WO2022209576A1 - 緩衝器及びバルブ装置 - Google Patents
緩衝器及びバルブ装置 Download PDFInfo
- Publication number
- WO2022209576A1 WO2022209576A1 PCT/JP2022/009338 JP2022009338W WO2022209576A1 WO 2022209576 A1 WO2022209576 A1 WO 2022209576A1 JP 2022009338 W JP2022009338 W JP 2022009338W WO 2022209576 A1 WO2022209576 A1 WO 2022209576A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- piston
- passage
- chamber
- seat portion
- Prior art date
Links
- 239000006096 absorbing agent Substances 0.000 title claims description 26
- 230000035939 shock Effects 0.000 title claims description 26
- 230000002093 peripheral effect Effects 0.000 claims abstract description 42
- 239000012530 fluid Substances 0.000 claims description 26
- 238000012856 packing Methods 0.000 claims description 8
- 238000005192 partition Methods 0.000 claims description 2
- 238000013016 damping Methods 0.000 abstract description 20
- 230000006835 compression Effects 0.000 description 50
- 238000007906 compression Methods 0.000 description 50
- 238000004891 communication Methods 0.000 description 8
- 238000011144 upstream manufacturing Methods 0.000 description 5
- 230000008602 contraction Effects 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 238000007789 sealing Methods 0.000 description 3
- 239000013013 elastic material Substances 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
- 230000001154 acute effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
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
- F16F9/34—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
-
- 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
- F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
- F16F9/062—Bi-tubular units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- 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
- F16F9/3485—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 supporting elements intended to guide or limit the movement of the annular discs
Definitions
- the present invention relates to a shock absorber that controls the flow of working fluid with respect to the stroke of a piston rod to vary the damping force, and a valve device used in the shock absorber.
- Patent Document 1 the surface between the inner edge a of the boss portion 12 and the outer edge b of the seat portion 13 is formed on the same curved surface that gradually rises from the inside to the outside, so that the leaf valve 4 is A shock absorber (hereinafter referred to as a "conventional shock absorber”) is disclosed in which localized deformation from the boss portion 12 to the seat portion 13 is eliminated. According to the conventional shock absorber, it is possible to prevent variations in the initial load applied to the outer peripheral end of the leaf valve 4, and to suppress variations in damping force.
- a shock absorber hereinafter referred to as a "conventional shock absorber”
- the leaf valve 4 is seated on the entire surface of the seat portion 13 in the width direction (boss portion radial direction).
- Contact width varies. If the contact width varies, the pressure-receiving area of the leaf valve 4 may vary, and the valve opening point and damping force may vary.
- An object of the present invention is to provide a shock absorber and a valve device that suppress variations in damping force.
- a shock absorber of the present invention comprises a cylinder in which a working fluid is sealed, a piston that divides the inside of the cylinder into a first chamber and a second chamber, and a valve member that opens and closes a passage provided in the piston.
- the piston is formed with an annular first seat portion protruding from the piston on the outer peripheral side of the opening of the passage, and the first seat portion includes an annular first protrusion and the first protrusion. and an annular second protrusion extending in a direction away from the piston, and the valve member, in a state of being assembled to the piston, abuts only on the second protrusion.
- An annular first seat portion protruding from the piston is formed on the outer peripheral side of the, and the first seat portion includes an annular first convex portion and a first convex portion extending in a direction away from the piston than the first convex portion.
- An annular second protrusion is formed, and the valve member is in contact only with the second protrusion when assembled to the piston.
- FIG. 3 It is a sectional view by the axis plane of the shock absorber concerning a 1st embodiment. It is a figure which expands and shows the damping force adjustment mechanism in FIG. 3 is an enlarged view of a contact portion between the extension side main valve (valve member) and the seat portion (first seat portion) in FIG. 2; FIG. It is an explanatory view of a 2nd embodiment.
- FIG. 1 shows a so-called piston built-in damping force adjustable shock absorber 1 (damping mechanism) in which a variable damping force mechanism 17 is built in a cylinder 2 .
- the shock absorber 1 has a double-cylinder structure in which an outer cylinder 10 is provided outside the cylinder 2 .
- the shock absorber 1 is slidably fitted in a cylinder 2, and has a piston 3 that divides the inside of the cylinder 2 into two chambers, a cylinder upper chamber 2A (first chamber) and a cylinder lower chamber 2B (second chamber).
- a piston rod 141 having one end connected to the piston 3 and the other end (the upper side in FIG. 1) extending to the outside of the cylinder 2; and a variable damping force mechanism 17 that communicates in two directions and controls the flow of hydraulic oil (working fluid) accompanying movement of the piston 3 to vary damping force characteristics.
- a reservoir 18 is formed between the cylinder 2 and the outer cylinder 10 .
- the piston 3 has an extension side passage 19 whose upper end side opens to the cylinder upper chamber 2A, and a compression side passage 20 whose lower end side opens to the cylinder lower chamber 2B.
- a base valve 45 that separates the cylinder lower chamber 2B and the reservoir 18 is provided at the lower end of the cylinder 2 .
- the base valve 45 is provided with passages 46 and 47 that communicate between the cylinder lower chamber 2B and the reservoir 18 .
- the passage 46 is provided with a check valve 48 that allows oil (working fluid) to flow from the reservoir 4 side to the cylinder lower chamber 2B side.
- the passage 47 is provided with a disk valve 49 that opens when the pressure of the hydraulic fluid on the side of the cylinder lower chamber 2B reaches the set pressure, and releases the pressure (fluid) on the side of the cylinder lower chamber 2B to the reservoir 18 side. be done.
- the working fluid the cylinder 2 is filled with oil, and the reservoir 18 is filled with oil and gas.
- a bottom cap 50 is joined to the lower end of the outer cylinder 10 .
- the variable damping force mechanism 17 consists of a valve mechanism section 28 and a solenoid 90 .
- the valve mechanism section 28 includes the piston bolt 5, the shaft portion 6 of which is inserted into the shaft hole 4 of the piston 3, and the extension-side valve mechanism 21, which controls the flow of the working fluid in the extension-side passage 19. and a compression-side valve mechanism 51 that controls the flow of the working fluid in the compression-side passage 20 .
- the extension side valve mechanism 21 has a bottomed cylindrical extension side pilot case 22 attached to the shaft portion 6 of the piston bolt 5 .
- the extension-side pilot case 22 has a cylindrical portion 26 opening on the side of the piston 3 and a bottom portion 27 .
- An extension-side main valve 23 (valve member) is arranged on the piston 3 side of the extension-side pilot case 22 .
- An extension-side back pressure chamber 25 is formed between the extension-side main valve 23 and the extension-side pilot case 22 on the opposite side of the extension-side main valve 23 (“lower side” in FIG. 2). be.
- the extension-side valve mechanism 21 has an annular seat portion 201 (first seat portion) formed on the outer peripheral side of the lower end surface of the piston 3 and against which the extension-side main valve 23 abuts so as to be separable and seatable.
- the seat portion 201 is formed on the outer peripheral side of the opening of the extension-side passage 19 .
- the extension-side back pressure chamber 25 is formed between the extension-side pilot case 22 and the back surface of the extension-side main valve 23 .
- the pressure in the extension side back pressure chamber 25 acts on the extension side main valve 23 in the valve closing direction.
- An annular packing 31 made of an elastic material is baked on the extension side main valve 23 .
- the extension-side main valve 23 is a packing valve in which the packing 31 contacts the inner peripheral surface of the cylindrical portion 26 of the extension-side pilot case 22 over the entire circumference.
- the extension-side back pressure chamber 25 communicates with the cylinder lower chamber 2B via a passage 32 formed in the bottom portion 27 of the extension-side pilot case 22 and the sub-valve 30 .
- the sub-valve 30 opens when the pressure in the extension-side back pressure chamber 25 reaches a predetermined pressure, and applies resistance to the flow of working fluid from the extension-side back pressure chamber 25 to the cylinder lower chamber 2B.
- the extension-side back pressure chamber 25 communicates through a passage 32 with a first pressure receiving chamber 172 formed between the extension-side pilot case 22 and the sub-valve 30 .
- the first pressure receiving chamber 172 is sector-shaped by a plurality of annular first seat portions 173 provided on the lower end surface of the extension-side pilot case 22 (the surface opposite to the extension-side main valve 23 side). Inside the plurality of first seat portions 173, passages 32 are opened respectively.
- the extension side pilot case 22 is provided with a back pressure introduction passage 171 through which the working fluid flows from the cylinder lower chamber 2B to the extension side back pressure chamber 25 when the piston 3 moves in the contraction direction.
- An annular seat portion 35 is provided on the upper end surface of the extension-side pilot case 22 (the surface on the extension-side main valve 23 side).
- the seat portion 35 defines an annular pressure receiving chamber 174 provided on the outer periphery of the inner peripheral portion of the bottom portion 27 .
- a second pressure receiving chamber 177 isolated from the first pressure receiving chamber 172 is provided on the lower end face of the extension side pilot case 22 .
- a back pressure introduction passage 171 opens into the second pressure receiving chamber 177 .
- the second pressure receiving chamber 177 is defined by the second seat portion 178 .
- the second seat portion 178 extends in an arc shape between a pair of adjacent first pressure receiving chambers 172 .
- the second seat portion 178 is provided with a first orifice 175 that communicates the second pressure receiving chamber 177 and the cylinder lower chamber 2B.
- the extension side valve mechanism 21 is formed with an extension side communication path (communication path) that communicates the cylinder lower chamber 2B and the extension side back pressure chamber 25 with each other.
- the extension-side communication passage moves the working fluid in the cylinder lower chamber 2B through the first orifice 175, the second pressure receiving chamber 177, the back pressure introduction passage 171, the pressure receiving chamber 174, and the check valve 33 by the movement of the piston 3 in the contraction direction. is introduced into the extension-side back pressure chamber 25 via .
- the compression side valve mechanism 51 has a bottomed cylindrical compression side pilot case 52 attached to the shaft portion 6 of the piston bolt 5 .
- the compression-side pilot case 52 is composed of a cylindrical portion 56 opening on the side of the piston 3 and a bottom portion 57 .
- a compression side main valve 53 (valve member) is arranged on the piston 3 side of the compression side pilot case 52 .
- a compression side back pressure chamber 55 is formed between the compression side main valve 53 and the compression side pilot case 52 on the opposite side of the compression side main valve 53 (“upper side” in FIG. 2). .
- the compression side valve mechanism 51 has an annular seat portion 211 (first seat portion) formed on the outer peripheral side of the upper end surface of the piston 3 and against which the compression side main valve 53 comes into contact so that it can be seated and separated.
- the seat portion 211 is formed on the outer peripheral side of the opening of the contraction-side passage 20 .
- the compression side back pressure chamber 55 is formed between the compression side pilot case 52 and the back surface of the compression side main valve 53 .
- the pressure in the compression side back pressure chamber 55 acts on the compression side main valve 53 in the valve closing direction.
- An annular packing 61 made of an elastic material is baked onto the compression side main valve 53 .
- the compression side main valve 53 is a packing valve in which the packing 61 is in contact with the inner peripheral surface of the cylindrical portion 56 of the compression side pilot case 52 over the entire circumference.
- the compression side back pressure chamber 55 communicates with the cylinder upper chamber 2A via a passage 62 formed in the bottom portion 57 of the compression side pilot case 52 and a sub-valve 60 .
- the sub-valve 60 opens when the pressure in the compression side back pressure chamber 55 reaches a predetermined pressure, and applies resistance to the flow of working fluid from the compression side back pressure chamber 55 to the cylinder upper chamber 2A.
- the compression side back pressure chamber 55 communicates through a passage 62 with a first pressure receiving chamber 182 formed between the compression side pilot case 52 and the sub valve 60 .
- the first pressure receiving chamber 182 is sector-shaped by a plurality of first seat portions 183 provided on the upper end surface of the compression side pilot case 52 (the surface opposite to the compression side main valve 53 side).
- a passage 62 is opened inside each of the plurality of first seat portions 183 .
- the compression side pilot case 52 is provided with a back pressure introduction passage 181 through which the working fluid flows from the cylinder upper chamber 2A to the compression side back pressure chamber 55 when the piston 3 moves in the extension direction.
- An annular seat portion 65 is provided on the lower end surface of the compression-side pilot case 52 (the surface on the side of the compression-side main valve 53 ).
- the seat portion 65 defines an annular pressure receiving chamber 184 provided on the outer periphery of the inner peripheral portion of the bottom portion 57 .
- a second pressure receiving chamber 187 isolated from the first pressure receiving chamber 182 is provided on the upper end face of the contraction side pilot case 52 .
- a back pressure introduction passage 181 opens into the second pressure receiving chamber 187 .
- the second pressure receiving chamber 187 is defined by the second seat portion 188 .
- the second seat portion 188 extends in an arc shape between a pair of adjacent first pressure receiving chambers 182 .
- the second seat portion 188 is provided with a first orifice 185 that communicates the second pressure receiving chamber 187 with the cylinder upper chamber 2A.
- the compression side valve mechanism 51 is formed with a compression side communication passage (communication passage) that communicates the cylinder upper chamber 2A and the compression side back pressure chamber 55 .
- the compression-side communication passage moves the working fluid in the cylinder upper chamber 2A through the first orifice 185, the second pressure receiving chamber 187, the back pressure introduction passage 181, the pressure receiving chamber 184, and the check valve 63 by the movement of the piston 3 in the extension direction. is introduced into the contraction-side back pressure chamber 55 via .
- valve parts constituting the extension side valve mechanism 21 and the compression side valve mechanism 51 are configured by tightening a nut 78 attached to a threaded portion (reference numerals omitted) of the shaft portion 6 of the piston bolt 5 so that the head of the piston bolt 5 is An axial force is generated by pressurization between the portion 7 and the washer 79 .
- a common passage 11 is formed in the piston bolt 5 as shown in FIG.
- the common passage 11 has an axial passage 12 formed inside (axial hole) of the sleeve 15 .
- the upper end of the sleeve 15 is fitted into a hole 16 opening into the head 6 of the piston bolt 5 .
- the common passage 11 has an axial passage 13 formed in the lower portion of the hole 16 (the portion below the lower end of the sleeve 15).
- the common passage 11 has an axial passage 14 which is a small diameter hole whose upper end opens into a hole 16 .
- the inner diameter of the common passage 11 is the largest in the axial passage 13 and decreases in the order of the axial passage 12 and the axial passage 14 .
- the axial passage 12 opens at the end face 9 of the head 7 of the piston bolt 5 .
- the extension-side back pressure chamber 25 passes through an orifice (reference numerals omitted) provided in the seat portion 35 of the extension-side pilot case 22 and the pressure receiving chamber 174 to reach the radial passage 34 formed in the shaft portion 6 of the piston bolt 5. is communicated with.
- the radial passage 34 communicates with the axial passage 14 .
- the axial passage 14 communicates with a radial passage 39 formed in the shaft portion 6 of the piston bolt 5 .
- the radial passage 39 includes an annular passage 41 formed at the lower end of the shaft hole 4 of the piston 3, a plurality of notches 42 formed in the inner circumference of the piston 3, and a disk valve 40 provided in the piston 3. through the extension side passage 19 .
- the disk valve 40 abuts on an annular seat portion 43 of the piston 3 provided on the inner peripheral side of the opening of the seat portion 201 and the extension side passage 19 so as to be separable and seatable.
- the disk valve 40 is a check valve that allows the working fluid to flow from the radial passage 39 to the extension passage 19 .
- the compression-side back pressure chamber 55 includes an orifice (reference numerals omitted) provided in the seat portion 65 of the compression-side pilot case 52 , a pressure-receiving chamber 184 , and an annular passage 68 formed in the inner peripheral portion of the bottom portion 57 of the compression-side pilot case 52 .
- the radial passage 64 formed in the shaft portion 6 of the piston bolt 5 .
- the radial passage 64 communicates with the axial passage 12 through a hole 66 formed in the side wall of the sleeve 15 .
- the radial passage 64 includes a width across flat portion 77 , an annular passage 71 formed in the upper end portion of the shaft hole 4 of the piston 3 , a plurality of notches 72 formed in the inner peripheral portion of the piston 3 , and the piston 3 . It communicates with the compression side passage 20 via the disk valve 70 provided.
- the disk valve 70 abuts on an annular seat portion 73 of the piston 3 provided on the inner peripheral side of the opening of the seat portion 211 and the compression side passage 20 so as to be separable and seatable.
- the disk valve 70 is a check valve that allows working fluid to flow from the radial passage 64 to the compression side passage 20 .
- the flow of working fluid in the common passage 11 is controlled by a pilot valve 81 (pilot control valve).
- the pilot valve 81 has a valve spool 82 slidably provided in the common passage 11 and a seat portion 83 formed around the opening periphery of the axial passage 14 at the bottom of the hole 16 .
- the valve spool 82 is formed of a solid shaft, and has a sliding portion 84 inserted into the sleeve 15 and a valve body 85 that abuts on the seat portion 83 in a separable manner.
- a head portion 87 of the valve spool 82 is formed at the upper end of the sliding portion 84 .
- a first chamber 130 is formed around the head 7 of the valve spool 82 .
- An outer flange-shaped spring receiver 88 is formed at the lower end of the head 87 .
- the spring receiver 88 is connected to the inner peripheral portion of a spring disc 113 that biases the valve body 85 in the valve opening direction.
- a bottomed cylindrical cap 121 with an open upper end is attached to the lower part of the outer peripheral surface of the head 7 of the piston bolt 5 .
- An annular sealing member 128 seals between the cap 121 and the head 7 of the piston bolt 5 .
- an annular second chamber 131 is formed between the cap 121 and the head portion 7 of the piston bolt 5 .
- the cap 121 is provided with an insertion hole 123 through which the shaft portion 6 of the piston bolt 5 is inserted.
- a plurality of notches 124 (indicated as “two” in FIG. 2) are provided on the outer periphery of the insertion hole 123 . The notch 124 communicates with the width across flats portion 77 formed in the shaft portion 6 .
- a spool back pressure relief valve 107 Between the cap 121 and the head 7 of the piston bolt 5, a spool back pressure relief valve 107, a spacer 108, and a retainer 132 are provided in this order from the head 7 side. Spool back pressure relief valve 107 , spacer 108 and retainer 132 are provided within second chamber 131 .
- the spool back pressure relief valve 107 is a check valve that allows the working fluid to flow from the first chamber 130 to the second chamber 131 via the passage 29 formed in the head 7 .
- An outer peripheral edge of the spool back pressure relief valve 107 abuts on an annular seat portion 109 formed on the head portion 7 of the piston bolt 5 so as to be separable and seatable.
- a plurality of cutouts 133 are provided in the inner peripheral edge of the retainer 132 to allow the second chamber 131 to communicate with the width across flat portion 77 and the cutouts 124 of the cap 121 .
- a retainer 59 is interposed between the cap 121 and the sub-valve 60 to determine the maximum opening amount of the sub-valve 60 .
- a fail-safe valve 111 is configured in the first chamber 130 .
- the fail-safe valve 111 has a disk 112 (valve seat) against which the spring receiver 88 (valve body) of the head 87 of the valve spool 82 is removably seated.
- the outer peripheral edges of the disc 112 and spring disc 113 are held between the head 7 of the piston bolt 5 and the core 99 of the solenoid 90 .
- a valve body 85 of the valve spool 82 is formed in a circular cross-section by an axis-perpendicular plane having a notch 86 (only one is shown in FIG. 2) having a width across flats.
- the valve spool 82 moves in the valve opening direction (upward direction in FIG. 2) of the pilot valve 81, and the valve body 85 is fitted into the axial passage 12. be.
- a pair of orifices 114 (only one shown in FIG. 2) communicating between the axial passages 12 and 13 is formed between the valve body 85 and the axial passage 12 . Only one of the pair of surfaces forming the width across flats (notch 86) may be formed. In this case, there will be only one orifice 114 .
- valve body 85 of the valve spool 82 is seated on the seat portion 83, and the pilot valve 81 is closed.
- the valve spool 82 receives the pressure on the side of the axial passage 14 from the circular pressure-receiving surface having the same area as the opening area of the axial passage 14.
- the portion 84 receives the pressure on the side of the axial passage 12 by an annular pressure-receiving surface having the same area as the cross-sectional area of the sliding portion 84 minus the cross-sectional area of the neck portion (reference numeral omitted) of the valve body 85 .
- the opening pressure of the pilot valve 81 can be adjusted by controlling the energization of the coil 95 .
- the biasing force of the spring disk 113 and the thrust generated by the plunger 96 are balanced, and the valve body 85 is separated from the seat portion 83 by a certain distance.
- the solenoid 90 has a solenoid mechanism portion 91, a yoke 94, and a coil 95 (armature coil).
- the solenoid mechanism 91 has an operating rod 92, a plunger 96 (armature) fixed to the outer periphery of the operating rod 92, and cores 98 and 99 divided into upper and lower parts.
- the cores 98 and 99 are held coaxially by holders 104 and 105 which are divided into upper and lower parts with a constant vertical interval therebetween.
- the operating rod 92 is guided vertically (axially) by a bush 100 attached to the core lid 106 and a bush 110 attached to the core 99 .
- An intra-rod passage 97 is formed inside the operating rod 92 .
- a sealing member 116 seals between the lower end of the bottomed cylindrical yoke 94 and the core 99 .
- an annular passage 117 is formed between the piston bolt 5 , the yoke 94 and the core 99 .
- the annular passage 117 communicates with the cylinder upper chamber 2 ⁇ /b>A via a passage 118 provided in the cylindrical portion 8 of the piston bolt 5 .
- a spool back pressure chamber 101 is formed inside the core 99 of the solenoid 90 .
- the spool back pressure chamber 101 communicates with the rod back pressure chamber 103 via a notch (reference numeral omitted) of the operating rod 92 and an intra-rod passage 97 .
- the lower end of the piston rod 141 is connected to the upper end of the yoke 94 . That is, the lower end (one end) of the piston rod 141 is connected to the piston 3 via the yoke 94 and the piston bolt 5 .
- a fastening force (axial force) between the yoke 94 and the piston rod 141 is generated by tightening the nut 137 and pressing the ring member 145 mounted in the annular groove 146 on the outer periphery of the piston rod 141 in the axial direction.
- a bump stopper 140 attached to a piston rod 141 is brought into contact with the upper end surface of the nut 137 .
- the piston rod 141 is inserted through a rod guide 135 and an oil seal 134 which are attached to the upper openings of the cylinder 2 and the outer cylinder 10 .
- a cover 136 that covers the upper end side of the outer cylinder 10 is attached to the outer circumference of the piston rod 141 .
- the space between the piston rod 141 and the yoke 94 is sealed by a sealing member 139 fitted in an annular groove 138 formed in the outer peripheral surface of the lower end of the piston rod 141.
- a sealing member 139 fitted in an annular groove 138 formed in the outer peripheral surface of the lower end of the piston rod 141.
- the piston rod 141 has a hollow shaft formed with a hollow portion 142 (shaft hole) extending along the shaft.
- a cable 151 is inserted through the hollow portion 142 of the piston rod 141 .
- Wires 153 and 154 of the cable 151 protruding from the lower end surface 143 (one end) of the piston rod 141 (piston 3 side) are connected to terminals 161 and 162 of the solenoid 90 .
- the terminal 161 is connected to the positive terminal of the coil 95, and the terminal 162 is connected to the negative terminal of the coil 95.
- the electric wires 153, 154 protruding from the upper end surface 144 (one end) of the piston rod 141 are connected to a connector 157 on the vehicle side (power supply device side).
- the working fluid in the cylinder upper chamber 2A flows through the upstream back pressure introduction passage, that is, the extension side passage 19, the orifice (reference numerals omitted) formed in the disk valve 40, the notch 42 formed in the piston 3,
- the extension side passage 19 formed in the shaft hole 4 of the piston 3
- the radial passage 34, the axial passage 14, the radial passage 39, the annular passage 38 formed in the extension side pilot case 22, and the check valve 33 the extension It is introduced into the side back pressure chamber 25 .
- the working fluid in the cylinder upper chamber 2A flows through the compression side communication passage, that is, the first orifice 185, the second pressure receiving chamber 187, the back pressure introduction passage 181, and the check valve 63. After that, it is introduced into the compression side back pressure chamber 55 . This prevents the compression side main valve 53 from opening due to the pressure in the cylinder upper chamber 2A during the extension stroke.
- the working fluid introduced into the compression-side back pressure chamber 55 during the extension stroke is formed in the orifice (reference numerals omitted) formed in the seat portion 65, the pressure-receiving chamber 184, and the inner peripheral portion of the bottom portion 57 of the compression-side pilot case 52.
- the annular passage 68 Through the annular passage 68, the width across flat portion 77 formed in the shaft portion 6 of the piston bolt 5, the notch 72 formed in the inner peripheral portion of the piston 3, the disk valve 70, and the compression side passage 20, the cylinder lower chamber 2B Since it flows into the (downstream side chamber), damping force of the orifice characteristic by the orifice 67 and the valve characteristic by the disk 70 is obtained before the opening of the extension side main valve 23, that is, in the low piston speed region.
- the working fluid in the cylinder lower chamber 2B flows through the upstream back pressure introduction passage, that is, the compression side passage 20, the orifice (reference numerals omitted) formed in the disc valve 70, the piston 3, and the compression side passage 20.
- the upstream back pressure introduction passage that is, the compression side passage 20, the orifice (reference numerals omitted) formed in the disc valve 70, the piston 3, and the compression side passage 20.
- an annular passage 71 formed in the shaft hole 4 of the piston 3 a width across flat portion 77 formed in the shaft portion 6 of the piston bolt 5, and an annular passage formed in the compression side pilot case 52 68 and a check valve 63 to the compression side back pressure chamber 55 .
- the working fluid in the cylinder lower chamber 2B (upstream side chamber) flows through the extension side communication passage, that is, the first orifice 175, the second pressure receiving chamber 177, the back pressure introduction passage 171 (downstream side back pressure introduction passage). passage) and the check valve 33 into the extension side back pressure chamber 25 .
- the extension side communication passage that is, the first orifice 175, the second pressure receiving chamber 177, the back pressure introduction passage 171 (downstream side back pressure introduction passage). passage
- the check valve 33 into the extension side back pressure chamber 25 .
- the working fluid introduced into the extension-side back pressure chamber 25 during the compression stroke is formed in the orifice (reference numerals omitted) formed in the seat portion 35, the pressure receiving chamber 174, and the inner peripheral portion of the bottom portion 27 of the extension-side pilot case 22.
- FIG. 3 is an enlarged view of the contact portion between the extension side main valve 23 (valve member) and the seat portion 201 (first seat portion) in FIG.
- the contact portion between the compression side main valve 53 (valve member) and the seat portion 211 (first seat portion) has the same structure as the contact portion between the extension side main valve 23 and the seat portion 201 . Therefore, for the purpose of simplifying the description of the specification, only the contact portion between the extension side main valve 23 (hereinafter referred to as "main valve 23") and the seat portion 201 is illustrated, and the compression side main valve 53 and the seat portion 201 are illustrated. The illustration of the contact portion with the seat portion 211 is omitted.
- the seat portion 201 includes an annular first surface 202 provided on the inner peripheral side (“left side” in FIG. 3) of the seat portion 201 and an annular first surface 202 provided on the outer peripheral side (“right side” in FIG. 3) of the seat portion 201. It has an annular second surface 203 and an annular third surface 204 provided between the first surface 202 and the second surface 203 .
- the first surface 202 , the second surface 203 , and the third surface 204 have straight cross sections along the axial plane of the piston 3 .
- the first surface 202 and the second surface 203 are formed so as to taper (the width in the radial direction becomes narrower) in the direction away from the piston 3 (“downward direction” in FIG. 3).
- the angle formed by the first surface 202 and the second surface 203 is an acute angle.
- An annular ridge 205 (second protrusion) is formed between the first surface 202 and the third surface 204 .
- An annular ridge 206 (first projection) is formed between the second surface 203 and the third surface 204 .
- the angle ⁇ 2 formed by the second surface 203 and the third surface 204, that is, the angle ⁇ 2 of the ridge 206 is an obtuse angle. is also large ( ⁇ 2> ⁇ 1).
- the ridge 205 extends (protrudes) in a direction away from the piston 3 (“downward” in FIG. 3) more than the ridge 206 does.
- the ridge portion 205 (second convex portion) on the inner peripheral side of the seat portion 201 (first seat portion) abutted only to
- the tip of the first seat portion is brought into contact with the seat surface obtained by cutting the tip of the first seat portion along a plane parallel to the plane perpendicular to the axis of the piston, the seat of the first seat portion The valve member was able to come into contact with the entire surface in the width direction (the entire surface in the radial direction). Therefore, in the conventional shock absorber, the diameter of the seat on which the valve member is seated (the contact diameter of the first seat portion) varies due to dimensional errors in the step height of the seat surface of the first seat portion.
- the pressure-receiving area of the member may vary and the valve opening point and damping force may vary.
- annular edge portion 205 (second convex portion) is provided between the first surface 202 on the inner peripheral side of the seat portion 201 (first seat portion) and the adjacent third surface 204 . ) is formed, and an annular ridge portion 206 (first convex portion) is formed between the second surface 203 on the outer peripheral side of the seat portion 201 and the adjacent third surface 204 to form the main valve 23 (valve member ) is configured to contact only the ridge portion 205 on the inner peripheral side of the seat portion 201 in the state assembled to the piston 3 .
- the contact area between the main valve 23 (valve member) and the seat portion 201 (first seat portion) can be minimized (the contact width in the radial direction can be reduced). Therefore, the contact diameter between the main valve 23 and the seat portion 201 (ridge portion 205) can be kept constant by controlling the radial dimension of the ridge portion 205 (second convex portion) on the inner peripheral side of the seat portion 201. is possible, and variations in valve opening point and damping force can be suppressed.
- the main valve 23 is configured so as to abut only the ridge 205 on the inner peripheral side of the seat portion 201 when assembled to the piston 3 .
- the main valve 23 (valve member) is mounted on the piston 3, and the ridge portion 206 (second convex portion) on the outer peripheral side of the seat portion 201 (first seat portion). ) so that it abuts only on the
- the angle ⁇ 1 formed by the first surface 202 and the third surface 204 is an obtuse angle.
- the angle ⁇ 2 formed by 203 and the third surface 204 is larger than the angle ⁇ 2 of the edge portion 206 (second convex portion) ( ⁇ 1> ⁇ 2).
- the ridge 206 extends (protrudes) in a direction away from the piston 3 (“downward” in FIG. 4) more than the ridge 205 does.
- the main valve 23 (valve member) is brought into contact only with the ridge portion 206 on the outer peripheral side of the seat portion 201 (first seat portion) while assembled to the piston 3 (see FIG. 2).
- the seat diameter (contact diameter of the first seat portion 201) on which the main valve 23 (valve member) is seated can be increased compared to the first embodiment in which the inner peripheral side of the seat portion 201 is high. can.
- the pressure-receiving area of the main valve 23 is increased, and the opening point of the damping force characteristic on the soft side is lowered, thereby improving the ride comfort of the vehicle.
- the embodiment is not limited to the form described above, and can be configured as follows, for example.
- the annular packings 31, 61 baked on the main valves 23, 53 (valve members) are brought into contact with the inner peripheral surfaces of the pilot cases 22, 52 to form the back pressure chambers 25, 55.
- the shock absorber 1 having the variable damping force mechanism 17 formed has been described, for example, the spool member is provided with a spool member that is axially movable in sliding contact with the inner peripheral surface of the pilot case.
- the configurations of the first and second embodiments can also be applied to a shock absorber having a variable damping force mechanism that forms a back pressure chamber by contacting the seal member of the disc valve.
- the present invention is not limited to the above-described embodiments, and includes various modifications.
- the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the configurations described.
- part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.
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Abstract
Description
本発明のバルブ装置は、シリンダの内部を第1室及び第2室に区画するピストンと、前記ピストンに設けられた通路を開閉するバルブ部材と、を備え、前記ピストンには、前記通路の開口の外周側に前記ピストンから突出する環状の第1シート部が形成され、前記第1シート部には、環状の第1凸部と、該第1凸部よりも前記ピストンから離間する方向へ延びる環状の第2凸部と、が形成され、前記バルブ部材は、前記ピストンに組付けられた状態で、前記第2凸部にのみ当接されることを特徴とする。
便宜上、図1における上下方向をそのまま「上下方向」と称する。図1に、減衰力可変機構17がシリンダ2に内蔵された、所謂、ピストン内蔵型の減衰力調整式緩衝器1(減衰機構)を示す。
これにより、第1実施形態では、メインバルブ23(バルブ部材)とシート部201(第1シート部)との接触面積を極力小さく(径方向接触幅を狭く)することができる。よって、シート部201の内周側の稜部205(第2凸部)の径方向寸法を管理することで、メインバルブ23とシート部201(稜部205)との接触径を一定に保つことが可能であり、バルブ開弁点及び減衰力のばらつきを抑制することができる。
次に、図4を参照して第2実施形態を説明する。
なお、第1実施形態との共通部分については、同一の称呼及び符号を用い、重複する説明を省略する。
また、第2実施形態では、シート部201の内周側が高い第1実施形態に対し、メインバルブ23(バルブ部材)が着座するシート径(第1シート部201の接触径)を大きくすることができる。これにより、メインバルブ23の受圧面積が大きくなり、ソフト側の減衰力特性における開弁点が下がることで、車両の乗り心地を向上させることができる。
第1及び第2実施形態では、メインバルブ23,53(バルブ部材)に焼き付けられた環状のパッキン31,61をパイロットケース22,52の内周面に当接させて背圧室25,55を形成する減衰力可変機構17を備えた緩衝器1への適用を説明したが、例えば、パイロットケースの内周面に摺接して軸方向へ移動可能なスプール部材を備え、スプール部材に形成した環状のシール部材をディスクバルブに当接させて背圧室を形成する減衰力可変機構を備えた緩衝器にも第1及び第2実施形態の構成を適用することができる。
Claims (5)
- 緩衝器であって、該緩衝器は、
作動流体が封入されるシリンダと、
前記シリンダの内部を第1室及び第2室に区画するピストンと、
前記ピストンに設けられた通路を開閉するバルブ部材と、を備え、
前記ピストンには、前記通路の開口の外周側に前記ピストンから突出する環状の第1シート部が形成され、
前記第1シート部には、環状の第1凸部と、該第1凸部よりも前記ピストンから離間する方向へ延びる環状の第2凸部と、が形成され、
前記バルブ部材は、前記ピストンに組付けられた状態で、前記第2凸部にのみ当接されることを特徴とする緩衝器。 - 請求項1に記載の緩衝器において、
前記バルブ部材の反ピストン側には、該バルブ部材に対して背圧を付与するパイロット室が設けられることを特徴とする緩衝器。 - 請求項1又は2に記載の緩衝器において、
前記バルブ部材は、パッキンが焼き付けられたディスクバルブであることを特徴とする緩衝器。 - 請求項1又は2に記載の緩衝器において、
前記バルブ部材は、ディスクバルブと、軸方向へ移動可能なスプール部材と、前記ディスクバルブと前記スプール部材との間に設けられるシール部材と、から構成されることを特徴とする緩衝器。 - バルブ装置であって、該バルブ装置は、
シリンダの内部を第1室及び第2室に区画するピストンと、
前記ピストンに設けられた通路を開閉するバルブ部材と、を備え、
前記ピストンには、前記通路の開口の外周側に前記ピストンから突出する環状の第1シート部が形成され、
前記第1シート部には、環状の第1凸部と、該第1凸部よりも前記ピストンから離間する方向へ延びる環状の第2凸部と、が形成され、
前記バルブ部材は、前記ピストンに組付けられた状態で、前記第2凸部にのみ当接されることを特徴とするバルブ装置。
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DE112022001839.9T DE112022001839T5 (de) | 2021-03-29 | 2022-03-04 | Stoßdämpfer und Ventilvorrichtung |
KR1020237028830A KR20230130145A (ko) | 2021-03-29 | 2022-03-04 | 완충기 및 밸브 장치 |
JP2023510720A JP7378010B2 (ja) | 2021-03-29 | 2022-03-04 | 緩衝器及びバルブ装置 |
US18/274,637 US20240093752A1 (en) | 2021-03-29 | 2022-03-04 | Shock absorber and valve apparatus |
CN202280020544.7A CN116997731A (zh) | 2021-03-29 | 2022-03-04 | 缓冲器以及阀装置 |
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JP2021055341 | 2021-03-29 | ||
JP2021-055341 | 2021-03-29 |
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US (1) | US20240093752A1 (ja) |
JP (1) | JP7378010B2 (ja) |
KR (1) | KR20230130145A (ja) |
CN (1) | CN116997731A (ja) |
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Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH08135712A (ja) * | 1994-11-10 | 1996-05-31 | Toyota Motor Corp | ショックアブソーバ |
JP2013170663A (ja) * | 2012-02-22 | 2013-09-02 | Kyb Co Ltd | 緩衝器 |
JP2019163769A (ja) * | 2016-07-26 | 2019-09-26 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP2021046944A (ja) * | 2017-07-27 | 2021-03-25 | 日立Astemo株式会社 | 緩衝器 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2010055341A (ja) | 2008-08-28 | 2010-03-11 | Asahi Kasei Homes Co | 建築部材の管理方法 |
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- 2022-03-04 JP JP2023510720A patent/JP7378010B2/ja active Active
- 2022-03-04 DE DE112022001839.9T patent/DE112022001839T5/de active Pending
- 2022-03-04 KR KR1020237028830A patent/KR20230130145A/ko unknown
- 2022-03-04 WO PCT/JP2022/009338 patent/WO2022209576A1/ja active Application Filing
- 2022-03-04 CN CN202280020544.7A patent/CN116997731A/zh active Pending
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Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH08135712A (ja) * | 1994-11-10 | 1996-05-31 | Toyota Motor Corp | ショックアブソーバ |
JP2013170663A (ja) * | 2012-02-22 | 2013-09-02 | Kyb Co Ltd | 緩衝器 |
JP2019163769A (ja) * | 2016-07-26 | 2019-09-26 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
JP2021046944A (ja) * | 2017-07-27 | 2021-03-25 | 日立Astemo株式会社 | 緩衝器 |
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DE112022001839T5 (de) | 2024-02-15 |
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