WO2024241407A1 - 減衰力調整装置、緩衝装置 - Google Patents

減衰力調整装置、緩衝装置 Download PDF

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Publication number
WO2024241407A1
WO2024241407A1 PCT/JP2023/018847 JP2023018847W WO2024241407A1 WO 2024241407 A1 WO2024241407 A1 WO 2024241407A1 JP 2023018847 W JP2023018847 W JP 2023018847W WO 2024241407 A1 WO2024241407 A1 WO 2024241407A1
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WO
WIPO (PCT)
Prior art keywords
damping force
control valve
oil
valve
contact
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2023/018847
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
剛太 中野
力 柳澤
智亮 篠崎
立矢 斉藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Astemo Ltd
Original Assignee
Hitachi Astemo Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Astemo Ltd filed Critical Hitachi Astemo Ltd
Priority to JP2025521624A priority Critical patent/JPWO2024241407A1/ja
Priority to CN202380094552.0A priority patent/CN120731332A/zh
Priority to KR1020257027974A priority patent/KR20250135319A/ko
Priority to PCT/JP2023/018847 priority patent/WO2024241407A1/ja
Priority to DE112023005328.6T priority patent/DE112023005328T5/de
Priority to DE112023005586.6T priority patent/DE112023005586T5/de
Priority to CN202380095890.6A priority patent/CN120936821A/zh
Priority to KR1020257030792A priority patent/KR20250145112A/ko
Priority to PCT/JP2023/045458 priority patent/WO2024241615A1/ja
Priority to JP2025521791A priority patent/JPWO2024241615A1/ja
Publication of WO2024241407A1 publication Critical patent/WO2024241407A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination
    • 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
    • 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
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/346—Throttling passages in the form of slots arranged in cylinder walls
    • 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
    • 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
    • F16F9/3488—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 intended to affect valve bias or pre-stress
    • 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
    • F16F9/464—Control of valve bias or pre-stress, e.g. electromagnetically
    • 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
    • F16F9/465—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 using servo control, the servo pressure being created by the flow of damping fluid, e.g. controlling pressure in a chamber downstream of a pilot passage
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
    • F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded

Definitions

  • the present invention relates to a damping force adjustment device and a shock absorber.
  • the damping valve described in Patent Document 1 has a pressure control valve body that seats and releases on a pressure control valve seat, and an on-off valve body that seats and releases on an on-off valve seat, and is equipped with a valve body member that opens and closes the upstream and downstream sides of a pilot passage.
  • the damping valve described in Patent Document 1 also has a disc spring that is interposed between the step and the valve body member to separate the pressure control valve body from the pressure control valve seat and to urge the valve body member in a direction that brings the on-off valve body closer to the on-off valve seat, and a solenoid that can drive the valve body member against the urging force of the disc spring.
  • the damping valve described in Patent Document 1 supplies current to the solenoid to apply a thrust to the valve body member, and presses the pressure control valve body of the valve body member against the urging force of the disc spring against the pressure control valve seat.
  • An object of the present invention is to provide a damping force adjusting device and the like that has good thrust efficiency by reducing waste of thrust from an actuator portion.
  • the present invention which was completed with this objective in mind, is a damping force adjusting device that includes a valve body that is provided in a flow path through which a fluid flows and that changes the area of the flow path; a case member that houses the valve body and has a valve seat with a through hole that can be closed by the valve body; an actuator unit that applies thrust to a movable member that can contact the side of the valve body opposite the side facing the valve seat; a first spring member that has one end that contacts the valve body and the other end that contacts the movable member; and a second spring member that has one end that contacts the valve body and the other end that is fixed to the case member.
  • FIG. 1 is a diagram showing an example of a schematic configuration of a hydraulic shock absorber according to a first embodiment
  • 1 is a diagram showing an example of a cross section of a damping force generating device according to a first embodiment
  • 3 is a diagram showing an example of a perspective cross section of a main valve portion and a damping force adjuster of the first embodiment
  • FIG. 3 is a diagram showing an example of a partial cross section of a main valve portion and a damping force adjuster of the first embodiment
  • FIG. 13A and 13B are diagrams illustrating an example of an oil flow when the moving speed of the piston portion is low in a state in which the pressing force of the pressing member is set to the smallest.
  • 13A and 13B are diagrams illustrating an example of an oil flow when the moving speed of a piston portion is high in a state in which the pressing force of a pressing member is set to a minimum.
  • 13A and 13B are diagrams illustrating an example of an oil flow when the moving speed of the piston portion is low in a state in which the pressing force of the pressing member is maximized.
  • 13A and 13B are diagrams illustrating an example of an oil flow when the moving speed of the piston portion is high in a state in which the pressing force of the pressing member is maximized.
  • 11 is a diagram illustrating an example of an oil flow when a solenoid portion is in a non-energized state and a piston portion moves at a low speed.
  • FIG. 11A and 11B are diagrams illustrating an example of the flow of oil when a solenoid portion is in a non-energized state and a piston portion moves at a high speed.
  • FIG. 13 is a diagram showing an example of a schematic configuration of a damping force generating device according to a second embodiment.
  • FIG. 13 is a diagram showing an example of a schematic configuration of a damping force generating device according to a third embodiment.
  • FIG. 13 is a diagram showing an example of a partial cross section of a damping force generating device according to a third embodiment.
  • 13 is a diagram showing an example of a state in which the biasing member is in contact with a first edge portion and is not in contact with a second edge portion;
  • FIG. 13 is a diagram showing an example of a state in which the biasing member is in contact with a first edge portion and is not in contact with a second edge portion;
  • FIG. 13 is a diagram showing an example of a state in which a biasing member is in contact with a first edge portion and a second edge portion;
  • FIG. 13 is a diagram showing an example of a state in which the control valve is seated on the round.
  • 5 is a diagram showing an example of the correlation between the current supplied to a solenoid portion and the thrust of the solenoid portion, the spring constant of a biasing member, and the valve opening amount of a control valve.
  • FIG. 1 is a diagram showing an example of a schematic configuration of a hydraulic shock absorber 1 according to a first embodiment.
  • the hydraulic shock absorber 1 includes a cylinder portion 10 that contains oil, and a rod 20 that has one side that is slidably inserted into the cylinder portion 10 and the other side that is provided so as to protrude from the cylinder portion 10.
  • the hydraulic shock absorber 1 also includes a piston portion 30 that is provided at one end of the rod 20, and a bottom portion 40 that is provided at one end of the cylinder portion 10.
  • the hydraulic shock absorber 1 further includes a damping force generating device 100 that is provided outside the cylinder portion 10 and generates a damping force.
  • the longitudinal direction of the cylinder section 10 shown in FIG. 1 may be referred to as the "axial direction", the lower side of FIG. 1 in the axial direction may be referred to as the "one side”, and the upper side of FIG. 1 may be referred to as the “other side”.
  • the left-right direction of the cylinder section 10 shown in FIG. 1 may be referred to as the "radial direction”, and in the radial direction, the central axis side of the cylinder section 10 may be referred to as the “inner side”, and the side away from the central axis may be referred to as the "outer side".
  • the cylinder section 10 has a cylinder 11 that contains oil, an outer cylinder body 12 that is provided on the outside of the cylinder 11, and a damper case 13 that is provided on the outside of the cylinder 11 and further outside the outer cylinder body 12.
  • the cylinder 11 is formed in a cylindrical shape, and a communication hole 11H that connects the inside and the outside is formed at the other end.
  • the external cylinder 12 is formed in a cylindrical shape.
  • the external cylinder 12 forms a communication path L between the cylinder 11.
  • the external cylinder 12 has an external cylinder opening 12H and an outer connection portion 12J at a position facing the damping force generator 100.
  • the outer connection portion 12J has an oil flow path, and protrudes outward to form a connection portion with the damping force generator 100.
  • the damper case 13 is formed in a cylindrical shape.
  • the damper case 13 forms a reservoir chamber R between itself and the outer cylinder body 12, where oil accumulates.
  • the reservoir chamber R absorbs oil from within the cylinder 11 and supplies oil to the cylinder 11 as the rod 20 moves relative to the cylinder 11.
  • the reservoir chamber R also accumulates oil that flows out from the damping force generating device 100.
  • the damper case 13 also has a case opening 13H at a position opposite the damping force generating device 100.
  • the rod 20 is a rod-shaped member that extends long in the axial direction.
  • the rod 20 holds the piston portion 30 on one side.
  • the rod 20 is also connected on the other side to, for example, the vehicle body via a connecting member or the like (not shown).
  • the piston portion 30 has a piston body 31 having a plurality of piston oil passage ports 311, a piston valve 32 that opens and closes the other side of the piston oil passage ports 311, and a spring 33 provided between the piston valve 32 and one end of the rod 20.
  • the piston portion 30 divides the oil in the cylinder 11 into a first oil chamber Y1 and a second oil chamber Y2.
  • the bottom portion 40 has a valve seat 41, a check valve portion 43 provided on the other side of the valve seat 41, and a fixing member 44 provided in the axial direction.
  • the bottom portion 40 separates the first oil chamber Y1 from the reservoir chamber R.
  • FIG. 2 is a diagram showing an example of a cross section of the damping force generating device 100 of the first embodiment.
  • FIG. 3 is a diagram showing an example of a perspective cross section of the main valve portion 50 and the damping force adjusting portion 60 according to the first embodiment.
  • FIG. 4 is a diagram showing an example of a partial cross section of the main valve portion 50 and the damping force adjusting portion 60 according to the first embodiment.
  • the longitudinal direction of the damping force generating device 100 shown in Fig. 2 (i.e., a direction intersecting (e.g., a direction substantially perpendicular) to the axial direction of the cylinder section 10 (see Fig. 1)) may be referred to as the "second axial direction”.
  • the central axis side of the cylinder section 10 in the second axial direction (the left side of the damping force generating device 100 in Fig. 2) may be referred to as the "first side”
  • the side away from the central axis of the cylinder section 10 (the right side of the damping force generating device 100 in Fig. 2) may be referred to as the "second side”.
  • second radial direction In the second radial direction, the side of the central axis along the second axis may be referred to as a "second inner side", and the side away from the central axis along the second axis may be referred to as a "second outer side”.
  • the damping force generating device 100 includes a main valve section 50 that mainly generates the damping force in the hydraulic shock absorber 1 of the first embodiment, and a damping force adjustment section 60 that adjusts the magnitude of the damping force generated by the damping force generating device 100.
  • the damping force generating device 100 further includes a communication section 80 that forms a parallel flow path with the main valve section 50, a connection flow path section 90 that forms an oil flow path from the communication path L to the main valve section 50 and the communication section 80, and an outer housing 100C that houses various parts that constitute the damping force generating device 100.
  • the main valve section 50 has a main valve 51 that generates a damping force by controlling the flow of oil to throttle it, and a main valve seat 52 that faces the main valve 51 and comes into contact with it.
  • the main valve 51 is a disk-shaped member that has an opening 51H on the second inner side and is elastically deformable.
  • the main valve 51 can be made of a metal such as iron.
  • the communication portion 80 passes through the opening 51H of the main valve 51.
  • the second inner side of the main valve 51 is sandwiched between the main valve seat 52 and a spacer member 684 (described later).
  • the main valve 51 faces the second side of the main valve seat 52.
  • the main valve 51 configured as described above has its positional movement in the second radial direction restricted by the connecting portion 80.
  • the second inner side of the main valve 51 has its movement in the second axial direction restricted by the main valve seat 52 and a spacer member 684 (described later). Meanwhile, the second outer side of the main valve 51 is capable of moving in the second axial direction by deformation.
  • the main valve 51 generates a damping force by throttling the flow of oil in the main flow passage 53 (described later) of the main valve seat 52.
  • the main valve seat 52 is a cylindrical member having an opening 52H on the second inner side.
  • the main valve seat 52 has a communication portion 80 inserted into a part of the opening 52H (see FIG. 4).
  • the main valve seat 52 has a central seat portion 520 around the opening 52H.
  • the main valve seat 52 also has an inner seat portion 521 provided on the second outer side of the central seat portion 520, and an outer seat portion 522 provided on the second outer side of the inner seat portion 521.
  • the main valve seat 52 has a main flow passage 53 that penetrates in the second axial direction on the second outer side of the opening 52H.
  • the central seat portion 520 protrudes in an arc shape toward the main valve 51.
  • the central seat portion 520 faces a second inner portion of the main valve 51.
  • the inner seat portion 521 is formed in an annular shape.
  • the inner seat portion 521 protrudes beyond the flow path opening 532 toward the main valve 51.
  • the protruding height of the inner seat portion 521 is substantially equal to the heights of the central seat portion 520 and the outer seat portion 522.
  • the outer seat portion 522 is formed in an annular shape and protrudes beyond the flow path port 532 toward the main valve 51 side.
  • the inner seat portion 521 and the outer seat portion 522 form contact points with the main valve 51 .
  • the inner seat portion 521 has a plurality of grooves 521T formed along the second radial direction.
  • the flow path cross-sectional area of each groove portion 521T is formed to be relatively small.
  • the grooves 521T form a so-called orifice flow path.
  • Each groove portion 521T forms a flow path through which oil flows from the second inner side of the inner seat portion 521 to the second outer side of the inner seat portion 521 when the main valve 51 is in contact with the inner seat portion 521.
  • the main flow passages 53 form a parallel flow passage with respect to the back pressure flow passage 77 of the control sheet 76 described later (see FIG. 4).
  • a plurality of main flow passages 53 are provided in the circumferential direction (see FIG. 3).
  • the first side flow passage opening 531 of each main flow passage 53 communicates with the opening 52H and faces the connecting flow passage portion 90.
  • the second side flow passage opening 532 of each main flow passage 53 is located between the central sheet portion 520 and the inner sheet portion 521.
  • the damping force adjusting unit 60 has an advance/retract unit 61 that advances/retracts a control valve 70 (described later) with respect to a control seat 76, a cap unit 67 that covers various components such as the main valve unit 50, and a back pressure generating mechanism 68 that changes the ease of deformation of the main valve 51 with respect to the main valve seat 52.
  • the damping force adjusting unit 60 also has a control valve 70 that throttles and controls the flow of oil in a communication unit 80, a control seat 76 that faces the control valve 70 and is a valve seat with which the control valve 70 comes into contact, and a throttle member 83 that throttles the flow of oil.
  • the damping force adjusting unit 60 also has a restriction member 72 that restricts the movement of the control valve 70 to the second side, and a biasing member 75 that applies a force to the control valve 70 in a direction opposite to the thrust of the solenoid unit 62.
  • the damping force adjustment portion 60 has a first spacer member 73A interposed between the biasing member 75 and the regulating member 72, a second spacer member 73B interposed between the regulating member 72 and the cap portion 67, and a third spacer member 73C interposed between the control sheet 76 and the biasing member 75.
  • the advancing/retreating unit 61 has a solenoid unit 62 that uses an electromagnet to advance and retract a pressing member 63 (described later), the pressing member 63 that presses the control valve 70 against a control seat 76, and a coil spring 64 provided between the pressing member 63 and the control valve 70.
  • the advancing/retreating unit 61 also has a solenoid case 60C that houses and supports the components that make up the advancing/retreating unit 61.
  • the solenoid portion 62 has a plunger 65 that moves back and forth along the second axial direction, and when the electromagnet is energized, the plunger 65 is pushed toward the first side. When the solenoid portion 62 is de-energized, the plunger 65 is pulled back toward the second side by the coil spring 64.
  • the pressing member 63 has a cylindrical portion 631, a bottom portion 632 covering the opening on the first side of the cylindrical portion 631, and a flange portion 633 provided at the end portion on the second side of the cylindrical portion 631 and protruding outwardly around the entire circumference.
  • the coil spring 64 is a compression coil spring that contacts the control valve 70 on a first side and contacts the pressing member 63 on a second side.
  • the coil spring 64 applies forces to the pressing member 63 and the control valve 70 in directions that move the pressing member 63 and the control valve 70 away from each other.
  • another member such as an elastic ring, may be used as long as it exhibits the same function.
  • the cap portion 67 is a part having a first opening 67H1 formed on the first side and a second opening 67H2 formed on the second side, and is generally cylindrical.
  • the inner diameter of the first opening 67H1 is larger than the inner diameter of the second opening 67H2.
  • a plurality of inner diameter portions each having a different inner diameter are formed inside the cap portion 67.
  • the inner diameter portion provided on the first side is formed so as to have a larger inner diameter than the inner diameter portion provided on the second side.
  • the cap portion 67 has a first inner diameter portion 671 on the first side of the second opening 67H2, a second inner diameter portion 672 on the first side of the first inner diameter portion 671, and a third inner diameter portion 673 on the first side of the second inner diameter portion 672.
  • the cap portion 67 accommodates the main valve portion 50, the damping force adjustment portion 60, and the communication portion 80 inside. More specifically, the cap portion 67 accommodates the main valve 51 and the control valve 70 of the main valve portion 50. A part of the cap portion 67, together with the back pressure generating mechanism 68 and the control seat 76, forms a back pressure chamber 68P that applies oil pressure (hereinafter sometimes referred to as "back pressure") from the second side, which is the opposite side to the main valve seat 52, to the main valve 51.
  • back pressure oil pressure
  • the cap portion 67 is fixed by being sandwiched between the solenoid case 60C and the connection flow passage portion 90.
  • the cap portion 67 also forms a cap flow passage 67R, through which oil flows, between the cap portion 67 and the solenoid case 60C.
  • the cap flow passage 67R is connected to the second opening 67H2 and also to the housing internal flow passage 111, which will be described later.
  • the plunger 65 is provided to pass through the second opening 67H2 of the cap portion 67. Furthermore, inside the cap portion 67, the pressing member 63 advances and retreats with respect to the second opening 67H2.
  • a groove 675 is formed on the edge of the first side of the second opening 67H2 of the cap portion 67.
  • the groove 675 forms a cap orifice flow path 67R2 (see FIG. 9 ) through which oil flows between the flange portion 633 of the pressing member 63 and the cap portion 67 in a state in which the pressing member 63 moves to the second side and contacts the cap portion 67.
  • the cap orifice flow path 67R2 communicates with the cap flow path 67R via the second opening 67H2.
  • the cross-sectional area of the oil flow path in the groove 675 is set so that the pressure in the back pressure chamber 68P is increased to a certain level or higher when the solenoid portion 62 is in a non-energized state. Furthermore, the cross-sectional area of the oil flow path in the groove 675 is set so that when the solenoid portion 62 is in a non-energized state, the main valve 51 opens the main flow path 53 and oil flows into the groove 675 to an extent that oil flows.
  • the configuration for causing oil to flow between the cap portion 67 and the pressing member 63 when the solenoid portion 62 described above is in a non-energized state is not limited to the groove portion 675.
  • a groove may be provided in the pressing member 63 to allow oil to flow between the pressing member 63 and the cap portion 67 when the pressing member 63 is in contact with the cap portion 67.
  • a groove portion 675 may be formed in the cap portion 67 and a groove may be provided in the pressing member 63.
  • the configuration for causing oil to flow between the cap portion 67 and the pressing member 63 when the pressing member 63 is in contact with the cap portion 67 is not limited to a groove portion and may be a through hole.
  • the back pressure generating mechanism 68 includes a partition member 681 provided on the opposite side of the main valve seat 52 with respect to the main valve 51, i.e., on the second side, and a partition member 682 between the cap portion 67 and the partition member 681.
  • the back pressure generating mechanism 68 further includes a return spring 683 that applies a force to the partition member 681 to press the partition member 681 against the main valve 51, and a pressure between the return spring 683 and the main valve 51. and a spacer member 684 interposed therebetween.
  • the bulkhead member 681 is generally formed in a substantially annular shape.
  • the bulkhead member 681 is movable in the second axial direction. For example, when the main valve 51 deforms toward the second side, the bulkhead member 681 moves toward the second side. Also, when the main valve 51 deforms toward the first side, the bulkhead member 681 moves toward the first side.
  • the partition member 681 has a main valve contact portion 681V that contacts the main valve 51, and a seal contact portion 681S where the seal member 682 is provided.
  • the main valve contact portion 681V is provided on the first side of the partition member 681.
  • the main valve contact portion 681V is formed so that its width gradually narrows from the second side to the first side. This main valve contact portion 681V contacts the main valve 51 in an annular shape.
  • the partition member 681 constitutes one of the components that form the back pressure chamber 68P.
  • the back pressure chamber 68P is a chamber into which oil flows and exerts a hydraulic pressure on the main valve 51 in accordance with the flow of oil.
  • the back pressure chamber 68P exerts a force on the main valve 51 to press the main valve 51 against the main valve seat 52.
  • the seal member 682 is formed in an annular shape.
  • the seal member 682 may be made of an elastically deformable resin material such as engineering plastic or rubber.
  • the seal member 682 seals between the partition member 681 and the third inner diameter portion 673 of the cap portion 67. More specifically, the outer circumferential surface 682G of the seal member 682 contacts the inner periphery of the third inner diameter portion 673 of the cap portion 67. Also, the first end surface 682T of the seal member 682 contacts the partition member 681. In this way, the seal member 682 prevents oil in the back pressure chamber 68P from flowing out of the back pressure chamber 68P through between the partition member 681 and the cap portion 67.
  • the return spring 683 has an annular portion 683R formed in an annular shape and a plurality of arm portions 683A protruding from the annular portion 683R toward the second outside.
  • the return spring 683 can be made of an elastic material such as a metal.
  • the return spring 683 has the connecting portion 80 penetrating the annular portion 683R, and the annular portion 683R is sandwiched in the second axial direction by a plurality of spacer members 684.
  • the arm portion 683A of the return spring 683 contacts the seal member 682.
  • the position where the annular portion 683R of the return spring 683 is fixed by the spacer member 684 and the position where the arm portion 683A contacts the seal member 682 differ in the second axial direction.
  • the arm portion 683A is inclined with respect to the second axial direction. Furthermore, the arm portion 683A contacts the second inner corner on the second side of the seal member 682. As a result, the arm portion 683A applies to the seal member 682 a spring force component along the second axial direction and a spring force component along the second radial direction.
  • the arm portion 683A of the return spring 683 is also in contact with the partition member 681.
  • the return spring 683 applies a spring force component along the second axial direction and a spring force component along the second radial direction to the partition member 681.
  • the control valve 70 has a cylindrical portion 701 and a conical portion 702 that covers an opening on the first side of the cylindrical portion 701 and protrudes to the first side.
  • the control valve 70 also has a protruding portion 71 that protrudes around the entire circumference to the second outside at the end of the cylindrical portion 701 on the first side.
  • the control valve 70 also has a flat surface 703 perpendicular to the second axial direction at the end of the conical portion 702 on the second side and at a second inner position.
  • the control valve 70 also has a protruding portion 706 that protrudes to the second outside at the center of the conical portion 702 in the second axial direction.
  • the protruding portion 706 has a flat surface 707 perpendicular to the second axial direction.
  • the outer diameter of the cylindrical portion 701 is equal to or greater than the outer diameter of the flange portion 633 of the pressing member 63, and the inner diameter of the cylindrical portion 701 is smaller than the outer diameter of the flange portion 633. As a result, the second end surface of the cylindrical portion 701 comes into contact with the flange portion 633 of the pressing member 63.
  • the inner diameter of the cylindrical portion 701 is larger than the outer diameter of the cylindrical portion 631 of the pressing member 63.
  • the cylindrical portion 631 and the bottom portion 632 of the pressing member 63 are accommodated in the second inner side of the control valve 70, with the second end face of the cylindrical portion 701 in contact with the flange portion 633 of the pressing member 63.
  • the coil spring 64 (an example of an elastic member) is disposed inside the space 704 (an example of a spring space) formed between the cylindrical portion 701 of the control valve 70 and the cylindrical portion 631 of the pressing member 63.
  • the first end of the coil spring 64 is supported by the flat surface 703 of the control valve 70, and the second end of the coil spring 64 is supported by the flange portion 633 of the pressing member 63.
  • the coil spring 64 is a member that acts at both ends, and because it does not have a fixed end, all of the thrust of the solenoid part 62 applied to the coil spring 64 is used to deform the coil spring 64 itself, resulting in excellent thrust efficiency.
  • the restricting member 72 has an annular portion 721 formed in an annular shape, and a plurality of arm portions 722 protruding from the annular portion 721 toward the second inner side.
  • Four of the arm portions 722 are provided at equal intervals in the circumferential direction of the annular portion 721.
  • the circumferential size of the arm portions 722 gradually decreases from the second outer side to the second inner side.
  • the diameter of an imaginary circle formed by the tips of the second inner sides of the arm portions 722 is larger than the diameter of the outer circumferential surface of the cylindrical portion 701 of the control valve 70 and smaller than the diameter of the outer circumferential surface of the protruding portion 71.
  • the first spacer member 73A, the second spacer member 73B, and the third spacer member 73C are annular members.
  • the outer diameters of the first spacer member 73A, the second spacer member 73B, and the third spacer member 73C are larger than the inner diameter of the first inner diameter portion 671 of the cap portion 67, and smaller than the inner diameter of the second inner diameter portion 672.
  • the inner diameters of the first spacer member 73A, the second spacer member 73B, and the third spacer member 73C are larger than the inner diameter of the first inner diameter portion 671 of the cap portion 67, and smaller than the inner diameter of the second inner diameter portion 672.
  • the first spacer member 73A and the second spacer member 73B are disposed between the first end face of the first inner diameter portion 671 of the cap portion 67 and the biasing member 75, and determine the position of the regulating member 72 in the second axial direction. More specifically, the regulating member 72 is located on the second side of the protruding portion 71 of the control valve 70, and regulates the control valve 70 from moving to the second side.
  • the position of the regulating member 72 in the second axis direction by adjusting the size (hereinafter sometimes referred to as "thickness") of the first spacer member 73A and the second spacer member 73B in the second axis direction.
  • the third spacer member 73C is disposed between the biasing member 75 and the control sheet 76 to determine the position of the biasing member 75 in the second axial direction.
  • the position of the biasing member 75 in the second axial direction can be adjusted by adjusting the size of the third spacer member 73C in the second axial direction (hereinafter, sometimes referred to as "thickness"). For example, if it is desired to set the position of the biasing member 75 in the second axial direction to the first side of FIG. 4, the thickness of the third spacer member 73C should be made thinner than the thickness shown in FIG. 4, and the thickness of the first spacer member 73A should be made thicker than the thickness shown in FIG. 4.
  • the thickness of the third spacer member 73C should be made thicker than the thickness shown in FIG. 4, and the thickness of the first spacer member 73A should be made thinner than the thickness shown in FIG. 4.
  • the biasing member 75 is an annular leaf spring that applies a force to the control valve 70 in a direction against the thrust of the solenoid unit 62 and the spring force of the coil spring 64, and is set to a spring constant higher than that of the coil spring 64.
  • the biasing member 75 has an annular portion 751 that is formed in an annular shape and functions as a fixed end, and a plurality of arm portions 752 that protrude from the annular portion 751 toward the second inner side and function as an acting end.
  • the shape of the biasing member 75 is not limited to this, and the shape is not particularly limited as long as it has a fixed end and an acting end that acts on the control valve 70.
  • the plurality of arm portions 752 are provided in three at equal intervals in the circumferential direction of the annular portion 751.
  • the number of the arm portions 752 is not limited to three, and may be two or less, or four or more.
  • the shapes of the plurality of arm portions 752 may all be the same, or may be different from each other.
  • the circumferential sizes of the plurality of arm portions 752 may be different from each other.
  • the biasing member 75 does not have to be a leaf spring, and may be an elastic member such as a coil spring interposed between the control valve 70 and the control seat 76 .
  • the control sheet 76 has an outer sheet portion 761 that holds the restricting member 72, the biasing member 75, the first spacer member 73A, the second spacer member 73B, and the third spacer member 73C together with the cap portion 67, and a recess 762 that is provided on the second inner side and recessed from the second side surface of the outer sheet portion 761.
  • a back pressure flow path 77 that is a hole penetrating in the second axial direction and forms an oil flow path for adjusting the oil pressure in the back pressure chamber 68P is formed in the second inner part of the recess 762.
  • the control sheet 76 has a round 77R around the back pressure flow path 77 that protrudes further to the second side than the bottom of the recess 762.
  • control sheet 76 has a communication chamber 78 that is provided on the first side of the back pressure passage 77 and communicates with the back pressure passage 77.
  • a plurality of back pressure communication passages 79 are formed in the circumferential direction around the communication chamber 78 in the control sheet 76, which are holes that penetrate in the second radial direction and communicate the communication chamber 78 with the back pressure chamber 68P.
  • the control sheet 76 configured as above is provided in a discharge flow passage, which will be described later, together with the control valve 70, and constitutes a valve 700 that varies the area of the discharge flow passage.
  • the throttle member 83 is fitted into the control sheet 76 on the first side of the communication chamber 78, and has a cylindrical portion 831 and a blocking portion 832 that blocks an opening on the second side of the cylindrical portion 831.
  • a back pressure orifice flow path 84 that connects an inflow flow path 81 (described later) and the communication chamber 78 is formed in the blocking portion 832.
  • the back pressure orifice flow path 84 is formed so that the cross-sectional area of the oil flow path is smaller than the back pressure communication passage 79 and the back pressure flow path 77.
  • the back pressure orifice flow path 84 makes it difficult for the oil in the back pressure chamber 68P to return to the inflow flow path 81.
  • the communication portion 80 of the first embodiment has an inflow passage 81 into which the oil flows from the communication passage L, and a connection portion 89 that connects to the control sheet 76 .
  • the inner diameter of the connection portion 89 is approximately equal to the outer diameter of the first side of the control sheet 76.
  • the end of the first side of the control sheet 76 is inserted into the connection portion 89.
  • the communication portion 80 may be configured to be inserted into the inside of the control sheet 76.
  • connection flow passage portion 90 has an inner flow passage 91 provided on the second inner side, and an outer flow passage 92 provided on the second outer side.
  • the inner flow passage 91 communicates with the outer cylinder opening 12H on a first side, and communicates with the inlet flow passage 81 of the communication portion 80 and the main flow passage 53 of the main valve seat 52 on a second side.
  • a plurality of outer flow passages 92 are provided in the circumferential direction. Each outer flow passage 92 communicates with the case opening 13H on a first side and communicates with the housing internal flow passage 111 on a second side.
  • the outer housing 100C is a substantially cylindrical member.
  • a first side of the outer housing 100C is fixed to the damper case 13 by, for example, welding.
  • the outer housing 100C defines, on a second outer side of the main valve portion 50 and the damping force adjusting portion 60, an inner housing flow passage 111 which is an oil flow passage within the outer housing 100C.
  • the oil flowing out from the second opening 67H2 of the cap portion 67 and the oil flowing out from the main flow path 53 of the main valve seat 52 when the main valve 51 is opened flow into the housing inner flow path 111.
  • the pressing force of the pressing member 63 is maximized.
  • the control valve 70 is pressed most strongly against the back pressure flow path 77 of the control seat 76, and the back pressure flow path 77 is closed (see FIG. 7).
  • a state is created in which the pressing force of the pressing member 63 is at its smallest.
  • the control valve 70 is separated from the back pressure flow path 77, and the back pressure flow path 77 is opened (see FIG. 5).
  • the pressing force of the pressing member 63 is set to a state between the smallest and largest.
  • the control valve 70 is farther away from the back pressure flow path 77 than when the pressing force is the largest, and closer to the back pressure flow path 77 than when the pressing force is the smallest.
  • the oil then flows into the damping force generating device 100 through the communication passage L and the outer cylinder opening 12H.
  • the oil first flows into the inner flow passage 91 of the connection flow passage portion 90. After that, in the damping force generating device 100, a damping force is generated in the main valve 51 or the control valve 70. The flow of oil at this time will be explained in detail later.
  • the oil that has flowed into the main valve 51 or the control valve 70 flows out into the housing internal flow path 111.
  • the oil then passes through the outer flow path 92 of the connection flow path portion 90 and flows into the reservoir chamber R from the case opening 13H.
  • the pressure in the first oil chamber Y1 is relatively low compared to the pressure in the reservoir chamber R. Therefore, the oil in the reservoir chamber R flows through the bottom portion 40 into the first oil chamber Y1.
  • the operation of the hydraulic shock absorber 1 during the compression stroke will be described.
  • the rod 20 moves relative to one side with respect to the cylinder 11.
  • the piston valve 32 that closes the piston oil passage port 311 opens due to the pressure difference between the first oil chamber Y1 and the second oil chamber Y2.
  • the oil in the first oil chamber Y1 flows out through the piston oil passage port 311 to the second oil chamber Y2.
  • the rod 20 is disposed in the second oil chamber Y2. Therefore, the oil flowing from the first oil chamber Y1 to the second oil chamber Y2 is in excess by the volume of the rod 20. Therefore, an amount of oil equivalent to the volume of the rod 20 flows out from the communication hole 11H to the communication passage L.
  • the oil flows into the damping force generating device 100 through the communication passage L and the outer cylinder opening 12H.
  • the flow of oil in the damping force generating device 100 is the same as the flow of oil during the extension stroke described above. That is, in the hydraulic shock absorber 1 of the first embodiment, the direction in which the oil flows in the damping force generating device 100 is the same during both the compression stroke and the extension stroke.
  • the damping force generating device 100 generates a damping force during both the compression stroke and the extension stroke.
  • FIG. 5 is a diagram showing an example of the oil flow when the piston portion 30 (see FIG. 1) moves at a low speed with the pressing force of the pressing member 63 at its smallest. 5, when the moving speed of the piston portion 30 is low, the oil that has flowed into the inner flow passage 91 flows into the inlet flow passage 81 and the main flow passage 53. Since the moving speed of the piston portion 30 is low, no oil flow that opens the main valve 51 occurs in the main flow passage 53.
  • the oil that has flowed into the inlet passage 81 flows through the back pressure orifice passage 84, the communication chamber 78, the back pressure passage 77, the second opening 67H2, and the cap passage 67R in that order, as shown by the arrows in Figure 5.
  • the oil then flows out from the housing internal passage 111 into the reservoir chamber R.
  • the damping force is generated by the flow of oil being restricted by the gap between the round 77R and the control valve 70.
  • FIG. 6 is a diagram showing an example of the oil flow when the piston portion 30 (see FIG. 1) moves at a high speed with the pressing force of the pressing member 63 at its smallest. 6, when the moving speed of the piston portion 30 is high, the oil that has flowed into the inner flow passage 91 flows into the inlet flow passage 81 and the main flow passage 53. The oil that has flowed into the main flow passage 53 opens the main valve 51 and flows out into the reservoir chamber R.
  • the oil that flows into the inlet passage 81 flows to the housing inner passage 111 while generating a pressure difference due to the flow rate being restricted by the gap between the round 77R and the control valve 70, just as when the moving speed is low, and then flows out into the reservoir chamber R.
  • the damping force is mainly generated by the flow of oil in the main flow passage 53 of the main valve seat 52.
  • the oil that has flowed into the inlet passage 81 transmits pressure to the backpressure chamber 68P through the backpressure orifice passage 84 and the backpressure communication passage 79.
  • the backpressure passage 77 that connects to the backpressure chamber 68P is opened by the control valve 70. Therefore, the pressure in the backpressure chamber 68P is lower than when the control valve 70 is pressed against the backpressure passage 77.
  • the main valve 51 which is in contact with the backpressure generating mechanism 68, is more likely to open the main passage 53. Therefore, when the pressing force of the pressing member 63 is at its smallest, the damping force generated by the flow of oil in the main passage 53 that opens the main valve 51 is lower than when the pressing force of the pressing member 63 is at its largest.
  • FIG. 7 is a diagram showing an example of the oil flow when the piston portion 30 (see FIG. 1) moves at a low speed in a state in which the pressing force of the pressing member 63 is at its largest. ((at low speed)) 7 when the moving speed of the piston portion 30 is low, the oil that has flowed into the inner flow passage 91 flows into the inlet flow passage 81 and the main flow passage 53. Since the moving speed of the piston portion 30 is low, the main valve 51 is opened and no flow of oil flows through the main flow passage 53. On the other hand, the oil that has flowed into the inlet flow passage 81 flows into the back pressure orifice flow passage 84 and the communication chamber 78 as shown by the arrows in Fig. 7.
  • the oil flows into the back pressure flow passage 77 while opening the control valve 70.
  • the oil further flows into the second opening 67H2 and the cap flow passage 67R in this order.
  • the oil then flows out from the housing internal flow passage 111 into the reservoir chamber R.
  • the damping force is generated by the oil flowing through the back pressure flow path 77 while the control valve 70 is open.
  • the damping force generated when the oil flows through the back pressure flow path 77 is higher than when the control valve 70 is located away from the back pressure flow path 77.
  • FIG. 8 is a diagram showing an example of the oil flow when the piston portion 30 (see FIG. 1) moves at a high speed in a state in which the pressing force of the pressing member 63 is maximized. 8, when the moving speed of the piston portion 30 is high, the oil that has flowed into the inner flow passage 91 flows into the inlet flow passage 81 and the main flow passage 53. The oil that has flowed into the main flow passage 53 opens the main valve 51 and flows out into the reservoir chamber R.
  • the oil that flows into the inlet passage 81 flows to the housing inner passage 111 while generating a pressure difference due to the flow rate being restricted by the gap between the round 77R and the control valve 70, just as when the pressing force of the pressing member 63 is at its smallest, and then flows out into the reservoir chamber R.
  • the damping force is generated mainly by the flow of oil in the main flow passage 53 of the main valve seat 52 .
  • the oil that has flowed into the inlet passage 81 transmits pressure to the backpressure chamber 68P through the backpressure orifice passage 84 and the backpressure communication passage 79.
  • the backpressure passage 77 that connects to the backpressure chamber 68P is held down by the control valve 70. This makes the pressure in the backpressure chamber 68P higher than when the backpressure passage 77 is open. This makes it difficult for the main valve 51, which is in contact with the backpressure generating mechanism 68, to open the main passage 53. Therefore, when the pressing force of the pressing member 63 is at its largest, the damping force generated by the flow of oil in the main passage 53 that opens the main valve 51 is higher than when the pressing force of the pressing member 63 is at its smallest.
  • the hydraulic shock absorber 1 adjusts the damping force at both low speeds and high speeds by operating the pressing member 63.
  • the hydraulic shock absorber 1 changes the pressing force of the control valve 70 against the control sheet 76 using the pressing member 63 to adjust the flow area of the back pressure flow path 77, which is the oil flow path at low speeds, and the flow area of the back pressure flow path 77, which adjusts the pressure of the back pressure chamber 68P, which is related to the flow area of the oil flow path at high speeds.
  • the pressing force of the pressing member 63 can be set arbitrarily within an adjustable range according to the amount of current to the solenoid section 62, in other words, the thrust of the solenoid section 62.
  • the damping force adjustment section 60 also allows multiple stages of adjustment of the damping force at low speeds and the damping force at high speeds.
  • FIG. 9 is a diagram showing an example of the flow of oil when the solenoid portion 62 is in a non-energized state and the moving speed of the piston portion 30 (see FIG. 1) is low.
  • FIG. 10 is a diagram showing an example of the flow of oil when the solenoid portion 62 is in a non-energized state and the moving speed of the piston portion 30 is high.
  • the oil that has flowed into the inlet flow passage 81 transmits pressure to the back pressure chamber 68P through the back pressure orifice flow passage 84 and the back pressure communication passage 79.
  • the back pressure chamber 68P is connected to the housing internal flow passage 111 via the back pressure flow passage 77.
  • the flow of oil between the back pressure chamber 68P and the housing internal flow passage 111 must pass through the cap orifice flow passage 67R2.
  • the cap orifice flow passage 67R2 restricts the flow of oil, thereby suppressing the outflow of oil from the back pressure chamber 68P, and the pressure in the back pressure chamber 68P is maintained in a state higher than the state in which the pressing force of the pressing member 63 is the smallest, as shown in FIG. 6.
  • the main valve 51 which is in contact with the back pressure generating mechanism 68, is relatively difficult to open the main flow passage 53. Therefore, when the solenoid unit 62 is in a non-energized state, the damping force generated by the flow of oil in the main flow passage 53 that opens the main valve 51 is relatively high.
  • both the damping force at low speeds and the damping force at high speeds are made relatively high.
  • the restricting member 72 restricts the movement of the control valve 70 to the second side.
  • the protrusion 71 of the control valve 70 comes into contact with the restricting member 72, and the control valve 70 receives a force from the restricting member 72 in the direction of the first side, so that the movement to the second side is restricted.
  • the cylindrical portion 631 and bottom portion 632 of the pressing member 63 are disposed on the second inner side of the cylindrical portion 701 and conical portion 702 of the control valve 70, and the diameter of the outer periphery of the flange portion 633 of the pressing member 63 is equal to or smaller than the outer diameter of the cylindrical portion 701 of the control valve 70, so that the pressing member 63 is less likely to be subjected to the force of the oil flowing through the back pressure flow path 77 toward the second opening 67H2. As a result, the pressing member 63 is also prevented from moving toward the second side, so that it tends to remain in a stable normal operating position, and is less likely to be pressed against the cap portion 67, which is the operating position during abnormal conditions.
  • the damping force generating device 100 can prevent abnormal operation even though the mechanism is capable of normal operation, and can perform abnormal operation when an abnormality occurs in the mechanism. Furthermore, even if the flow path cross-sectional area of the cap orifice flow path 67R2 is changed to adjust the damping force generated during abnormality, this change can be prevented from affecting the damping force during normal operation.
  • the damping force generating device 100 includes a main valve 51 (an example of a main valve) that restricts the flow of oil (an example of a fluid) to generate a damping force, a back pressure chamber 68P that applies pressure to the main valve 51 in a valve closing direction, and a flow path (hereinafter sometimes referred to as a "discharge flow path") that allows oil to flow out from the back pressure chamber 68P.
  • the discharge flow path is a flow path that passes through the back pressure communication passage 79, the communication chamber 78, the back pressure flow path 77, the second opening 67H2, the cap flow path 67R, and the housing inner flow path 111.
  • the damping force generating device 100 also includes a valve 700 that is provided on the discharge flow path and has a control valve 70 (an example of a valve body) that varies the area of the discharge flow path, and a control seat 76 (an example of a valve seat) on which the control valve 70 can be seated.
  • the damping force generating device 100 also includes a pressing member 63 that can contact the side of the control valve 70 opposite to the side facing the control seat 76 and can apply a pressing force in a direction to press the control valve 70 against the control seat 76.
  • the damping force generating device 100 also includes a solenoid unit 62 as an example of an actuator unit that can generate a thrust to position the control valve 70 between the first position and the second position according to a supplied current.
  • the first position can be exemplified as the position shown in FIG. 7 where the pressing member 63 is closest to the control seat 76.
  • the second position can be exemplified as the position shown in FIG. 9 where the pressing member 63 is farthest from the control seat 76. If the damping force generating device 100 does not include the regulating member 72, when the pressure of the oil passing through the back pressure flow path 77 is high, the control valve 70 will be in a state where the end face of the second side of the cylindrical portion 701 is in contact with the flange portion 633 of the pressing member 63 even when the pressing member 63 is located at the second position shown in FIG. 9. In this state, that is, when the pressing member 63 is located at the second position shown in Fig.
  • the damping force generating device 100 also includes a restricting member 72 that restricts the movement of the control valve 70 so that the pressing member 63 does not reach the second position even if the control valve 70 receives the pressure of the oil passing through the discharge flow path and moves in a direction to move the pressing member 63 toward the second position.
  • the damping force generating device 100 has a housing that is formed in a cylindrical shape to accommodate the pressing member 63 and the control valve 70 and has a protrusion formed on its inner circumferential surface.
  • the cap portion 67, the first spacer member 73A, and the second spacer member 73B are formed into a cylindrical shape that accommodates the pressing member 63 and the control valve 70, and the regulating member 72 protrudes from the inner circumferential surfaces of the first spacer member 73A and the second spacer member 73B to the second inner side.
  • the regulating member 72 and the protruding portion 71 of the control valve 70 function as an example of a regulating portion that regulates the movement of the control valve 70 in the direction toward the second position at a third position between the first position and the second position.
  • the third position can be exemplified as the position shown in FIG. 9, where the protruding portion 71 of the control valve 70 abuts against the regulating member 72.
  • the damping force generating device 100 even if the pressure of the oil passing through the back pressure flow path 77 is high during normal operation and the control valve 70 moves to the second side to move the pressing member 63 to the second side, the movement of the control valve 70 is restricted by the restricting member 72, so that the pressing member 63 does not reach the farthest position from the control seat 76.
  • the pressing member 63 reaches the farthest position from the control seat 76 during abnormal operation when the current supplied to the solenoid section 62 is zero, in other words, when the solenoid section 62 is in a non-energized state and the thrust of the solenoid section 62 is zero. Therefore, according to the damping force generating device 100, even if the pressure of the oil passing through the back pressure flow path 77 is high during normal operation when the mechanism is capable of normal operation, operation during abnormal operation is suppressed.
  • the damping force generating device 100 also includes a coil spring 64 (an example of a moving member) that generates a force on the pressing member 63 in a direction away from the control valve 70 and is capable of moving the pressing member 63 to a second position when the movement of the control valve 70 is restricted by the restricting member 72.
  • a coil spring 64 an example of a moving member
  • the coil spring 64 is an example of an elastic member disposed between the control valve 70 and the pressing member 63. Therefore, the damping force adjusting portion 60 can have a simple configuration.
  • the pressing member 63 is fixed to a plunger 65 (an example of a driving member) of the solenoid portion 62. Therefore, for example, in the event of an abnormality in which the thrust of the solenoid portion 62 becomes zero, it becomes possible to press the pressing member 63 against the cap portion 67 with high accuracy, and it is possible to adjust the damping force with high accuracy according to the current supplied to the solenoid portion 62.
  • the pressing member 63 has a cylindrical portion 631 (an example of a tubular portion), a bottom portion 632 that covers the opening of the cylindrical portion 631 on the control sheet 76 side, and a flange portion 633 (an example of an applying portion) that protrudes from the outer circumferential surface of the cylindrical portion 631 to the second outside (an example of the outside) and applies a pressing force to the control valve 70.
  • the control valve 70 accommodates the cylindrical portion 631 and the bottom portion 632 of the pressing member 63. Therefore, the pressing member 63 is less likely to be subjected to the pressure of the oil passing through the back pressure flow path 77.
  • the damping force adjustment unit 60 which is an example of a damping force adjustment device, is provided on a flow path through which a fluid flows and includes a control valve 70 that varies the area of the flow path, and a case member that houses the control valve 70 and has a control sheet 76 (an example of a valve seat) in which a back pressure flow path 77 (an example of a through hole) that can be closed by the control valve 70 is formed.
  • the case member is composed of the control sheet 76, a cap portion 67, a first spacer member 73A, a second spacer member 73B, a third spacer member 73C, and the like.
  • the damping force adjustment unit 60 also includes a solenoid portion 62 that applies a thrust to a pressing member 63 (an example of a movable member) that can contact the side of the control valve 70 opposite to the side facing the control sheet 76, and a coil spring 64 (an example of a first spring member) that has one end in contact with the control valve 70 and the other end in contact with the pressing member 63.
  • the damping force adjustment unit 60 also includes a plate-shaped biasing member 75 (an example of a second spring member) that has one end in contact with the control valve 70 and the other end fixed to a case member (e.g., between the first spacer member 73A and the third spacer member 73C).
  • the pressing member 63 to which the thrust of the solenoid unit 62 is applied is placed against the control valve 70, and in the region from when the pressing member 63 and the control valve 70 are separated by the action of the coil spring 64 until they come into contact, the biasing member 75 is harder than the coil spring 64, so the second axial position of the control valve 70 does not change, and the solenoid thrust is used only to deform the coil spring 64. In other words, the solenoid thrust is not used for anything else, and there is little waste in the thrust efficiency of the solenoid unit 62.
  • the pressing member 63 also has a flange portion 633 (an example of a restricting portion) that restricts the flow path that flows from the second opening 67H2, the cap flow path 67R, and the housing internal flow path 111, which is the flow path downstream of the control valve 70, to the reservoir chamber R, and the other end of the coil spring 64 contacts the flange portion 633. Therefore, for example, in the event of an abnormality, the pressing member 63 can be pressed against the cap portion 67 with high accuracy.
  • FIG. 11 is a diagram showing an example of a schematic configuration of a damping force generating device 200 according to the second embodiment.
  • the damping force generator 200 according to the second embodiment differs from the damping force generator 100 according to the first embodiment in that it has a control valve 270 corresponding to the control valve 70 and a restricting member 272 corresponding to the restricting member 72.
  • the differences from the first embodiment will be described below.
  • the same reference numerals are used for the same components in the first and second embodiments, and detailed descriptions thereof will be omitted.
  • the restricting member 272 differs from the restricting member 72 in that it does not have an arm portion 722, but only a portion corresponding to the annular portion 721.
  • the inner diameter of the restricting member 272 is smaller than the inner diameters of the first spacer member 73A and the second spacer member 73B, and the restricting member 272 protrudes a second inward beyond the first spacer member 73A and the second spacer member 73B.
  • the control valve 270 differs from the control valve 70 in that the protrusion 271 corresponds to the protrusion 71.
  • the protrusion 271 is not formed around the entire circumference, but is formed in multiple (e.g., four) around the cylindrical portion 701.
  • the multiple protrusions 271 are provided at equal intervals in the circumferential direction of the cylindrical portion 701.
  • the circumferential size of the protrusion 271 gradually decreases from the second inner side to the second outer side.
  • the diameter of the imaginary circle formed by the second outer tips of the multiple protrusions 271 is larger than the inner diameter of the regulating member 272 and smaller than the inner diameters of the first spacer member 73A and the second spacer member 73B.
  • the damping force generating device 200 is provided on the back pressure flow path 77 and includes a valve 700 having a conical portion 702 (an example of a valve body) of the control valve 270 that varies the area of the back pressure flow path 77 and a control seat 76 (an example of a valve seat) on which the control valve 70 can be seated.
  • the damping force generating device 200 also includes a protrusion 271 that restricts the movement of the control valve 270 so that the pressing member 63 does not reach the second position even if the control valve 270 receives pressure from the oil passing through the back pressure flow path 77 and moves in a direction that moves the pressing member 63 toward the second position.
  • the damping force generating device 200 has a housing that is formed in a cylindrical shape to accommodate the pressing member 63 and the control valve 270 and has a protrusion formed on its inner surface.
  • the cap portion 67, the first spacer member 73A, the second spacer member 73B, etc. are formed into a cylindrical shape that accommodates the pressing member 63 and the control valve 270, and the regulating member 272 protrudes from the inner circumferential surface of the first spacer member 73A and the second spacer member 73B to the second inner side.
  • the regulating member 272 and the protruding portion 271 of the control valve 270 function as an example of a regulating portion that regulates the movement of the conical portion 702 of the control valve 270 in the direction toward the second position at a third position between the first position and the second position. According to the damping force generating device 200 configured in this way, even if the pressure of the oil passing through the back pressure flow path 77 is high during normal times when the mechanism can operate normally, abnormal operation is suppressed.
  • FIG. 12 is a diagram showing an example of a schematic configuration of a damping force generating device 400 according to the third embodiment.
  • FIG. 13 is a diagram showing an example of a partial cross section of a damping force generating device 400 according to the third embodiment.
  • the damping force generator 400 according to the third embodiment differs from the damping force generator 100 according to the first embodiment in that it has a damping force adjusting unit 460 that corresponds to the damping force adjusting unit 60.
  • the differences from the first embodiment will be described below.
  • the same reference numerals are used for the same parts in the first and third embodiments, and detailed descriptions thereof will be omitted.
  • the damping force adjustment section 460 according to the third embodiment differs from the damping force adjustment section 60 according to the first embodiment in that it includes a control sheet 476 that corresponds to the control sheet 76. Also, the damping force adjustment section 460 differs from the damping force adjustment section 60 in that it does not include a third spacer member 73C, and the biasing member 75 is fixed by a first spacer member 73A and a control sheet 476.
  • the control seat 476 is formed with a first recess 481 that is recessed annularly on the first side from the fixed portion 471 between the fixed portion 471, which is a portion that fixes the biasing member 75 in the second radial direction, and the round 77R on which the control valve 70 can be seated, and a second recess 482 that is recessed annularly on the first side at a second inner side from the first recess 481.
  • a first edge portion 491 is formed on the edge of the opening on the second side of the first recess 481, and a second edge portion 492 is formed on the edge of the opening on the second side of the second recess 482.
  • the first edge portion 491 is a portion located slightly on the second inner side from the fixed portion 471, and the second edge portion 492 is a portion connecting the first recess 481 and the second recess 482.
  • FIG. 14 is a diagram showing an example of a state in which the biasing member 75 is in contact with the first edge portion 491 and is not in contact with the second edge portion 492.
  • FIG. 15 is a diagram showing an example of a state in which the biasing member 75 is in contact with the first edge portion 491 and the second edge portion 492.
  • FIG. 16 is a diagram showing an example of a state in which the control valve 70 is seated on the round 77R.
  • the control valve 70 When the current supplied to the coil of the solenoid unit 62 is a first current, which is a low current, the control valve 70 receives a force from the biasing member 75 toward the second side, and the spring force of the coil spring 64, the spring force of the biasing member 75, and the solenoid thrust are in balance, as shown in Fig. 13. Note that, as described above, the present invention is not limited to the third embodiment, and when the current supplied to the coil of the solenoid unit 62 is between zero and the first current, all of the solenoid thrust is used to deform the coil spring 64, so thrust efficiency is good. In this state, the biasing member 75 does not bend, and the flat surface 707 of the control valve 70 and the biasing member 75 are in surface contact with each other.
  • the biasing member 75 When the current supplied to the solenoid portion 62 becomes a second current greater than the first current, the biasing member 75 is pushed by the control valve 70 and bends so as to come into contact with a first edge portion 491 of the control sheet 476, as shown in FIG. 14 .
  • the biasing member 75 When the current supplied to the solenoid portion 62 becomes a third current which is greater than the second current, as shown in FIG. 15 , the biasing member 75 is pushed by the control valve 70 and bends further, coming into contact with the first edge portion 491 and the second edge portion 492 of the control sheet 476.
  • the biasing member 75 When the current supplied to the solenoid portion 62 becomes a fourth current greater than the third current, the biasing member 75 is pushed by the control valve 70 and bends further, as shown in FIG. 16, so that the control valve 70 seats on the round 77R.
  • the current supplied to the solenoid portion 62 when the biasing member 75 starts to contact the first edge portion 491 is the second current
  • the current supplied to the solenoid portion 62 when the biasing member 75 starts to contact the second edge portion 492 is the third current
  • the current supplied to the solenoid portion 62 when the control valve 70 starts to seat on the round 77R is the fourth current.
  • FIG. 17 is a diagram showing an example of the correlation between the current supplied to the solenoid portion 62 and the thrust force F of the solenoid portion 62 (see FIGS. 14 to 16), the spring constant K of the biasing member 75, and the valve opening amount A of the control valve 70 (see FIGS. 14 and 15).
  • the biasing member 75 bends from the first edge 491 when the current supplied to the solenoid portion 62 is equal to or greater than the second current and less than the third current, and bends from the second edge 492 when the current supplied to the solenoid portion 62 is equal to or greater than the third current. Therefore, as shown in Fig.
  • the spring constant K2 of the biasing member 75 when it bends from the second edge 492 is substantially greater than the spring constant K1 of the biasing member 75 when it bends from the first edge 491. In this way, the spring constant K of the biasing member 75 changes so that it substantially increases as the control valve 70 moves toward the round 77R (an example of a valve seat).
  • the change in the valve opening amount A with respect to an increase in the supply current is smaller than the change in the valve opening amount A with respect to an increase in the supply current with respect to the current supplied to the solenoid portion 62 is equal to or greater than the second current and less than the third current.
  • the sensitivity of the actual position of the control valve 70 with respect to the supply current (in other words, the valve opening amount) can be made lower than when the current supplied to the solenoid portion 62 is equal to or greater than the third current and less than the third current.
  • the biasing member 75 is configured with something other than a leaf spring as described above, it is possible to use, for example, an unequal pitch coil spring, so that the spring constant K can be configured to change so as to substantially increase as the control valve 70 moves toward the round 77R (an example of a valve seat).
  • the control sheet 476 is formed with a first recess 481 that is annularly recessed toward the round 77R on the second inner side of the fixed portion 471 of the biasing member 75, and a second recess 482 that is annularly recessed toward the round 77R on the inner side of the first recess 481.
  • the biasing member 75 does not contact the first edge 491 that is the edge of the first recess 481 and the second edge 492 that is the edge of the second recess 482.
  • the amount of movement of the control valve 70 toward the round 77R is based on the position where the movement of the control valve 70 toward the second side is restricted by the restricting member 72.
  • the first predetermined value is a distance from the reference to a position where the current supplied to the solenoid portion 62 is the first current, and the spring force of the coil spring 64 and the spring force of the biasing member 75 are balanced without the biasing member 75 being substantially deflected.
  • the biasing member 75 contacts the first edge portion 491 and does not contact the second edge portion 492.
  • the biasing member 75 contacts the first edge portion 491 and does not contact the second edge portion 492.
  • the biasing member 75 contacts the first edge portion 491 and the second edge portion 492.
  • the biasing member 75 comes into contact with the first edge portion 491 and the second edge portion 492.
  • the second predetermined value is the distance from the reference to the position of the control valve 70 when the current supplied to the solenoid portion 62 is the third current and the biasing member 75 is at a position where it starts to come into contact with the second edge portion 492.
  • the biasing member 75 has an annular portion 751 as an example of a fixed portion that serves as a fixed end, and arms 752 as an example of multiple acting portions that extend from the annular portion 751 toward the control valve 70 and contact the control valve 70 simultaneously.
  • the biasing member 75 is exerting a force on the control valve 70, it is possible to form a flow path between adjacent arms 752 that extends from the back pressure flow path 77 toward the second opening 67H2.
  • the first recess 481 and the second recess 482 are formed in the control sheet 476, but this is not particularly limited to this aspect.
  • a third spacer member 73C may be provided between the control sheet 476 and the biasing member 75 to form a first recess 481 recessed toward the first side from the contact site with the biasing member 75.
  • the position in the second axial direction of the first edge portion 491, which is the starting point of the deflection of the biasing member 75, is the same around the entire circumference, but is not particularly limited to this.
  • the first recess 481 may be formed so that the position in the second axial direction of the first edge portion 491 varies stepwise or steplessly around the circumference.
  • the first recess 481 may be formed so that the position in the second radial direction of the first edge portion 491 varies stepwise or steplessly around the circumference. This allows the spring constant K1 when the biasing member 75 deflects starting from the first edge portion 491 to be changed stepwise or steplessly.
  • the size of the recess in the second axial direction and the position in the second radial direction of the first recess 481 do not have to be uniform.
  • the position in the second axial direction of the second edge 492, which is the starting point of the deflection of the biasing member 75, is the same around the entire circumference, but is not limited to this.
  • the second recess 482 may be formed so that the position in the second axial direction of the second edge 492 varies stepwise or steplessly around the circumference.
  • the second recess 482 may be formed so that the position in the second radial direction of the second edge 492 varies stepwise or steplessly around the circumference. This allows the spring constant K2 when the biasing member 75 deflects starting from the second edge 492 to be changed stepwise or steplessly.
  • the size of the recess in the second axial direction or the position in the second radial direction of the second recess 482 do not have to be uniform.
  • 1...hydraulic shock absorber 10...cylinder section, 11...cylinder, 20...rod, 30...piston section, 51...main valve (an example of a main valve), 60, 460...damping force adjustment section, 62...solenoid section (an example of an actuator section), 63...pressure member (an example of a movable member), 64...coil spring (an example of a moving member, an example of a first spring member), 65...plunger, 67...cap section (an example of a case member), 68P...back pressure chamber, 70...control valve (an example of a valve body), 72...regulating member (an example of a regulating section), 75...biasing member (an example of a second spring member), 76, 476 ...Control seat (an example of a valve seat, an example of a case member), 77...Back pressure flow path (an example of a flow path), 77R...Round (an example of a valve seat), 100, 200, 400...Damping force generating device, 270...Control valve,

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid-Damping Devices (AREA)
  • Magnetically Actuated Valves (AREA)
PCT/JP2023/018847 2023-05-19 2023-05-19 減衰力調整装置、緩衝装置 Ceased WO2024241407A1 (ja)

Priority Applications (10)

Application Number Priority Date Filing Date Title
JP2025521624A JPWO2024241407A1 (https=) 2023-05-19 2023-05-19
CN202380094552.0A CN120731332A (zh) 2023-05-19 2023-05-19 阻尼力调整装置、缓冲装置
KR1020257027974A KR20250135319A (ko) 2023-05-19 2023-05-19 감쇠력 조정 장치, 완충 장치
PCT/JP2023/018847 WO2024241407A1 (ja) 2023-05-19 2023-05-19 減衰力調整装置、緩衝装置
DE112023005328.6T DE112023005328T5 (de) 2023-05-19 2023-05-19 DÄMPFUNGSKRAFT-EINSTELLVORRICHTUNG UND STOßDÄMPFUNGSVORRICHTUNG
DE112023005586.6T DE112023005586T5 (de) 2023-05-19 2023-12-19 Dämpfungskraft-erzeugungsvorrichtung
CN202380095890.6A CN120936821A (zh) 2023-05-19 2023-12-19 阻尼力产生装置
KR1020257030792A KR20250145112A (ko) 2023-05-19 2023-12-19 감쇠력 발생 장치
PCT/JP2023/045458 WO2024241615A1 (ja) 2023-05-19 2023-12-19 減衰力発生装置
JP2025521791A JPWO2024241615A1 (https=) 2023-05-19 2023-12-19

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WO2019239521A1 (ja) * 2018-06-13 2019-12-19 株式会社ショーワ 圧力緩衝装置

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SE532533C2 (sv) 2008-06-25 2010-02-16 Oehlins Racing Ab Tryckregulator för stötdämpare
JP7667646B2 (ja) * 2020-09-29 2025-04-23 カヤバ株式会社 ソレノイド、電磁弁、および緩衝器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019239521A1 (ja) * 2018-06-13 2019-12-19 株式会社ショーワ 圧力緩衝装置

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JPWO2024241407A1 (https=) 2024-11-28

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