WO2023013511A1 - シリンダ装置及び制御弁装置 - Google Patents

シリンダ装置及び制御弁装置 Download PDF

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Publication number
WO2023013511A1
WO2023013511A1 PCT/JP2022/029054 JP2022029054W WO2023013511A1 WO 2023013511 A1 WO2023013511 A1 WO 2023013511A1 JP 2022029054 W JP2022029054 W JP 2022029054W WO 2023013511 A1 WO2023013511 A1 WO 2023013511A1
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WO
WIPO (PCT)
Prior art keywords
chamber
piston
passage
valve
control valve
Prior art date
Application number
PCT/JP2022/029054
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English (en)
French (fr)
Japanese (ja)
Inventor
祐太 山口
Original Assignee
日立Astemo株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立Astemo株式会社 filed Critical 日立Astemo株式会社
Priority to CN202280047511.1A priority Critical patent/CN117642564A/zh
Priority to JP2023540296A priority patent/JP7531063B2/ja
Priority to KR1020247001890A priority patent/KR20240022632A/ko
Priority to DE112022003790.3T priority patent/DE112022003790T5/de
Publication of WO2023013511A1 publication Critical patent/WO2023013511A1/ja

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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
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity

Definitions

  • the present invention relates to a cylinder device capable of adjusting damping force characteristics and a control valve device assembled to the cylinder device.
  • Patent Document 1 discloses a shock absorber equipped with a frequency sensitive damping valve device.
  • the shock absorber described in Patent Document 1 (hereinafter referred to as "conventional cylinder device") adjusts the load deflection characteristics by varying the hardness of the rubber of the seal ring 15, so the load deflection characteristics can be adjusted freely. low.
  • One of the objects of the present invention is to provide a frequency sensitive cylinder device with improved flexibility in adjusting load deflection characteristics and a control valve device assembled to the cylinder device.
  • a cylinder device includes a cylinder in which a working fluid is enclosed, a piston slidably provided in the cylinder and partitioning the inside of the cylinder, one end side connected to the piston, and the other a piston rod whose end extends outside the cylinder; a first passage through which a working fluid flows out due to movement of the piston; a second passage provided in parallel with the first passage; and a second passage provided in the first passage.
  • damping force generating mechanism a case member formed in a cylindrical shape with a bottom and through which a shaft-shaped member penetrates, the shaft-shaped member penetrates, and is provided inside the case member so as to face the bottom of the case member, a movable member movable by a working fluid in the case member; a first chamber and a second chamber formed by dividing the inside of the case member by the movable member; a hole, a bypass passage provided in parallel with the first through-hole, a second damping force generating mechanism provided in the bypass passage and opened when the pressure in the first chamber reaches a predetermined pressure, and an elastic body provided between the case member and the moving member for suppressing movement of the moving member.
  • a control valve device is a control valve device that is attached to a cylinder device and that controls a flow of working fluid generated by movement of a piston of the cylinder device with an actuator, the control valve device comprising a first passage and a second passage provided in parallel with the first passage; a first damping force generating mechanism provided in the first passage; an actuator for adjusting the damping force generated by the first damping force generating mechanism;
  • a case member formed in a cylindrical shape through which a shaft-shaped member penetrates; a movable member, a first chamber and a second chamber formed by partitioning the inside of the case member by the moving member, a first through hole passing through the bottom of the case member, and the first through hole a bypass passage provided in parallel; a second damping force generating mechanism provided in the bypass passage and opened when the pressure in the first chamber reaches a predetermined pressure; and between the case member and the moving member. and an elastic body that is provided in and suppresses movement of the moving member.
  • FIG. 2 is an enlarged view of a rebound damping force generating mechanism in FIG. 1; 2 is an enlarged view of a compression-side damping force generating mechanism, a pilot valve, and a fail-safe valve in FIG. 1; FIG. It is a top view of a contraction side pilot case.
  • FIG. 5 is a diagram showing a cross section taken along line AA in FIG. 4; It is a figure which expands and shows the principal part of the cylinder apparatus which concerns on 2nd Embodiment. It is explanatory drawing of the damping force generation mechanism of the cylinder apparatus which concerns on 3rd Embodiment.
  • FIG. 8 is an enlarged view of a main part in FIG.
  • FIG. 1 shows a so-called piston built-in type damping force adjustment type cylinder device in which a damping force generating mechanism 110 (control valve device) is built in a cylinder 2 .
  • the cylinder device 1 has a double cylinder structure in which an outer cylinder 3 is provided outside the cylinder 2 .
  • the cylinder device 1 is slidably fitted in a cylinder 2, and a piston 5 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 6 having one end connected to the piston 5 and the other end (the upper side in FIG. 1) extending outside the cylinder 2; and a damping force generating mechanism 110 that communicates in two directions and controls the flow of the working fluid that accompanies the movement of the piston 5 to vary the damping force characteristics.
  • a reservoir 4 is formed between the cylinder 2 and the outer cylinder 3 .
  • the piston 5 has an extension side passage 7 (first passage) whose upper end side opens to the cylinder upper chamber 2A, and a contraction side passage 8 (second passage) whose lower end side opens to the cylinder lower chamber 2B.
  • a base valve 21 that separates the cylinder lower chamber 2B and the reservoir 4 is provided at the lower end of the cylinder 2 .
  • the base valve 21 is provided with passages 22 and 23 that communicate the cylinder lower chamber 2B and the reservoir 4 .
  • the passage 22 is provided with a check valve 24 that allows oil (working fluid) to flow from the reservoir 4 side to the cylinder lower chamber 2B side.
  • the passage 23 is provided with a disk valve 25 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 4 side. be done.
  • the working fluid the cylinder 2 is filled with oil, and the reservoir 4 is filled with oil and gas.
  • a bottom cap 50 is joined to the lower end of the outer cylinder 3 .
  • the damping force generating mechanism 110 consists of a valve mechanism section and a solenoid 81 (actuator).
  • the valve mechanism includes a piston bolt 31 having a shaft portion 32 inserted through the shaft hole 9 of the piston 5 , an extension side damping force generating mechanism 111 for controlling the flow of working fluid in the extension side passage 7 , and a compression side passage 8 . and a compression-side damping force generating mechanism 171 that controls the flow of the working fluid.
  • a common passage 51 is formed in the piston bolt 31 .
  • the common passage 51 has an axial passage coaxial with the shaft portion 32 of the piston bolt 31 .
  • the axial passages are composed of an axial passage 52 whose upper end opens into the head portion 33 of the piston bolt 31, an axial passage 54 whose lower end is closed, and an axial passage 53 formed between the axial passages 52 and 54. , have As for the inner diameter of the axial passages, the axial passage 53 has the largest inner diameter, and the axial passages 52 and 54 have smaller inner diameters in this order.
  • the extension-side damping force generating mechanism 111 has an extension-side main valve 112 which abuts on an annular seat portion 114 formed on the lower end surface of the piston 5 so as to be separable and seatable.
  • the seat portion 114 is formed outside (peripheral side) the opening of the extension-side passage 7 .
  • the extension-side damping force generating mechanism 111 has a bottomed cylindrical extension-side pilot case 131 (case member) attached to the shaft portion 32 of the piston bolt 31 .
  • the extension-side pilot case 131 has a bottom portion 132 and a cylindrical portion 133 opening on the piston 5 side.
  • An annular packing 115 made of an elastic material is baked on the extension side main valve 112 .
  • Packing 115 contacts the opening side (“upper side” in FIG. 2 ) of inner peripheral surface 134 of cylindrical portion 133 of extension-side pilot case 131 over the entire circumference.
  • an annular extension-side back pressure chamber 113 is formed between the extension-side main valve 112 and the extension-side pilot case 131 .
  • the pressure in the extension-side back pressure chamber 113 acts on the extension-side main valve 112 in the valve-closing direction.
  • the extension-side damping force generating mechanism 111 extends from the axial passage 54 to a radial passage 56 formed in the shaft portion 32 of the piston bolt 31 and an annular passage formed between the shaft portion 32 of the piston bolt 31 and the piston 5. It has a check valve 117 that allows the working fluid to flow through the passage 116 to the extension side passage 7 .
  • the check valve 117 abuts on an annular seat portion 118 formed on the lower end surface of the piston 5 so as to be separable and seatable.
  • the seat portion 118 is formed inside (on the inner peripheral side) of the opening of the extension-side passage 7 .
  • the check valve 117 is formed with an orifice 119 that communicates the extension side passage 7 and the axial passage 54 .
  • a moving body 151 (moving member) consisting of an annular spool is provided in the extension-side back pressure chamber 113 .
  • the moving body 151 is supported by a check valve 153 and a disk valve 157 (elastic body).
  • the outer peripheral portion 155 (outer peripheral surface 163) of the moving body 151 is slidably fitted to the bottom portion 132 side (“lower side” in FIG. 2) of the cylindrical portion 133 (inner peripheral surface 134) of the extension side pilot case 131. be.
  • a metal seal seals between the moving body 151 (outer peripheral surface 163) and the extension side pilot case 131 (inner peripheral surface 134).
  • the moving body 151, the check valve 153 and the disk valve 157 divide the extension-side back pressure chamber 113 into a first chamber 121 on the side of the piston 5 ("upper side” in FIG. 2) and a first chamber 121 on the side opposite to the piston 5 ("lower side” in FIG. 2). side”) and the second chamber 122.
  • the inner peripheral portion of the check valve 153 is clamped between the piston 5 and an annular boss 160 provided on the outer periphery of the shaft portion 32 of the piston bolt 31 .
  • a spacer 161 Between the piston 5 and the boss 160, a spacer 161, an inner peripheral portion of the extension side main valve, a plurality of spacers 162, and an inner peripheral portion of the check valve 153 are arranged in this order from the piston 5 side.
  • the inner periphery of disc valve 157 which is a disc-shaped member, is clamped between boss 160 and the inner periphery of extension-side pilot case 131 .
  • a constant gap 152 is formed between the boss 160 and an inner peripheral surface 163 (facing surface) of the moving body 151 .
  • the check valve 153 abuts on an annular seat portion 154 formed on the side of the piston 5 of the moving body 151 (the "upper side” in FIG. 2) so that it can be seated and removed.
  • the check valve 153 retains the pressure (pilot pressure) in the first chamber 121 of the extension-side back pressure chamber 113 , and the pressure from the axial passage 54 to the radial passage 57 formed in the shaft portion 32 of the piston bolt 31 . , the width across flat portion 35 (bypass passage) formed in the shaft portion 32 of the piston bolt 31, and the orifice 156 formed in the check valve 153 to the first chamber 121 of the extension side back pressure chamber 113. Allow working fluid flow.
  • the pressure in the first chamber 121 of the extension-side back pressure chamber 113 acts on the portion (surface) of the moving body 151 on the outer peripheral side of the seat portion 154 .
  • the piston 5 side of the outer peripheral portion 155 of the moving body 151 is lower than the inner peripheral portion where the seat portion 154 is formed in order to avoid interference with the packing 115 of the extension side main valve 112 .
  • the disk valve 157 abuts on an annular seat portion 158 formed on the side opposite to the piston 5 (the "lower side” in FIG. 2) near the outer peripheral portion 155 of the moving body 151 so that it can be seated and removed.
  • the disc valve 157 is configured by stacking a plurality of discs with different outer diameters ("four" in this embodiment, one or more discs with the same outer diameter may be stacked).
  • the pressure in the second chamber 122 of the extension-side back pressure chamber 113 acts on the portion (surface) of the moving body 151 on the outer peripheral side of the seat portion 158 .
  • a concave portion 165 is formed inside (inner peripheral side) of the seat portion 158 of the moving body 151 .
  • a constant gap 166 is formed between the recess 165 and the disc valve 157 .
  • the second chamber 122 of the extension-side back pressure chamber 113 is provided below the cylinder by a plurality of passages 137 (first through holes) formed in the bottom portion 132 of the extension-side pilot case 131 (only “two" are shown in FIG. 2). It communicates with chamber 2B.
  • Each passage 137 opens into an annular seat surface 138 formed on the piston 5 side of the outer peripheral portion 135 of the bottom portion 132 of the extension-side pilot case 131 .
  • a concave portion 139 is formed between the seat surface 138 and the inner peripheral portion of the bottom portion 132 on the inner peripheral side.
  • an annular protrusion 167 is formed on the outer peripheral edge 155 of the moving body 151 and protrudes toward the seat surface 138 of the extension-side pilot case 131 ("lower side" in FIG. 2).
  • the protrusion 167 contacts the seat surface 138 of the extension side pilot case 131 when the moving body 151 moves toward the anti-piston 5 side against the elastic force of the disc valve 157 , thereby By closing the opening on the side, communication between the second chamber 122 of the extension side back pressure chamber 113 and the cylinder lower chamber 2B is cut off.
  • the check valve 153 is formed via the second chamber 122 of the extension-side back pressure chamber 113, the gaps 166 and 152, the passage 168, and the first chamber 121.
  • An orifice 159 communicating with the orifice 156 is formed.
  • a disk valve 157 is arranged on the inner peripheral side of the convex portion 167 of the moving body 151 .
  • a disk valve 123 (second damping force generating mechanism) is provided on the side of the extension-side pilot case 131 opposite to the piston 5 .
  • the outer peripheral edge of the disc valve 123 is removably seated on an annular seat 124 formed on the outer peripheral portion 135 of the expansion pilot case 131 on the opposite side of the piston 5 (“lower side” in FIG. 2).
  • the seat portion 124 is arranged near the opening of the passage 137 on the side opposite to the piston 5 .
  • the inner peripheral portion of the disk valve 123 is clamped between the inner peripheral portion of the extension side pilot case 131 and the nut 17 screwed onto the shaft portion 32 of the piston bolt 31 .
  • a disk valve 123, a spacer 19, and a washer 18 are arranged in order from the piston 5 side ("upper side" in FIG. 2).
  • the moving body 151 moves against the elastic force of the disc valve 157 toward the side opposite to the piston 5, and the check valve 153 is released from the seat portion 154 .
  • the working fluid (pressure) in the first chamber 121 of the extension-side back pressure chamber 113 flows through the orifice 156 formed in the check valve 153 and the width across flat portion 35 formed in the shaft portion 32 of the piston bolt 31.
  • a plurality of notches 140 (only “two" are shown in FIG. 2) formed in the inner peripheral portion of the extension-side pilot case 131, and between the inner peripheral portion of the extension-side pilot case 131 and the seat portion 124.
  • the disc valve 123 Via the formed annular recess 141, the disc valve 123 is opened to flow (release) to the cylinder lower chamber 2B.
  • the disc valve 123 (second damping force generating mechanism) provides resistance to the flow of working fluid from the extension-side back pressure chamber 113 to the cylinder lower chamber 2B.
  • the working fluid (pressure) in the cylinder lower chamber 2B is transferred through the passage 137 (back pressure introduction passage) formed in the extension side pilot case 131, the orifice 159 formed in the seat portion 158 of the moving body 151, and a passage 168 (second through hole) that penetrates the moving body 151 in the axial direction (“vertical direction” in FIG. 2), and the gap 152, the check valve 153 is opened, and the extension side back pressure chamber 113 is introduced into the first chamber 121 of the cylinder lower chamber 2B, the expansion-side main valve 112 is prevented from being opened by the pressure in the cylinder lower chamber 2B.
  • the compression side damping force generating mechanism 171 has a compression side main valve 172 which abuts on an annular seat portion 174 formed on the upper end surface of the piston 5 so as to be separable and seatable.
  • the seat portion 174 is formed outside the opening of the contraction-side passage 8 .
  • the compression side damping force generating mechanism 171 has a bottomed cylindrical compression side pilot case 191 attached to the shaft portion 32 of the piston bolt 31 .
  • the compression side pilot case 191 has a bottom portion 192 and a cylindrical portion 193 that opens on the side of the piston 5 (“lower side” in FIG. 3).
  • An annular packing 175 made of an elastic material is baked on the compression side main valve 172 .
  • the packing 175 contacts the inner peripheral surface 194 of the cylindrical portion 193 of the contraction-side pilot case 191 over the entire circumference.
  • an annular compression side back pressure chamber 173 is formed between the compression side main valve 172 and the compression side pilot case 191 .
  • the pressure in the compression side back pressure chamber 173 acts on the compression side main valve 172 in the valve closing direction.
  • the compression-side damping force generating mechanism 171 extends from the axial passage 52 to the radial passage 55 formed in the shaft portion 32 of the piston bolt 31, the width across flat portion 36 formed in the shaft portion 32 of the piston bolt 31, the piston bolt It has a check valve 177 that allows the working fluid to flow into the contraction side passage 8 via an annular passage 176 formed between the shaft portion 32 of 31 and the piston 5 .
  • the check valve 177 abuts on an annular seat portion 178 formed on the upper end surface of the piston 5 so as to be separable and seatable.
  • the seat portion 178 is formed inside (on the inner peripheral side) of the opening of the contraction-side passage 8 .
  • the check valve 177 is formed with an orifice 179 that communicates the contraction side passage 8 and the axial passage 52 .
  • a check valve 180 is provided on the piston 5 side of the compression side pilot case 191 ("lower side" in FIG. 3). An outer peripheral edge of the check valve 180 abuts on an annular seat portion 181 formed in the compression side pilot case 191 so as to be separable and seatable.
  • the check valve 180 extends from the cylinder lower chamber 2B through the orifice 179 formed in the check valve 177, the width across flat portion 36 formed in the shaft portion 32 of the piston bolt 31, and the orifice formed in the check valve 180. 182 to allow the working fluid to flow into the compression side back pressure chamber 173 .
  • check valve 180 spacer 183, retainer 184, spacer 185, compression side main A valve 172, a spacer 186 and a check valve 177 are arranged.
  • a disc valve 187 (relief valve) is provided on the side of the compression side pilot case 191 opposite to the piston 5 ("upper side” in FIG. 3).
  • the disk valve 187 is a relief valve that opens when the pressure in the compression side back pressure chamber 173 reaches a predetermined pressure, and releases the working fluid (pressure) in the compression side back pressure chamber 173 to the cylinder upper chamber 2A. .
  • the disc valve 187 and the compression side pilot case 191 are partitioned by fan-shaped seats 196 arranged around the shaft hole 195 of the compression side pilot case 191 at regular intervals.
  • a plurality of (“five” in this embodiment) pressure receiving chambers 197 are formed.
  • a seat portion 198 is formed in the center of each seat portion 196 to contact the disc valve 187 .
  • Each pressure receiving chamber 197 includes a notch 199 formed in the inner peripheral portion of the compression side pilot case 191, a width across flat portion 36 formed in the shaft portion 32 of the piston bolt 31, and an orifice 182 formed in the check valve 180. , to the compression side back pressure chamber 173 via the check valve 180 .
  • a seat portion 200 extending in the circumferential direction is formed between a pair of adjacent seat portions 196 .
  • a pressure receiving chamber 201 defined by a seat portion 200 and a pair of seat portions 196 is formed between the disc valve 187 and the compression side pilot case 191 .
  • the pressure receiving chamber 201 communicates with the cylinder upper chamber 2A through a notch 202 formed in the seat portion 200 .
  • a passage 203 is formed in the contraction-side pilot case 191 so as to pass through the bottom portion 192 in the axial direction (“vertical direction” in FIG. 5).
  • the passage 203 has an upper end opened to the pressure receiving chamber 201 and a lower end opened to an annular recess 204 formed inside (inner peripheral side) of the seat portion 181 .
  • the pilot valve 61 has a valve spool 62 slidably provided in the common passage 51 and a seat portion 63 formed around the opening peripheral edge of the axial passage 54 .
  • the valve spool 62 is formed of a solid shaft and has a sliding portion 64 inserted into the axial passage 52 and a valve body 65 contacting the seat portion 63 in a separable manner.
  • a head 67 is formed at the upper end of the valve spool 62 .
  • An outer flange-shaped spring receiver 68 is formed at the lower end of the head 67 .
  • the spring receiver 68 is connected to the inner peripheral portion of a spring disk 69 that biases the valve body 65 in the valve opening direction.
  • An annular first chamber 37 is formed on the outer periphery of the upper end of the valve spool 62 on the side opposite to the piston 5 ("upper side" in FIG. 3) of the head 33 of the piston bolt 31 .
  • a bottomed cylindrical cap 38 with an open upper end is attached to the outer periphery of the head 33 of the piston bolt 31 .
  • An annular seal member 39 seals between the cap 38 and the head 33 of the piston bolt 31 .
  • An annular second chamber 40 is formed between the cap 38 and the head 33 of the piston bolt 31 .
  • a shaft hole 41 of the cap 38 through which the shaft portion 32 of the piston bolt 31 is inserted communicates with the width across flat portion 36 formed on the shaft portion 32 .
  • a disc valve 42 Between the head 33 of the piston bolt 31 and the cap 38, a disc valve 42, a spacer 43, and a retainer 44 are provided in this order from the head 33 side.
  • a disc valve 42 , a spacer 43 and a retainer 44 are provided within the second chamber 40 .
  • the disc valve 42 is a reverse valve that allows the working fluid to flow from the first chamber 37 to the second chamber 40 via a plurality of passages 45 (only “two" are shown in FIG. 3) formed in the head 33 . It is a stop valve.
  • the outer peripheral edge of the disk valve 42 abuts on an annular seat portion 46 formed on the head portion 33 of the piston bolt 31 so as to be separable and seatable.
  • the seat portion 46 is provided outside (peripheral side) of the opening of the passage 45 .
  • the inner peripheral edge of the retainer 44 is provided with a plurality of pieces (“two pieces in FIG. ) are formed.
  • a retainer 48 is provided between the cap 38 and the disc valve 187 .
  • a fail-safe valve 71 is configured in the first chamber 37 formed in the head 33 of the piston bolt 31 .
  • the fail-safe valve 71 has a seat portion (in the present embodiment, the “inner peripheral portion of the spring disk 69”) against which the spring receiver 68 (valve body) of the head portion 67 of the valve spool 62 abuts in a separable manner.
  • the outer peripheral edge of the spring disc 69 is held between the head 33 of the piston bolt 31 and the core 84 of the solenoid 81 .
  • a notch 66 having a width across flats is formed in the valve body 65 of the valve spool 62 .
  • the valve spool 62 moves in the valve opening direction of the pilot valve 61 (upward in FIG. 3), and the valve body 65 is fitted into the axial passage 52. be.
  • a pair of orifices 72 (only one is shown in FIG. 3) communicating between the axial passages 52 and 53 is formed between the valve body 65 and the axial passage 52 .
  • valve body 65 of the valve spool 62 when the coil 82 is energized, the valve body 65 of the valve spool 62 is seated on the seat portion 63, and the pilot valve 61 is closed.
  • the valve spool 62 receives the pressure on the side of the axial passage 54 from the circular pressure-receiving surface having the same area as the opening area of the axial passage 54.
  • the portion 64 receives the pressure on the side of the axial passage 52 by an annular pressure receiving surface having the same area as the cross-sectional area of the sliding portion 64 minus the cross-sectional area of the neck portion (reference numeral omitted) of the valve body 65 .
  • the opening pressure of the pilot valve 61 can be adjusted by controlling the energization of the coil 82 .
  • the biasing force of the spring disk 69 and the thrust generated by the plunger 86 are balanced, and the valve body 65 is separated from the seat portion 63 by a certain distance.
  • the solenoid 81 has a solenoid mechanism, a yoke 87, and a coil 82 (armature coil).
  • the solenoid mechanism section has an operating rod 83, a plunger 86 (armature) fixed to the outer periphery of the operating rod 83, and vertically divided cores 85 and 84.
  • the cores 85 and 84 are held coaxially by a holder 88 with a constant vertical spacing.
  • the operating rod 83 is guided in the axial direction (“vertical direction” in FIG. 1) by bushes 90 and 91 attached to the core lid 89 and a bush 91 attached to the core 84 .
  • An intra-rod passage 92 is formed in the operating rod 83 .
  • a seal member 93 seals between the lower end of the bottomed cylindrical yoke 87 and the core 84 .
  • An annular passage 94 is formed between the cylindrical portion 34 of the piston bolt 31 and the lower end portion of the core 84 .
  • the annular passage 94 communicates with the cylinder upper chamber 2A through a plurality of passages 95 (only “two” are shown in FIG. 1) provided in the cylindrical portion 34 of the piston bolt 31 .
  • a spool back pressure chamber 96 is formed inside the core 84 of the solenoid 81 (outer periphery of the head 67 of the valve spool 62).
  • the spool back pressure chamber 96 communicates with a rod back pressure chamber 97 formed inside the core lid 89 via a notch (reference numeral omitted) formed in the operating rod 83 and an intra-rod passage 97 .
  • the upper end of the yoke 87 is connected to the lower end of the piston rod 6 . That is, the lower end of piston rod 6 is connected to piston 5 via yoke 87 and piston bolt 31 .
  • a cable 101 is inserted through the hollow portion 10 (axial hole) of the piston rod 6 .
  • a cable 101 is connected to terminals 104 and 105 of a solenoid 81 by electric wires 102 and 103 projecting from the lower end side opening of the hollow portion 10 of the piston rod 6 .
  • terminal 104 is connected to the positive terminal of coil 82 and terminal 105 is connected to the negative terminal of coil 82 .
  • electric wires 102 and 103 projecting from the upper end opening of the hollow portion 10 of the piston rod 6 are connected to a connector (not shown) on the vehicle side (power supply device side).
  • the damping force generating mechanism 110 functions as a valve opening control mechanism
  • the working fluid in the cylinder upper chamber 2A is in the low moving speed range of the piston 5 in the extension stroke (hereinafter referred to as "piston speed").
  • the orifice 119 formed in the check valve 117, the annular passage 116, the radial passage 56, the axial passage 54, the radial passage 57, the width across flat portion 35, and the orifice 156 the extension side It is introduced into the first chamber 121 of the back pressure chamber 113 .
  • the working fluid in the cylinder upper chamber 2A passes through the notch 202, the pressure receiving chamber 201, the passage 203, and the recess 204, opens the check valve 180, and is introduced into the compression side back pressure chamber 173. be done. This prevents the compression side main valve 172 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 173 during the extension stroke passes through the orifice 182, the width across flat portion 36, the check valve 177, and the compression side passage 8, and flows into the cylinder lower chamber 2B.
  • the orifice characteristic of the orifice 182 and the valve characteristic damping force of the check valve 177 are obtained.
  • the working fluid in the cylinder lower chamber 2B is introduced into the compression side back pressure chamber 173 via the compression side passage 8, the orifice 179, the width across flat portion 36, and the orifice 182.
  • the working fluid in the cylinder lower chamber 2B flows through the passage 137 formed in the extension-side pilot case 131, the second chamber 122, the orifice 159 formed in the seat portion 158, and the passage formed in the moving body 151. 168 , the check valve 153 is opened and the fuel is introduced into the extension-side back pressure chamber 113 . This prevents the extension side main valve 112 from opening due to the pressure in the cylinder lower chamber 2B during the compression stroke.
  • the damping force generating mechanism 110 in the first embodiment functions as a variable damping force mechanism that varies the damping force according to the piston frequency even if the piston speed is the same.
  • the amplitude of the piston 5 is small when the piston frequency is high.
  • the amount of deflection of the disc valve 157 (elastic body) is small.
  • the moving body 151 moves toward the counter-piston 5 side and the seat portion 154 leaves the check valve 153. Since the convex portion 167 of the outer peripheral portion 155 of the body 151 is not seated on the seat surface 138 of the extension side pilot case 131, the second chamber 122 of the extension side back pressure chamber 113 communicates with the cylinder lower chamber 2B.
  • the working fluid in the second chamber 122 flows into the cylinder lower chamber 2B, and the volume of the first chamber 121 increases, so the pressure rise in the first chamber 121 is suppressed.
  • the extension side main valve 112 is easily opened, and the damping force characteristic of the extension side damping force generating mechanism 111 (first damping force generating mechanism) becomes soft.
  • the hard characteristic disk valve 123 (second damping force generating mechanism) does not open.
  • the working fluid in the extension-side back pressure chamber 113 flows through the orifice 156 formed in the check valve 153 and the piston.
  • the disk valve 123 (second damping force generating mechanism) is opened via the width across flat portion 35 formed on the shaft portion 32 of the bolt 31, the notch 140 formed on the extension side pilot case 131, and the recess 141. and flows into the cylinder lower chamber 2B. At this time, the disk valve 123 generates a hard characteristic damping force.
  • the piston frequency varies the flow area by the orifice 119 formed in the check valve 117 and the orifice 156 formed in the check valve 153. It can be adjusted by varying the flow rate of the working fluid introduced into the pressure chamber 113 . Further, the valve opening pressure of the extension side main valve 112 can be adjusted by varying the disk rigidity of the extension side main valve 112 when the piston frequency is high. On the other hand, the valve opening pressure of the extension side main valve 112 can be adjusted by varying the disk rigidity of the disk valve 123 (second damping force generating mechanism) when the piston frequency is low.
  • the conventional cylinder device adjusts the load deflection characteristics of the moving body by varying the hardness of the rubber of the seal ring, the moving body affects the transient characteristics (switching from hard damping force to soft damping force).
  • the degree of freedom of the load deflection characteristics is low, and there is room for improvement.
  • the piston frequency can be adjusted by varying the flow area of the orifice 119 formed in the check valve 117 and the orifice 156 formed in the check valve 153, and the piston frequency can be freely adjusted. degree can be improved.
  • the damping force generation mechanism is equal to the axial length of the adjustment mechanism.
  • the shaft length of (the control valve device) was increased, and the cylinder device was increased in size, making it difficult to install it in a small vehicle.
  • the extension-side back pressure chamber 113 is divided into a first chamber 121 on the side of the piston 5 and a second chamber 122 on the side opposite to the piston 5 by a moving body 151 (moving member).
  • a passage 137 (first through hole) for communicating the second chamber 122 and the cylinder lower chamber 2B is formed in the bottom portion 132 of the side pilot case 131, and the convex portion 167 of the outer peripheral portion 155 of the moving body 151 extends through the extension side pilot case 131.
  • the second chamber 122 and the cylinder lower chamber 2B are brought into contact with the seat surface 138 so that they can be seated and detached, thereby controlling the communication between the second chamber 122 and the cylinder lower chamber 2B. ), and by extension, an increase in the axial length of the cylinder device 1 can be suppressed.
  • a metal seal is used to seal between the outer peripheral surface 163 of the moving body 151 and the inner peripheral surface 134 of the extension side pilot case 131, thereby
  • the pressure chamber 113 is divided into a first chamber 121 on the side of the piston 5 and a second chamber 122 on the side opposite to the piston 5 .
  • an annular seal is provided between the outer peripheral surface 163 of the moving body 151 (moving member) and the inner peripheral surface 134 of the extension side pilot case 131 .
  • a damping force generating mechanism 110 (control valve device) is configured by sealing with a ring 212 (for example, an “O-ring” or the like).
  • the seal ring 212 is attached to an annular seal groove 213 formed in the outer peripheral surface 163 of the moving body 151 .
  • the damping force generating mechanism 221 (control valve device) in the third embodiment does not include the common passage 51, the pilot valve 61, and the solenoid 81 in contrast to the damping force generating mechanism 110 in the first embodiment.
  • the head 33 of the piston bolt 31 is directly connected to the lower end of the piston rod 6 .
  • the extension-side back pressure chamber 113 formed in the extension-side pilot case 131 is divided into a first chamber 121 on the side of the piston 5 and a second chamber 122 on the side opposite to the piston 5 by a free valve 251 (moving member).
  • the free valve 251 consists of a disk with packing having an annular disk 252 and an annular elastic seal member 253 fixed to the outer peripheral edge of the disk 252 .
  • the elastic seal member 253 has a lip portion 254 provided on the piston 5 side of the disk 252 (“upper side” in FIG. 8). The lip portion 254 is slidably brought into contact with the small inner diameter portion 231 formed on the cylindrical portion 133 of the extension pilot case 131 on the side opposite to the piston 5 (“lower side” in FIG. 8).
  • the elastic seal member 253 has an annular seal portion 255 (elastic body) whose tip portion 256 (lower end) abuts against the seat surface 138 of the bottom portion 132 of the extension side pilot case 131 .
  • the annular seal portion 255 is formed such that a cross section taken along the axial plane of the disk 252 (the plane including the axis of the piston bolt 31) tapers toward the tip portion 256.
  • each passage 137 is opened outside (peripheral side) the contact portion of the elastic seal member 253 with the tip portion 256 of the annular seal portion 255 .
  • An annular third chamber 230 is formed between the annular elastic seal member 253 and the bottom portion 132 of the extension side pilot case 131 and the small inner diameter portion 231 of the cylindrical portion 133 .
  • the third chamber 230 has a substantially right-angled triangular cross-section taken along the axial plane of the disk 252 .
  • the second chamber 122 of the extension-side back pressure chamber 113 includes a notch 257 formed in the tip portion 256 of the annular seal portion 255 of the elastic seal member 252, the third chamber 230, and the extension-side pilot case 121. It communicates with the cylinder lower chamber 2B via the passage 137 .
  • the disk 252 of the free valve 251 is supported by the annular pilot case retainer 241 and the annular disk 258 so as to be movable in the axial direction of the piston bolt 31 ("vertical direction" in FIG. 8).
  • the shaft portion 32 of the piston bolt 31 is inserted into the inner diameter portion of the disc 258 .
  • the outer diameter of disc 258 is greater than the inner diameter of disc 252 of free valve 251 .
  • the inner peripheral edge of the disc 252 of the free valve 251 is received by the outer peripheral edge of the disc 258 .
  • the contact portion 259 between the disk 252 and the disk 258 of the free valve 151 extends from the cylinder lower chamber 2B through the passage 137, the third chamber 230, the notch 257 formed in the annular seal portion 255, and the second chamber 122. It functions as a check valve that allows the working fluid to flow through to the first chamber 121 of the extension-side back pressure chamber 113 and as a second through hole that allows communication between the first chamber 121 and the second chamber 122 .
  • Pilot case retainer 241 is provided in first chamber 121 of extension-side back pressure chamber 113 .
  • An annular seat portion 243 is formed on the outer peripheral edge portion of the pilot case retainer 241 on the side opposite to the piston 5 (“lower side” in FIG. 8). The seat portion 243 receives the vicinity of the elastic seal member 253 of the disk 252 of the free valve 251 .
  • An annular recess 245 is formed between the inner peripheral portion of the pilot case retainer 241 and the seat portion 243 .
  • a plurality of recesses 245 (in FIG. 8, The first chamber 121 and the second chamber 122 are communicated with each other by the notch 246 and the notch 243 (only “two" are shown).
  • the pilot case retainer 241 is provided between the extension side main valve 112 and the extension side pilot case 131 . Between the inner peripheral portion of the extension side main valve 112 and the inner peripheral portion of the pilot case retainer 241, a plurality of (“two” in this embodiment) are provided in order from the piston 5 side (“upper side” in FIG. 8). Spacers 222, disk valves 223, one spacer 222 and disk 225 are arranged. In the disk valve 223, the working fluid in the cylinder upper chamber 2A passes through the extension side passage 7 (first passage), the orifice 119 formed in the check valve 117, and the shaft portion 32 of the piston bolt 31 during the extension stroke. An orifice 224 is formed through the width across flats portion 35 to introduce into the first chamber 121 of the extension side back pressure chamber 113 .
  • a spacer 226, a spacer 227, a disk 258, and a disk 228 are arranged in this order from the piston 5 side.
  • the spacer 227 has the same plate thickness as the disc 252 of the free valve 251 and is arranged on the inner circumference of the disc 252 of the free valve 251 .
  • the outer diameter of the spacer 227 is smaller than the inner diameter of the disk 252 of the free valve 251 . Thereby, an annular gap 229 is formed between the spacer 227 and the disk 252 .
  • the damping force generating mechanism 110 in the third embodiment functions as a variable damping force mechanism that varies the damping force according to the piston frequency even if the piston speed is the same.
  • the amplitude of the piston 5 is small when the piston frequency is high.
  • the deflection amount of the free valve 251 is small.
  • the second chamber of the extension-side back pressure chamber 113 communicates with the cylinder lower chamber 2B via the notch 257 formed in the annular seal portion 255, the third chamber 230, and the passage 137.
  • the working fluid in the second chamber 122 flows into the cylinder lower chamber 2B, and the volume of the first chamber 121 increases, so the pressure rise in the first chamber 121 is suppressed.
  • the extension side main valve 112 is easily opened, and the damping force characteristic of the extension side damping force generating mechanism 111 (first damping force generating mechanism) becomes soft.
  • the hard characteristic disk valve 123 (second damping force generating mechanism) does not open.
  • the working fluid in the extension-side back pressure chamber 113 flows through the orifice 224 formed in the disk valve 223 and the piston bolt.
  • the disk valve 123 (second damping force generating mechanism) is opened via the width across flat portion 35 formed on the shaft portion 32 of 31, the notch 140 formed on the extension side pilot case 131, and the recess 141. and flows into the cylinder lower chamber 2B. At this time, the disk valve 123 generates a hard characteristic damping force.
  • the piston frequency varies the flow area of the orifice 119 formed in the check valve 117 and the orifice 224 formed in the disk valve 223, that is, the pressure from the cylinder upper chamber 2A to the extension side back pressure It can be adjusted by varying the flow rate of the working fluid introduced into the chamber 113 .
  • the valve opening pressure of the extension side main valve 112 can be adjusted by varying the disk rigidity of the extension side main valve 112 when the piston frequency is high.
  • the valve opening pressure of the extension side main valve 112 can be adjusted by varying the disk rigidity of the disk valve 123 (second damping force generating mechanism) when the piston frequency is low.
  • the compression side damping force generating mechanism 235 of the damping force generating mechanism 221 in the third embodiment has the same structure and operation as the conventional conventional compression side damping force generating mechanism, so the description of the specification will be simplified. Therefore, the detailed description of the compression-side damping force generating mechanism 235 is omitted.
  • a damping force generating mechanism 261 (control valve device) according to the fourth embodiment includes a common passage 51, a pilot valve 61, and a solenoid 81 in contrast to the damping force generating mechanism 110 according to the first embodiment, as in the third embodiment. do not have.
  • the head 33 (see FIG. 7) of the piston bolt 31 is directly connected to the lower end of the piston rod 6 (see FIG. 7).
  • the damping force generating mechanism 110 in the first embodiment, the movement of the moving body 151 (moving member) toward the side opposite to the piston 5 is suppressed by the disk valve 157 (elastic body). .
  • the elastic member 262 protrudes toward the side opposite to the piston 5 (“lower side” in FIG. 9), and the tip (lower end) contacts the seat surface 138 formed on the outer peripheral portion 135 of the extension-side pilot case 131. be done.
  • the elastic member 262 is formed such that a cross section taken along the axial plane of the moving body 151 (the plane including the axis of the piston bolt 31) tapers toward the tip.
  • the length (height) of the elastic member 262 in the axial direction (“vertical direction” in FIG. 9) is equal to the length in the radial direction (the same length as the width of the convex portion 167 of the outer peripheral portion 155 of the moving body 151). is longer than
  • a passage 263 is formed in the bottom portion 132 of the extension side pilot case 131 to communicate the second chamber 122 of the extension side back pressure chamber 113 with the cylinder lower chamber 2B.
  • the second chamber 122 side of the passage 263 is opened inside (inner peripheral side) of the portion of the seat surface 138 with which the elastic member 262 abuts.
  • the movement of the moving body 151 (moving member) to the side opposite to the piston 5 (“downward” in FIG. 9) is controlled by the disk valve 157 and the moving body 151. It is configured to be suppressed by two elastic bodies, namely, an annular elastic member 262 fixed to the outer peripheral portion 155 of the.
  • the damping force generating mechanism 271 (control valve device) in the fifth embodiment
  • the movement of the moving body 151 (moving member) to the side opposite to the piston 5 (“lower side” in FIG. 10) is controlled by the disk valve 157. and the coil spring 272.
  • Coil spring 272 is interposed between convex portion 167 of outer peripheral portion 155 of moving body 151 and bottom portion 132 of extension-side pilot case 131 .
  • the movement of the moving body 151 (moving member) to the side opposite to the piston 5 (“lower side” in FIG. 10) is controlled by the disk valve 157 and the coil spring 272. and two elastic bodies.
  • the damping force generating mechanism 281 (control valve device) in the sixth embodiment
  • the movement of the moving body 151 (moving member) to the side opposite to the piston 5 (“lower side” in FIG. 11) is controlled by the disk valve 157. and the disk spring 282.
  • the disc spring 282 is interposed between the outer peripheral portion 155 of the moving body 151 and the bottom portion 132 of the extension side pilot case 131 .
  • the second chamber 122 of the extension side back pressure chamber 113 and the cylinder lower chamber 2B are formed in the bottom portion 132 of the extension side pilot case 131 as in the first embodiment (see FIG. 2). (only “two" are shown).
  • a damping force generating mechanism 291 (control valve device) in the seventh embodiment has a common passage 51, a pilot valve 61, and a solenoid 81 in contrast to the damping force generating mechanism 110 in the first embodiment, as in the third to sixth embodiments. does not have In the damping force generating mechanism 291, the head 33 (see FIG. 7) of the piston bolt 31 is directly connected to the lower end of the piston rod 6 (see FIG. 7).
  • the pressure (pilot pressure).
  • the mechanism functioning as the check valve 153 of the damping force generating mechanism 110 of the first embodiment is placed on the disc valve 123 (second damping force generating mechanism) side. established.
  • An annular disc valve 292 is provided in the first chamber 121 of the extension-side back pressure chamber 113 .
  • the shaft portion 32 of the piston bolt 31 is inserted into the inner diameter portion of the disc valve 292 .
  • the outer diameter of the disc valve 292 is smaller than the outer diameter of the annular seat portion 154 formed on the moving body 151 .
  • the inner periphery of disk valve 292 is clamped between spacer 162 and retainer 294 .
  • the disc valve 292 is formed with an orifice 293 that communicates between the first chamber 121 of the extension-side back pressure chamber 113 and the width across flat portion 35 formed on the shaft portion 32 of the piston bolt 31 .
  • the retainer 294 is arranged between the disc valve 292 and the boss 160, and the shaft portion 32 of the piston bolt 31 is inserted into its inner diameter portion.
  • the outer diameter of retainer 294 is larger than the outer diameter of boss 160 .
  • An annular recess 295 is formed on the inner peripheral edge of the moving body 151 on the side of the piston 5 (“upper side” in FIG. 12). The concave portion 295 of the moving body 151 is received by the surface of the outer peripheral portion of the retainer 294 on the side opposite to the piston 5 .
  • a An orifice passage 296 is formed to communicate between the annular recess 141 and the cylinder lower chamber 2B.
  • a disk valve 297 , a retainer 299 , and a check valve 300 are arranged in order from the piston 5 side (“upper side” in FIG. 12 ) between the inner peripheral portion of the extension-side pilot case 131 and the disk valve 123 .
  • the check valve 300 allows the working fluid to flow from the cylinder lower chamber 2B to the recess 141 via the orifice passage 296 .
  • the disc valve 297 is formed with an orifice 298 that communicates between the width across flat portion 35 formed on the shaft portion 32 of the piston bolt 31 and the annular recess 141 .
  • the working fluid in the cylinder upper chamber 2A passes through the width across flat portion 35 formed in the shaft portion 32 of the piston bolt 31 and the orifice 293 formed in the disc valve 292. and introduced into the first chamber 121 of the extension-side back pressure chamber 113 .
  • the pressure (pilot pressure) in the first chamber 121 is maintained by the check valve 300 blocking the opening of the orifice passage 296 .
  • the disc valve 123 is opened.
  • the working fluid in the cylinder lower chamber 2B passes through the orifice passage 296 to open the check valve 300, and the annular recess 141, the orifice 298 formed in the disc valve 297, and the shaft of the piston bolt 31 It is introduced into the first chamber of the extension side back pressure chamber 113 via the width across flats portion 35 formed in the portion 32 and the orifice 293 formed in the disc valve 292 .
  • the expansion side main valve 122 from opening due to an increase in pressure in the cylinder lower chamber 2B.
  • the frequency adjustment mechanism having the moving body 151 is applied to the rebound damping force generating mechanism 111, but only the compression damping force generating mechanism 171 or the rebound damping force is applied.
  • a frequency adjustment mechanism can be applied to both the generating mechanism 111 and the compression-side damping force generating mechanism 171 .
  • the damping force generating mechanisms 221, 261, 271, 281, and 291 are configured by providing the common passage 51, the pilot valve 61, and the solenoid 81 as in the first to second embodiments. can do.
  • the damping force generating mechanism 291 can be configured by providing the seal ring 212 on the outer peripheral portion 155 of the moving body 151 as in the second embodiment.
  • 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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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)
PCT/JP2022/029054 2021-08-02 2022-07-28 シリンダ装置及び制御弁装置 WO2023013511A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN202280047511.1A CN117642564A (zh) 2021-08-02 2022-07-28 缸装置以及控制阀装置
JP2023540296A JP7531063B2 (ja) 2021-08-02 2022-07-28 制御弁装置
KR1020247001890A KR20240022632A (ko) 2021-08-02 2022-07-28 실린더 장치 및 제어 밸브 장치
DE112022003790.3T DE112022003790T5 (de) 2021-08-02 2022-07-28 Zylindervorrichtung und regelventilvorrichtung

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JP2021126693 2021-08-02

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KR (1) KR20240022632A (zh)
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150276005A1 (en) * 2014-03-28 2015-10-01 Mando Corporation Piston assembly for shock absorber
WO2017047661A1 (ja) * 2015-09-14 2017-03-23 日立オートモティブシステムズ株式会社 緩衝器
WO2018164167A1 (ja) * 2017-03-10 2018-09-13 日立オートモティブシステムズ株式会社 緩衝器
JP2021021436A (ja) * 2019-07-26 2021-02-18 日立オートモティブシステムズ株式会社 減衰力調整式緩衝器

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015220707B4 (de) 2015-10-23 2022-06-02 Zf Friedrichshafen Ag Steueranordnung für eine frequenzabhängige Dämpfventileinrichtung eines Schwingungsdämpfers, sowie Verfahren zur plastischen Verformung des Topfbodens der Steueranordnung.
JP7321953B2 (ja) 2020-02-17 2023-08-07 株式会社神戸製鋼所 自動溶接システム、溶接方法、学習装置、学習済みモデルの生成方法、学習済みモデル、推定装置、推定方法、及びプログラム

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150276005A1 (en) * 2014-03-28 2015-10-01 Mando Corporation Piston assembly for shock absorber
WO2017047661A1 (ja) * 2015-09-14 2017-03-23 日立オートモティブシステムズ株式会社 緩衝器
WO2018164167A1 (ja) * 2017-03-10 2018-09-13 日立オートモティブシステムズ株式会社 緩衝器
JP2021021436A (ja) * 2019-07-26 2021-02-18 日立オートモティブシステムズ株式会社 減衰力調整式緩衝器

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KR20240022632A (ko) 2024-02-20
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CN117642564A (zh) 2024-03-01
JP7531063B2 (ja) 2024-08-08

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