel with the substrate portion 131 and the outer end plate portion 135.
  • the inner protruding plate portion 132, the tip end plate portion 133, and the outer protruding plate portion 134 constitute a protruding portion 136 axially protruding from the base plate portion 131 and the outer end plate portion 135 on both sides in the radial direction.
  • the convex portion 136 (inner projecting portion) has an annular shape.
  • a plurality of, specifically two, notches 138 are formed in the contact disk 115 at equal intervals in the circumferential direction.
  • the notched portion 138 penetrates in the thickness direction, and comes out radially outward from the portion on the inner projecting plate portion 132 side of the tip end plate portion 133 through the outer projecting plate portion 134 and the outer end plate portion 135.
  • the abutting disc 115 is formed in the above shape by press forming from a flat metal plate having a constant plate thickness. Therefore, as shown in FIG. 3, the inner protruding plate portion 132, the tip end plate portion 133, and the outer protruding plate portion 134 which form the convex portion 136 of the abutting disk 115 are almost the same as the substrate portion 131 and the outer end plate portion 135. It has become thick.
  • the outer diameter of the portion of the contact disc 115 excluding the cutout portion 138 of the outer end plate portion 135 is equal to the outer diameter of the tip end surface 64 of the first outer sheet 61. Further, the outer diameter of the end portion on the outer end plate portion 135 side of the outer peripheral surface 140 of the outer protruding plate portion 134 is slightly smaller than the inner diameter of the leading end surface 64 of the first outer sheet 61 There is.
  • the outer circumferential surface 140 of the outer protruding plate portion 134 has a taper equivalent to the tapered surface 62 of the first width gradually decreasing portion 65 of the first outer sheet 61. In addition, it is also possible to make one taper of the outer peripheral surface 140 and the taper surface 62 larger than the other taper, and conversely, make the other taper larger than one taper.
  • the abutting disc 115 is in a state where the convex portion 136 protrudes from the base portion 131 and the outer end plate portion 135 on both sides in the radial direction to the piston 12 side, and the outer end plate portion 135 faces the piston 12 side. Then, the front end surface 64 of the first outer sheet 61 is opposed to and in contact with the seat, and the base plate portion 131 is in contact with the front end surface 73 of the first inner sheet 71 shown in FIG.
  • the tip end surface 142 of the tip end plate portion 133 of the abutting disc 115 is located closer to the opening surface 52 than the tip end surface 64 of the first outer sheet 61.
  • the notch 138 of the abutment disk 115 allows the first passage 76 to enter the first chamber 19 even when the abutment disk 115 is seated on the front end surface 64 of the first outer sheet 61 at the opposing surface 141 of the outer end plate portion 135. Form a fixed orifice to communicate.
  • a fixed orifice may be formed in the first outer sheet 61 by providing a cutaway portion penetrating the same in the radial direction from the distal end surface 64.
  • the abutting disc 115 forms an inner projecting portion by the tip end surface 142 as a thick portion projecting to the surface on the piston 12 side as the valve main body.
  • valve lift amount 0
  • radially inward of the annular first width gradually decreasing portion 65 of the first outer sheet 61 At that time, the tapered surface 62 of the first width gradually decreasing portion 65 inclined by the same taper and the outer peripheral surface 140 of the outer protruding plate portion 134 overlap in the axial position and face each other with a slight gap in the radial direction. .
  • the annular convex portion 136 is an annular first width gradually decreasing portion of the piston main body 31 65 and the position in the axial direction are superimposed and opposed in the radial direction.
  • the first width gradually decreasing portion 65 of the first outer sheet 61 gradually decreases in radial width toward the contact disk 115.
  • the large diameter disc 116 is flat, and the outer diameter is equal to the outer diameter of the portion of the outer end plate portion 135 of the contact disc 115 excluding the notch 138.
  • the medium diameter disc 117 is flat and has an outer diameter smaller than the outer diameter of the large diameter disc 116.
  • the intermediate diameter disc 118 is flat and has an outer diameter smaller than the outer diameter of the intermediate diameter disc 117.
  • the small diameter disc 119 is flat, and the outer diameter is smaller than the outer diameter of the middle diameter disc 118, and is substantially equal to the outer diameter of the tip end surface 73 of the first inner sheet 71.
  • the small diameter disc 119 is a component common to the small diameter disc 112.
  • the restriction member 120 has an outer diameter larger than the outer diameter of the small diameter disc 119.
  • the restricting member 120 is a component common to the restricting member 111.
  • the abutting disc 115, the large diameter disc 116, the intermediate diameter disc 117 and the intermediate diameter disc 118 constitute a disc valve 144.
  • the disc valve 144 is axially clamped at its inner peripheral side by the small diameter disc 119 and the first inner sheet 71, and a portion outside the small diameter disc 119 is deformed away from the piston main body 31 and the tip of the first outer sheet 61 Away from face 64.
  • a first damping force generating mechanism provided in the first passage 76 for controlling the flow of the working fluid to generate a damping force, the disc valve 144 and the first outer sheet 61 and the first inner sheet 71 for seating the disc valve 144 145 (damping force generation mechanism) is comprised.
  • the first damping force generation mechanism 145 controls the damping force by controlling the flow passage area (hereinafter simply referred to as the flow passage area) which is the smallest in the first passage 76.
  • the flow passage area is the area of the gap between the first outer sheet 61 and the disc valve 144.
  • the opening 53 of the second passage 106 is disposed radially outward of the disk valve 144, and the second passage 106 is not blocked by the disk valve 144.
  • a second damping force generating mechanism provided in the second passage 106 for controlling the flow of the working fluid and generating a damping force, the disc valve 127 and the second outer sheet 91 and the second inner sheet 101 for seating the disc valve 127 It comprises 148.
  • the second damping force generation mechanism 148 controls the flow path area of the second passage 106 to control the damping force.
  • the flow passage area is the area of the gap between the second outer sheet 91 and the disc valve 127.
  • the opening 83 of the first passage 76 is disposed radially outward of the disk valve 127, and the first passage 76 is not blocked by the disk valve 127.
  • the piston main body 31, the restricting member 111 and the restricting member 120 have higher rigidity than the large diameter disc 113, the abutting disc 114, the abutting disc 115, the large diameter disc 116, the intermediate diameter disc 117 and the intermediate diameter disc 118, respectively. ing.
  • the restricting member 111 suppresses further deformation of the disc valve 127 in a state where the deformed disc valve 127 is in contact.
  • the restricting member 120 suppresses further deformation of the disc valve 144 when the deformed disc valve 144 is in contact.
  • the pressure of the second chamber 20 is higher than the pressure of the first chamber 19 by the piston 12 moving integrally with the piston rod 13. Ral.
  • the working fluid of the second chamber 20 is introduced into the plurality of first passage holes 41 of the first passage 76 from the openings 83 of the respective constant openings.
  • the working fluid introduced from the opening 83 acts on the disc valve 144 which comes out of the opening 51 and joins the first annular passage 75 to close the first opening 77.
  • the working fluid in the first passage 76 does not cause the disc valve 144 of the first damping force generation mechanism 145 to leave the first outer seat 61. That is, as shown in FIG. 3, the contact state between the facing surface 141 of the outer end plate portion 135 of the contact disk 115 and the leading end surface 64 of the first outer sheet 61 is maintained. Then, the working fluid of the second chamber 20 flows from the first passage 76 to the first chamber 19 through the notch 138 as a fixed orifice of the contact disk 115 of the disk valve 144. As a result, since the flow passage area of the first passage 76 becomes constant, a damping force of the orifice characteristic (the damping force is approximately proportional to the square of the piston speed) is generated.
  • the working fluid in the first passage 76 causes the disc valve 144 including the abutment disc 115 of the first damping force generation mechanism 145 to be released from the first outer sheet 61.
  • the damping force of the valve characteristic (the damping force is substantially proportional to the piston speed) corresponding to the flow passage area between the disc valve 144 and the first outer seat 61 which becomes the flow passage area of the first passage 76 is generated.
  • the disc valve 144 is separated from the first outer sheet 61 by the pressure difference generated between the upstream side and the downstream side.
  • the valve opening height which is the distance between the facing surface 141 of the outer end plate portion 135 of the abutting disk 115 and the leading end surface 64 of the first outer sheet 61, is proportional to the pressure difference.
  • the contact disk 115 faces the first width gradually decreasing portion 65 of the first outer sheet 61 with a slight gap in the radial direction in a small state including the valve closing state where the valve opening height is 0.
  • a projecting portion 136 including an outwardly projecting plate portion 134 is provided.
  • FIGS. 5A to 5C are diagrams for explaining the state of the first damping force generation mechanism of the shock absorber according to the first embodiment.
  • FIG. 5A shows a closed state in which the first width gradually decreasing portion 65 is in contact with the abutting disk 115 and the valve opening height is zero.
  • 5B is to contact the disc 115 is a diagram illustrating a state in which the first width gradually decreasing portion 65 is spaced by a predetermined distance h b.
  • FIG. 6 is a characteristic diagram showing the relationship of the flow passage area to the valve opening height.
  • the horizontal axis h represents the valve opening height.
  • the vertical axis S represents the flow passage area.
  • the point a shown in FIG. 6 corresponds to the state of FIG. 5A.
  • the point b shown in FIG. 6 corresponds to the state of FIG. 5B.
  • the point c shown in FIG. 6 corresponds to the state of FIG. 5C. That is, FIG.
  • FIG. 5A shows a closed state in which the valve opening height is zero.
  • the flow passage area Sab increases in proportion to the increase of the valve opening height h.
  • a range in which the contact disk 115 and the first width gradually decreasing portion 65 having the inner tapered surface 62 (the inner diameter is expanded) is opposed in the radial direction by overlapping the position in the valve opening height direction It contains.
  • the valve opening height h is increased.
  • the flow passage area S bc increases proportionally at a higher rate than in the sections a to b.
  • the flow passage area formed in the gap formed by the first outer sheet 61, which is the top of the outer sheet, and the contact disc 115 as a disc valve is smaller than S ab , and then the sections a to b are also in that state Will continue.
  • the flow passage area S bc between the sections b to c is larger than the gap formed by the first outer sheet 61 which is the top of the outer sheet and the contact disc 115 as a disc valve. That is, the flow path area formed in the gap between the contact disc 115 and the top of the first outer sheet 61 is changed from a smaller state to a larger state.
  • the radius of the inner peripheral edge of the front end surface 64 of the first outer sheet 61 is r 1
  • the radius of the outer peripheral edge of the front end surface 142 of the contact disk 115 is r 2.
  • the height from the facing surface 141 to the tip end surface 142 is H.
  • the angle of inclination with respect to the central axis of the tapered surface 62 of the first outer sheet 61 and theta 1 the angle of inclination with respect to the central axis of the outer peripheral surface 140 of the abutment disc 115 and theta 2, section a
  • the height from the facing surface 141 of the contact disk 115 to the tip end surface 64 of the first outer sheet 61 at b to b is h b .
  • the height from the facing surface 141 of the abutting disk 115 to the leading end surface 64 of the first outer sheet 61 in the sections b to c is h c .
  • the flow passage area S bc in the sections b to c can be obtained by the following equation (2).
  • h b H + h b cos 2 ⁇ 2
  • S ab S bc .
  • the contact disc 115 and the first width gradually decreasing portion 65 are positions in the valve opening height direction And the radially opposed range is included.
  • the rate of increase in damping force with respect to the increase in piston speed is lower in the speed range in which the piston speed in the sections b to c is higher than in the speed range in which the piston speed in the sections a to b is slow.
  • the flow passage area S bc is a flow passage area between the contact disk 115 and the first width gradually decreasing portion 65 when the first width gradually decreasing portion 65 is not opposed in the radial direction.
  • the flow passage area S ab which is the flow passage area between the abutting disk 115 and the first width gradually decreasing portion 65 when facing in the direction, is larger than the flow passage area S ab .
  • the first width compared with the flow passage area of the first passage 76 determined by the distance relationship between the contact disk 115 and the first width gradually decreasing portion 65 when the first width gradually decreasing portion 65 faces the radial direction, the first width The flow passage area of the first passage 76 determined by the distance relationship between the contact disk 115 and the first width gradually decreasing portion 65 when the gradually decreasing portion 65 does not face in the radial direction is larger.
  • the ratio of the increase in the flow passage area to the valve opening height increases Also, the rate of increase in damping force relative to the increase in piston speed is kept lower than before.
  • the pressure of the first chamber 19 is made higher than the pressure of the second chamber 20 by the piston 12 moving integrally with the piston rod 13.
  • the working fluid in the first chamber 19 is introduced into the plurality of second passage holes 42 of the second passage 106 from the openings 53 of the respective constant openings.
  • the working fluid introduced from the opening 53 comes out of the opening 81 and joins into the second annular passage 105 and acts on the disk valve 127 of the second damping force generating mechanism 148 which closes the second opening 107.
  • the working fluid in the second passage 106 opens the disc valve 127 away from the second outer sheet 91.
  • the working fluid flows from the first chamber 19 to the second chamber 20 via the second passage 106 in a flow passage area corresponding to the valve opening amount of the disk valve 127 and the second outer sheet 91. Therefore, damping force of the valve characteristic is generated.
  • the piston speed is increased by separating the disc from the outer sheet when the piston speed is in the middle speed range and separating the disc from the intermediate sheet when the piston speed is in the high speed range.
  • a shock absorber is described which lowers the rate of increase in damping force at high speeds compared to medium speeds. This shock absorber allows the working fluid to flow from the space between the intermediate sheet and the disc, which has a smaller diameter than the outer sheet, in the high speed range of the piston speed, so the flow passage area can not be made sufficiently large It is possible that the rate of increase in power can not be reduced sufficiently.
  • the first damping force generation mechanism 145 of the shock absorber 10 has the first width of the first outer sheet 61 in a state where the contact disc 115 is in contact with the first outer sheet 61. It faces the taper part 65 in the radial direction in the convex part 136.
  • the first width gradually decreasing portion 65 in the radial direction By increasing the flow passage area between the abutment disk 115 and the first width gradually decreasing portion 65 when not facing each other, the ratio of the increase in damping force to the increase in piston speed is greater than the medium speed range of piston speed.
  • the working fluid can flow from between the first outer sheet 61 and the abutting disc 115, so the flow passage area can be made sufficiently wide.
  • the increase of the flow passage area at the initial stage of valve opening of the first damping force generation mechanism 145 can be moderated, and a rapid pressure change can be suppressed, and the generation of sound resulting therefrom can be suppressed.
  • the first width gradually decreasing portion 65 is radially opposed to the contact disc 115 in a state of being in contact with the first outer sheet 61, and separated from the first outer sheet 61 by a predetermined amount. Since it is sufficient to provide the convex portion 136 so as not to face the radial direction 65, the ratio of the increase of the damping force to the increase of the piston speed is made lower in the high speed range than the medium speed range of the piston speed be able to.
  • the convex portion 136 is formed on the contact disc 115 formed by press molding at the time of press molding. Therefore, an increase in the number of parts can be suppressed, and an increase in cost can be suppressed.
  • the convex portion 136 is formed on the abutting disc 115, but as shown in the first modification shown in FIG. 7, the abutting disc 115 is a flat plate main body disc 151 and a diametrically opposed flat plate It may be configured with 152.
  • the main body disc 151 has an opposing surface 141 that is seated on the front end surface 64 of the first outer sheet 61.
  • the diametrically opposed disc 152 is disposed radially inward of the first outer sheet 61 in a state where the main disc 151 is seated on the distal end surface 64 of the first outer sheet 61 at the opposed surface 141, and It has an outer peripheral surface 140 and a tip end surface 142 which are opposed in the radial direction by overlapping axial positions.
  • the convex portion 136 of the abutting disc 115 is formed by the inner protruding plate portion 132, the tip end plate portion 133 and the outer protruding plate portion 134 having the same thickness as the substrate portion 131 and the outer end plate portion 135.
  • the thickness between the substrate portion 131 and the outer end plate portion 135 is greater than these.
  • a thick thick portion 155 may be formed, and the thick portion 155 may form a convex portion 136 projecting from the substrate portion 131 and the outer end plate portion 135.
  • the substrate portion 131, the outer end plate portion 135, and the convex portion 136 can be formed by integral molding of resin.
  • the abutting disc 115 is constituted by a disc main body 161 made of a flat metal plate and a separate member 162 made of synthetic resin provided on the outer peripheral side of the disc main body 161. Also good.
  • the separate member 162 has a main portion 163 in which a convex portion 136 having an outer peripheral surface 140 and a tip end surface 142 and an opposing surface 141 are formed and in close contact with the disc main body 161; And a mounting portion 165 in close contact with the opposite side of the main portion 163 of the disc main body 161.
  • the covering portion 164 connects the outer peripheral edge portion of the main portion 163 and the outer peripheral edge portion of the mounting portion 165.
  • the disc main body 161 is placed in a mold in which a cavity having the shape of the separate member 162 is formed, and synthetic resin material is poured into the cavity to form the separate member 162 on the outer peripheral portion of the disc main body 161 Become.
  • the abutting disk 115 is a flat plate and a convex portion 136 as a separate member having an outer peripheral surface 140 and a tip end surface 142 on the disk main body 168 forming the opposing surface 141. May be attached.
  • the disc main body 168 can be made of metal and the convex portion 136 can be made of synthetic resin. Also in this case, the disc main body 168 is placed in a mold in which a cavity in the shape of the convex portion 136 is formed, and a synthetic resin material is poured into the cavity to form the convex portion 136 in the disc main body 168.
  • the outer peripheral surface 140 of the convex portion 136 of the abutting disk 115 is made to be the same taper as the tapered surface 62 of the first outer sheet 61, and these are opposed in the radial direction with a slight gap.
  • the taper surface 62 of the first outer sheet 61 is made larger than the taper of the outer peripheral surface 140 of the convex portion 136 so that the tapered surface 62 is on the tip end surface 142 side of the outer peripheral surface 140. You may make it contact
  • the taper of the tapered surface 62 of the first outer sheet 61 is made smaller than the taper of the outer peripheral surface 140 of the convex portion 136, and the tip of the tapered surface 62 is The end on the surface 64 side may be in contact with the outer peripheral surface 140.
  • the contact disk 115 is provided with the notch 138 or the first outer sheet 61 is provided with the notch which is recessed from the distal end surface 64 and penetrates radially. Configure a fixed orifice.
  • the abutting disk 115A is partially different from the abutting disk 115 of the first embodiment.
  • the contact disk 115A has a substrate portion 131A and a projecting plate portion 171 (a projecting portion, an outer projecting portion).
  • the substrate portion 131A extends radially outward from the radial inner end position of the abutting disk 115A.
  • the protruding plate portion 171 protrudes to one side in the plate thickness direction from the outer peripheral edge portion of the substrate portion 131A.
  • the projecting plate portion 171 is located at the radial outer end position of the abutting disc 115A. That is, the protruding plate portion 171 forms an outer protruding portion by curving toward the valve main body side.
  • the projecting plate portion may be formed on the inner side than the first outer sheet 61 to form the inner projecting portion.
  • the substrate portion 131A is a disk-shaped flat plate.
  • the projecting plate portion 171 has a tapered cylindrical shape having a larger diameter as it is separated from the substrate portion 131A in the axial direction.
  • the protruding plate portion 171 protrudes from the substrate portion 131A while expanding in diameter.
  • the abutting disk 115A is formed with a notch 138A which penetrates in the thickness direction and which passes through the projecting plate 171 from the side of the projecting plate 171 of the substrate 131A to be pulled outward in the radial direction.
  • the abutting disc 115A is formed in the above shape by press forming from a flat metal plate having a constant plate thickness.
  • the substrate portion 131A and the protruding plate portion 171 of the abutting disk 115A have the same thickness.
  • the outer diameter of the substrate portion 131A of the abutting disk 115A is substantially equal to the outer diameter of the leading end surface 64 of the first outer sheet 61.
  • the inner circumferential surface 172 of the protruding plate portion 171 has a taper equivalent to the radially outer tapered surface 63 of the first width gradually decreasing portion 65 of the first outer sheet 61.
  • the abutting disc 115A is in a state in which the projecting plate portion 171 projects from the base portion 131A on the radially inner side to the piston 12 side, and the base portion 131A is an opposing surface 141A on the piston 12 side.
  • the end surface 64 and the end surface 73 (see FIG. 2) of the first inner sheet 71 are seated.
  • the tip end portion of the protruding plate portion 171 of the abutting disc 115A is located closer to the opening surface 52 than the tip end surface 64 of the first outer sheet 61.
  • the notch portion 138A of the abutment disk 115A constitutes a fixed orifice that allows the first passage 76 to communicate with the first chamber 19 even when the abutment disk 115A is seated on the leading end surface 64 of the first outer sheet 61.
  • the first outer sheet 61 may be provided with a notch which is recessed from the distal end surface 64 and penetrates in the radial direction to constitute a fixed orifice.
  • the abutting disc 115A is seated on the leading end surface 64 of the first outer seat 61 of the piston main body 31 in the base plate portion 131A, and the annular projecting plate portion 171 is formed of the annular first portion of the first outer seat 61.
  • the width decreasing portion 65 is inserted radially inward. At that time, the tapered surface 63 of the first width gradually decreasing portion 65 inclined by the same taper and the inner peripheral surface 172 of the projecting plate portion 171 overlap in the axial position and face each other with a slight gap in the radial direction .
  • the annular projecting plate portion 171 is the annular first width gradually decreasing portion 65 of the piston main body 31. And the position in the axial direction are superimposed and opposed in the radial direction.
  • the flow passage area of the first passage 76 determined by the distance relationship between the contact disk 115A and the first width gradually decreasing portion 65 when the protruding plate portion 171 faces the first width gradually decreasing portion 65 in the radial direction is larger.
  • the abutting disc 115A, the large diameter disc 116, the intermediate diameter disc 117 and the intermediate diameter disc 118 constitute a disc valve 144A.
  • the disc valve 144A and the first outer sheet 61 and the first inner sheet 71 (see FIG. 2) on which the disc valve 144A is seated constitute a first damping force generating mechanism 145A (damping force generating mechanism).
  • the working fluid in the second chamber 20 acts from the first passage 76 to the disc valve 144A.
  • the working fluid in the first passage 76 does not cause the disc valve 144A of the first damping force generation mechanism 145A to move away from the first outer sheet 61. It flows into the first chamber 19 through the notch 138A as a fixed orifice of the abutment disk 115A, and a damping force of the orifice characteristic is generated.
  • the working fluid in the first passage 76 causes the disc valve 144A of the first damping force generation mechanism 145A to separate from the first outer seat 61.
  • the abutting disk 115A of the disk valve 144A is provided with a projecting plate portion 171 which faces the first width gradually decreasing portion 65 of the first outer sheet 61 with a slight gap in the radial direction when the valve opening height is small. . For this reason, the rate of increase of the flow passage area to the increase of the piston speed changes between the low speed region and the high speed region, and the rate of increase of the damping force to the increase of the piston speed changes between the low speed region and the high speed region.
  • the projecting plate portion 171 is provided on the first width gradually decreasing portion 65 of the first outer sheet 61 in a state where the abutting disk 115A abuts on the first outer sheet 61. In the radial direction.
  • the first width gradually decreases in comparison with the flow passage area between the contact disk 115A and the first width gradually decreasing portion 65 when the projecting plate portion 171 faces the first width gradually decreasing portion 65 in the radial direction.
  • the first width gradually reducing portion 65 is radially opposed, and when it is separated from the first outer sheet 61 by a predetermined amount Since the projecting plate portion 171 may be provided so as not to face each other, the structure is simple. In addition, since the protruding plate portion 171 is formed at the time of press molding on the contact disc 115A formed by press molding, an increase in the number of parts can be suppressed, and an increase in cost can be suppressed.
  • the shock absorber is a cylinder in which the working fluid is enclosed, and a piston slidably inserted in the cylinder to define the inside of the cylinder into two chambers.
  • a piston rod connected to the piston and extending to the outside of the cylinder, a passage through which the working fluid flows by sliding of the piston, and a passage provided in the passage to control the flow of the working fluid to provide a damping force And a damping force generating mechanism to be generated.
  • the damping force generation mechanism includes: a valve body having the passage extending therethrough; a substantially circular outer sheet formed to protrude from the valve body so as to surround an opening of the passage; and the outer sheet on the valve body And a disk-shaped disc valve which is seated on the outer sheet and the inner sheet and which is seated on the outer peripheral sheet by bending on the outer peripheral side.
  • the outer sheet has at least one of an inner-peripheral-side tapered portion whose inner-peripheral side expands as it faces the seat surface on which the disc valve is seated, or an outer-peripheral-side tapered portion whose outer peripheral side shrinks.
  • the disc valve has at least one of an inner protrusion radially opposed to the inner tapered portion or an outer protrusion radially opposed to the outer tapered portion in a valve closed state seated on the outer seat.
  • the portion between the inner projecting portion and the radially inner tapered portion is radially opposed, or A flow area formed by a portion formed between the outer protruding portion and the outer circumferential tapered portion in a radial direction is formed in a gap between the disc valve and the top of the outer sheet; It becomes a state larger than the road area.
  • the disk valve is curved toward the valve body to form the inner protrusion or the outer protrusion.
  • the disk valve is formed with the inner protrusion or the outer protrusion by a thick portion protruding from the surface on the valve body side.
  • the thick part is configured by attaching another member to the disk closest to the main body.
  • the disc valve is formed of a plurality of discs, and the disc on the main body side is a valve having a diameter smaller than that of the inner tapered portion. As the inner protrusion.
  • shock absorber 11 cylinder 12 piston 13 piston rod 19 first chamber 20 second chamber 31 piston main body (valve main body) 61 1st outside sheet (outside sheet) 65 First width gradually decreasing portion (width gradually decreasing portion) 71 1st inner sheet (inner sheet) 76 1st passage (passage) 77 1st opening (opening) 115, 115A Abutment Disc (Disc) 136 Convex part 145, 145A first damping force generation mechanism (damping force generation mechanism) 171 Protruding plate part (convex part)

Landscapes

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

Abstract

L'invention concerne un amortisseur dont le mécanisme de production de force d'amortissement comprend : un corps de soupape (31) à travers lequel s'étend un passage (76), le passage (76) permettant à un fluide de fonctionnement de s'écouler à travers celui-ci ; un siège externe sensiblement circulaire (61), formé de manière à faire saillie à partir du corps de soupape (31) et à entourer l'ouverture (77) du passage (76) ; un siège interne, formé de manière à faire saillie à l'intérieur du siège externe (61) ; et un disque (115) reposant sur le siège externe (61) et sur le siège interne. Le siège externe (61) possède une section (65) de largeur progressivement décroissante, dont la largeur radiale diminue progressivement vers le disque (115). Lorsqu'il repose sur le siège externe (61), le disque (115) fait face radialement à la section (65) de largeur progressivement décroissante. La surface de voie d'écoulement entre le disque (115) et la section (65) de largeur progressivement décroissante est supérieure lorsque le disque (115) ne fait pas face radialement à la section (65) de largeur progressivement décroissante par rapport à lorsque le disque (115) le fait.
PCT/JP2018/029233 2017-08-09 2018-08-03 Amortisseur Ceased WO2019031405A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE112018004049.6T DE112018004049T5 (de) 2017-08-09 2018-08-03 Dämpfer
JP2019535174A JP6921201B2 (ja) 2017-08-09 2018-08-03 緩衝器
CN201880051425.1A CN110998130B (zh) 2017-08-09 2018-08-03 缓冲器

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Application Number Priority Date Filing Date Title
JP2017154817 2017-08-09
JP2017-154817 2017-08-09

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Publication Number Publication Date
WO2019031405A1 true WO2019031405A1 (fr) 2019-02-14

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JP (1) JP6921201B2 (fr)
CN (1) CN110998130B (fr)
DE (1) DE112018004049T5 (fr)
WO (1) WO2019031405A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62156637U (fr) * 1986-03-27 1987-10-05
JP2013029173A (ja) * 2011-07-29 2013-02-07 Hitachi Automotive Systems Ltd 流体圧緩衝器
JP2015086966A (ja) * 2013-10-31 2015-05-07 日立オートモティブシステムズ株式会社 緩衝器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3471438B2 (ja) * 1993-12-06 2003-12-02 株式会社ショーワ 緩衝器のバルブ構造
JP5115814B2 (ja) * 2008-05-30 2013-01-09 日立オートモティブシステムズ株式会社 緩衝器
US8297418B2 (en) * 2008-06-05 2012-10-30 Tenneco Automotive Operating Company Inc. Nested check high speed valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62156637U (fr) * 1986-03-27 1987-10-05
JP2013029173A (ja) * 2011-07-29 2013-02-07 Hitachi Automotive Systems Ltd 流体圧緩衝器
JP2015086966A (ja) * 2013-10-31 2015-05-07 日立オートモティブシステムズ株式会社 緩衝器

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CN110998130B (zh) 2022-04-26
CN110998130A (zh) 2020-04-10
JPWO2019031405A1 (ja) 2020-04-23
DE112018004049T5 (de) 2020-04-16
JP6921201B2 (ja) 2021-08-18

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