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WO2014109189A1 - Amortisseur hydraulique et procédé pour sa fabrication - Google Patents

Amortisseur hydraulique et procédé pour sa fabrication Download PDF

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Publication number
WO2014109189A1
WO2014109189A1 PCT/JP2013/083865 JP2013083865W WO2014109189A1 WO 2014109189 A1 WO2014109189 A1 WO 2014109189A1 JP 2013083865 W JP2013083865 W JP 2013083865W WO 2014109189 A1 WO2014109189 A1 WO 2014109189A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
seal ring
piston
oil
piston rod
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/JP2013/083865
Other languages
English (en)
Japanese (ja)
Inventor
龍 服部
章 坂田
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.)
Honda Motor Co Ltd
Piolax Inc
Original Assignee
Honda Motor Co Ltd
Piolax Inc
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 Honda Motor Co Ltd, Piolax Inc filed Critical Honda Motor Co Ltd
Publication of WO2014109189A1 publication Critical patent/WO2014109189A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/20—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with the piston-rod extending through both ends of the cylinder, e.g. constant-volume dampers
    • 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
    • F16F9/36—Special sealings, including sealings or guides for piston-rods
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F16J15/3236—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips with at least one lip for each surface, e.g. U-cup packings

Definitions

  • the present invention relates to, for example, a hydraulic damper that damps vibrations in a state in which a door of an automobile is closed, or alleviates a sudden opening / closing operation of a door that opens and closes, and a manufacturing method thereof.
  • hatchbacks, wagons, vans, and other vehicles are equipped with back doors for opening and closing the rear luggage compartment.
  • the back door is configured such that its peripheral edge abuts the peripheral edge of the opening of the cargo compartment via a rubber stopper or the like and closes the opening.
  • the back door resonates due to vibrations during running of the vehicle or idling.
  • unpleasant noise and discomfort may occur.
  • a hydraulic damper that provides a damping action of hydraulic vibration may be used.
  • it can be used in various applications such as alleviating sudden opening and closing operations when various doors and lids of the vehicle open and close, absorbing shocks in the drive system of the vehicle, and preventing vibration of buildings, etc.
  • a hydraulic damper is used.
  • a cylinder having one end closed and an opening provided at the other end, a partition wall having an orifice and partitioning the inside of the cylinder, a piston slidably arranged in the cylinder, A piston rod extending from one end face of the piston and projecting outward from the opening from the opening; a first chamber and a second chamber formed in the cylinder; and a communication pipe communicating with the first chamber and the second chamber A hydraulic anti-vibration device is provided.
  • the first chamber, the second chamber and the communication pipe are filled with oil, and two O-rings for preventing oil leakage are adjacent between the opening of the cylinder and the piston rod. Is arranged.
  • a hydraulic damper if air remains in the hydraulic chamber, it is mixed with the oil to form bubbles, and it is not desirable because it cannot exert a predetermined performance (attenuation performance or shock absorption capability).
  • an object of the present invention is to fill a hydraulic chamber with oil without a gap, and to prevent the oil from leaking to the outside when the piston slides or during manufacture, and a method for manufacturing the same Is to provide.
  • a hydraulic damper includes a flange-like piston body, a piston having a piston rod protruding from at least one end face of the piston body, and a cylinder that slidably accommodates the piston body.
  • the main body and a cylinder portion that slidably supports the piston rod, and a gap between the cylinder filled with oil and the piston rod and the cylinder portion of the cylinder are sealed, and the oil is sealed
  • a seal ring that forms a hydraulic chamber, and the seal ring is a first seal ring that is located on the cylinder body side, and a second seal ring that is located on the outside of the cylinder body with respect to the first seal ring.
  • the oil is filled in the hydraulic chamber sealed with the first seal ring without any gap. Between the second sealing ring and the first seal ring, and a space for holding the oil leaks from the first seal ring is provided.
  • a first annular groove for holding the first seal ring is provided on the cylinder body side on an outer periphery of the piston rod, and the first rod is formed through a partition made of an annular rib.
  • a second annular groove for holding the second seal ring is provided on the outer side of the cylinder body with respect to the one annular groove, and an outer diameter of the partition wall slides on the cylindrical portion of the piston rod. It is preferable that the outer diameter of the supported portion is smaller.
  • the seal pressure of the first seal ring is set larger than the seal pressure of the second seal ring.
  • the piston rod protrudes from both end faces of the piston body
  • the cylinder includes a first body and a second body joined to the first body.
  • the body has a first cylindrical portion that slidably supports one of the piston rods, a cylinder body, and a joint that expands from the outer periphery of the cylinder body into a flange shape and has a peripheral edge standing in a cylindrical shape.
  • the second body includes a second cylinder portion that slidably supports the other of the piston rods, and a flange portion that is joined to the joint portion, and the joint portion and the flange portion.
  • a gasket is interposed between the first body and the peripheral portion of the joint portion of the first body so as to cover the flange portion. It is preferred that Di is bonded.
  • a flange-shaped piston body a piston having piston rods protruding from both end faces of the piston body, a cylinder body for slidably housing the piston body, and A cylinder portion that slidably supports the piston rod, seals a gap between a cylinder filled with oil, and the piston rod and the cylinder portion of the cylinder, and seals the oil to hydraulic pressure.
  • a seal ring that forms a chamber, and the seal ring includes a first seal ring that is located on the cylinder body side, and a second seal ring that is located on the outside of the cylinder body with respect to the first seal ring.
  • a hydraulic damper manufacturing method in which a space for holding the oil leaking from the first seal ring is provided between a ring and the second seal ring, wherein the first body is a piston rod A first cylindrical portion that slidably supports one of the cylinder body, the cylinder main body, and a joint portion that expands from the outer periphery of the cylinder main body into a flange shape and has a peripheral edge standing in a cylindrical shape;
  • the second body has a second cylinder part that slidably supports the other of the piston rods, and a flange part joined to the joint part, and one of the piston rods is connected to the first cylinder of the first body.
  • the piston is accommodated in the first body and the piston is accommodated in the first body.
  • the first body is filled with oil that is larger than the volume of the hydraulic chamber, and the flange of the second body is filled with excess oil.
  • Overflow The first body is inserted into the first body through the gasket and placed in the joint portion, and the peripheral portion of the joint portion of the first body is caulked so as to cover the flange portion. The body and the second body are joined.
  • the hydraulic damper of the present invention when the hydraulic damper is manufactured or the piston is operated, even if the hydraulic chamber has a high pressure and oil leaks from the first seal ring, the leaked oil remains in the first seal ring and the second seal. Since it is held in the space between the ring, it can be prevented from leaking outside. As a result, even if oil is filled in the hydraulic chamber without any gaps, it is possible to maintain good quality by preventing the external leakage of the oil, and because the oil is filled in the hydraulic chambers without any gaps, a stable damper action is obtained. be able to.
  • the first body of the cylinder is filled with oil that exceeds the volume of the hydraulic chamber, and the flange portion of the second body overflows with excess oil.
  • oil can be filled into the hydraulic chamber without any gap.
  • the gasket is crushed, the volume in the hydraulic chamber is reduced, the pressure in the hydraulic chamber is increased, and when the pressure exceeds the seal pressure of the first seal ring, the oil leaks from the first seal ring.
  • the oil leaked from the first seal ring is held in the space between the first seal ring and the second seal ring, and leakage to the outside can be prevented. Furthermore, when caulking the joint, the volume in the hydraulic chamber is reduced and pressurized, and excess oil can be leaked from the first seal ring, so that the oil can be easily filled into the hydraulic chamber without any gaps. The oil pressure in the hydraulic chamber can be kept appropriate.
  • 1 is an exploded perspective view showing an embodiment of a hydraulic damper according to the present invention. It is a cross-sectional perspective view of the hydraulic damper. In the hydraulic damper, it is explanatory drawing in the state where braking force is not acting on a piston rod. In the hydraulic damper, it is explanatory drawing in the state where the piston rod was pushed and braking force acted. It is a principal part expansion explanatory view of the hydraulic damper. 1 shows an embodiment of a method for manufacturing a hydraulic damper according to the present invention, and is an explanatory view of a first step thereof. It is explanatory drawing which shows the 2nd process of the manufacturing method of the hydraulic damper. It is explanatory drawing which shows the 3rd process of the manufacturing method of the hydraulic damper.
  • the hydraulic damper 10 of this embodiment includes an opening 3 provided in a rear luggage compartment of an automobile, and a hatchback door attached to the opening 3.
  • the opening / closing body 5 is used to prevent vibration when the opening / closing body 5 is closed.
  • this hydraulic damper is not limited to this, for example, it is used for vibration prevention of hinge doors and slide doors on the side of the vehicle, when opening and closing the doors, and when opening and closing the glove box or lid, It may be used as a buffer for a sudden opening / closing operation.
  • the hydraulic damper 10 of this embodiment includes a piston 20 and a cylinder 40 that slidably accommodates the piston 20.
  • the piston 20 includes a flange-shaped piston main body 21 and piston rods 23 and 25 protruding from both end surfaces of the piston main body 21.
  • the cylinder 40 includes a first body 40A and a second body 40B joined to the first body 40A.
  • the cylinder body 43 and the piston rods 23 and 25 that slidably accommodate the piston body 21 are slidable. It has the cylinder parts 41 and 47 supported by. In each piston rod 23, 25, a gap between the piston rods 23, 25 and the cylinder portions 41, 47 of the cylinder 40 is sealed, and oil O is sealed to form a hydraulic chamber 51 (see FIGS.
  • the hydraulic damper 10 includes a coil spring 56 that urges the piston rod 23 toward the opening 3 of the automobile, a cover member 58 that covers the cylinder 40, and a stopper that attaches the cylinder 40 to the opening / closing body 5. 60.
  • the first seal ring 35 and the second seal ring 37 constitute a “seal ring” in the present invention.
  • the piston 20 protrudes from the center of one end surface of the piston body 21 having a circular flange shape and a predetermined length, and slides to the first tube portion 41 of the first body 40A. From the center of the other end surface of the piston rod 23 to be supported and the piston main body 21, it projects coaxially with the piston rod 23 and shorter than the piston rod 23, and is slidably supported by the second cylinder portion 47 of the second body 40B. And a piston rod 25.
  • notched orifices 21a and 21a are formed at opposing positions on the outer periphery of the piston main body 21, respectively.
  • the present invention is not limited to this mode.
  • a through hole is provided in the piston main body 21 as an orifice, or a gap is provided between the inner periphery of the cylinder main body 43 and the outer periphery of the piston main body 21. Good.
  • a first annular groove 27 is formed on the cylinder body 43 side in the middle of each piston rod 23, 25 in the axial direction, and through a partition wall 29 made of an annular rib.
  • a second annular groove 31 is formed outside the cylinder body 43 with respect to the first annular groove 27.
  • a first seal ring 35 is attached to the first annular groove 27, the first seal ring 35 is disposed on the cylinder body 43 side, and a second seal ring 37 is attached to the second annular groove 31.
  • the second seal ring 37 is arranged outside the first seal ring 35 with respect to the cylinder body 43.
  • the outer diameter D2 of the partition wall 29 is smaller than the outer diameter D1 of the portions of the piston rods 23, 25 that are slidably supported by the cylinder portions 41, 47 of the cylinder 40. As a result, the space 52 is formed.
  • the first seal ring 35 and the second seal ring 37 in this embodiment include a so-called U-shaped section having a bifurcated outer peripheral lip and an inner peripheral lip and having a U-shaped cross section. Packing is adopted, and the outer peripheral lip and the inner peripheral lip are mounted in the respective annular grooves 27 and 31 with the cylinder body 43 side facing.
  • the seal ring may be, for example, a so-called O-ring having a circular cross section, a so-called V packing having a V-shaped cross section, or other cross-sectional shapes, and is not particularly limited.
  • the seal pressure of the first seal ring 35 is preferably set larger than the seal pressure of the second seal ring 37.
  • the seal pressure of the outer peripheral lip of the first seal ring 35 with respect to the cylinder portions 41 and 47 of the cylinder 40 is set to be larger than the seal pressure of the outer peripheral lip of the second seal ring 37.
  • an E-ring mounting groove 33 is formed on the outer periphery of the tip of the piston rod 23, and an E-ring 57 is mounted on the E-ring mounting groove 33 to prevent the washer plate 55 disposed at the tip of the piston rod from slipping out. (See FIGS. 2 to 4).
  • An elastic contact member 59 that elastically contacts the periphery of the opening 3 (see FIG. 9) of the automobile is mounted on the front side of the washer plate 55 (see FIGS. 1 to 4). .
  • the cylinder 40 that slidably accommodates the piston 20 having the above-described structure is composed of the first body 40A and the second body 40B joined thereto, as described above.
  • the first body 40A includes a cylindrical first tube portion 41 that is slidably supported by inserting the piston rod 23, and a flange at one end portion of the first tube portion 41.
  • a cylinder main body 43 that is continuously connected via a connecting wall 44 and has a diameter larger than that of the first cylinder portion 41 and that slidably accommodates the piston main body 21, and an outer periphery of one end of the cylinder main body 43.
  • the peripheral portion 45a has a joint portion 45 erected in a cylindrical shape.
  • the second body 40B joined to the first body 40A includes a bottomed cylindrical second cylindrical portion 47 that slidably supports the piston rod 25, and an opening peripheral edge of the second cylindrical portion 47. It has a flange portion 49 that extends in the outer diameter direction and has a smaller diameter than the inner diameter of the peripheral edge portion 45a of the joint portion 45 of the first body 40A.
  • a connecting hole 50 is formed in the center of the bottom of the second cylindrical portion 47 (see FIGS. 2 to 4), and a plurality of notches not shown are provided on the outer periphery thereof at equal intervals in the circumferential direction. .
  • annular gasket 54 made of woven fabric or rubber is interposed between the joint portion 45 of the first body 40A and the flange portion 49 of the second body 40B, and joined to the surface side of the flange portion 49.
  • the second body 40B is joined to the first body 40A in a liquid-tight state by caulking the peripheral portion 45a of the portion 45 so that a hydraulic chamber 51 is formed in the cylinder 40 (see FIG. 2-4).
  • first body 40A and the second body 40B may be joined without using the gasket 54.
  • the first body 40A and the second body 40B are joined.
  • the gap between the piston rod 23 and the first tube portion 41 of the first body 40A, and the piston rod 25 and the first body 40B are joined.
  • the gap between the second body 40B and the second cylindrical portion 47 is sealed by the first seal ring 35 and the hydraulic chamber 51 is sealed, so that the oil O is filled in the hydraulic chamber 51 without any gap. It has become.
  • the oil is filled in the hydraulic chamber without any gap means that the oil is filled in every corner without having a void (bubble) that can be visually discriminated in the hydraulic chamber. It means the state. However, the presence of a minute amount of air dissolved or dispersed in the oil is acceptable.
  • a stopper 60 for attaching the cylinder 40 to the opening / closing body 5 is mounted on the outer periphery of the second body 40B.
  • the stopper 60 engages with the front peripheral edge of the mounting hole 7 (see FIGS. 3 and 4) of the opening / closing body 5, and a flange portion 61 in which a seal member 68 (see FIG. 1) is disposed on the back surface side thereof, While being inserted into the mounting hole 7, a bottomed cylindrical housing cylinder portion 63 that houses the second cylinder portion 47 of the second body 40 ⁇ / b> B, and an engaging claw 65 that engages with the rear peripheral edge of the mounting hole 7. And have. Further, a connecting hole 63a is formed at the bottom of the accommodating cylinder 63, and a rivet 67 is inserted into and engaged with the connecting hole 50 of the second cylinder 47 of the second body 40B. A stopper 60 is attached to the cylinder 40 via a rivet 67 (see FIGS. 2 to 4).
  • a coil spring 56 is disposed in a compressed state on the outer periphery of the first body 40A of the cylinder 40, one end of which is abutted and supported by the joint 45 of the first body 40A, and the other end of the piston rod 23. It is abutted and supported by a washer plate 55 attached to the tip. As a result, the piston rod 23 protrudes from the tip opening of the first cylinder portion 41 of the first body 40A via the washer plate 55 and is attached toward the opening 3 (see FIG. 9) side of the automobile. Has come to be.
  • the cylinder 40 is inserted into the mounting hole 7 of the opening / closing body 5 through the stopper 60 and fixed (see FIGS. 3 and 4), but the portion protruding from the mounting hole 7 to the front side can be expanded and contracted.
  • the cover member 58 is covered.
  • the cover member 58 is formed of an elastic material such as rubber, and as shown in FIGS. 1 to 4, a base portion 58a is attached to the outer periphery of the collar portion 61 of the stopper 60 to form a bellows-like cover.
  • the cylindrical portion 58b covers the protruding portion of the cylinder 40 from the mounting hole 7.
  • the hydraulic damper 10 configured as described above is used when the oil O filled in the hydraulic chamber 51 without a gap passes through the orifice 21a of the piston main body 21 when the piston main body 21 slides in the cylinder 40. A braking force is applied to the piston body 21 by the flow resistance.
  • the piston body 21 is normally urged by the coil spring 56 and abuts against the connecting wall 44 of the first body 40A (see FIG. 3), and resists the urging force of the coil spring 56 on the second body 40B side. When moving to the position, it contacts the gasket 54 and further movement is restricted (see FIG. 4).
  • a jig 70 for supporting the first body 40A of the cylinder 40 and a hanging tool 79 for hanging and supporting the second body 40A are used.
  • the jig 70 includes an accommodating portion 71 that receives the first cylindrical portion 41 of the first body 40A, and a stepped portion 73 that supports the joining portion 45 of the first body 40A.
  • a ring mounting groove 75 is formed in the O-ring 77.
  • the hanging tool 79 has an engaging portion 79a that can be inserted into or inserted into the second cylindrical portion 47 in alignment with the connection hole 50 of the second body 40B and a notch (not shown). .
  • first seal ring 35 and the second seal ring 37 are attached to the piston rods 23 and 25 of the piston 20 in advance.
  • the piston rod 23 of the piston 20 is inserted into the first cylinder portion 41 of the first body 40A, and the gap between the first cylinder portion 41 and the piston rod 23 is sealed with the first seal ring 35 and the second seal ring 37.
  • the tip end portion projects from the tip opening of the first tube portion 41, and the piston body 21 is brought into contact with the connecting wall 44.
  • the first cylindrical portion 41 of the first body 40A is turned downward and inserted into the accommodating portion 71 of the jig 70, and the joint portion 45 of the first body 40A is supported by the stepped portion 73, and the jig
  • the first body 40A and the piston 20 are positioned and fixed to 70 (see FIG. 6).
  • the O-ring 77 elastically contacts the outer periphery of the peripheral portion 45a of the joint portion 45 of the first body 40A, and the gap between the upper peripheral wall of the jig 70 and the peripheral portion 45a of the joint portion 45 is sealed.
  • the gasket 54 is placed on the upper part of the inner surface of the joint 45 of the first body 40A.
  • the engaging portion 79a of the suspending tool 79 is inserted into the connecting hole 50 and the notch of the second body 40B in alignment, and the suspending tool 79 is rotated, whereby the engaging portion 79a is moved to the second cylinder.
  • the second body 40B is suspended and supported by engaging with the inner surface of the bottom of the portion 47, and the flange portion 49 is disposed in a state aligned with the joint 45 of the first body 40A (see FIG. 6).
  • the oil O is supplied from the oil supply device 81, and the oil O exceeding the volume of the hydraulic chamber 51 is filled in the first body 40A.
  • the oil O is filled more than the height of the peripheral edge 45a of the joint 45 of the first body 40A, and overflows from the first body 40.
  • the second body 40B is lowered through the suspending tool 79, and the flange portion 49 is inserted into the peripheral portion 45a of the joint portion 45 of the first body 40A while overflowing excess oil O,
  • the flange portion 49 is placed on the upper part of the inner surface of the joint portion 45 of the first body 40A via the gasket 54 (see FIG. 8).
  • the engaging part 79a of the hanging tool 79 is removed from the connecting hole 50 and the notch of the second body 40B
  • the engaging part 79a is rotated so as not to be aligned with the connecting hole 50 and the notch.
  • the bottom of the second cylindrical portion 47 of the second body 40B is pushed downward.
  • the excess oil O overflowed is sucked appropriately, and the peripheral portion 45a of the joint portion 45 is covered on the surface side of the flange portion 49 in a state where the oil O is slightly left on the flange portion 49 of the second body 40B.
  • the second body 40B is attached to the first body 40A in a state where the gap between the joint portion 45 of the first body 40A and the flange portion 49 of the second body 40B is sealed while the gasket 54 is crushed. They can be joined (see FIGS. 2 to 4).
  • the hydraulic chamber 51 of the cylinder 40 is filled with oil O that exceeds its capacity, and the flange portion 49 of the second body 40B overflows with excess oil O.
  • the oil is inserted into the first body 40A through the gasket 54 and placed on the inner surface of the joint 45, and the peripheral edge 45a is caulked in that state.
  • the first body 40A and the second body 40B can be joined in the filled state.
  • the volume in the hydraulic chamber 51 is reduced and pressurized, and the excess oil O is supplied to the first portion.
  • the seal ring 35 By leaking from the seal ring 35, the oil O can be easily filled into the hydraulic chamber 51 without a gap, and the pressure of the oil O in the hydraulic chamber 51 can be kept appropriate.
  • the coil spring 56 is attached to the outer periphery of the first body 40A of the cylinder 40 via the washer plate 55, the stopper 60 is attached to the cylinder 40 via the rivet 67, and the outer periphery of the cylinder 40 is covered.
  • the hydraulic damper 10 of this embodiment is manufactured.
  • the hydraulic damper 10 is attached to the attachment hole 7 of the opening / closing body 5 via a stopper 60.
  • the hydraulic damper 10 can be attached to the attachment hole 7 by engaging the back side periphery and indirectly engaging the flange portion 61 of the stopper 60 via the seal member 68 to the front side periphery of the attachment hole 7. it can.
  • the hydraulic damper 10 is attached to the attachment hole 7 of the opening / closing body 5, but conversely, an attachment hole is formed in the periphery of the opening 3 of the automobile, and the periphery thereof is formed.
  • the hydraulic damper 10 may be attached.
  • the oil pressure chamber 51 is filled with the oil O without a gap and no bubbles are mixed therein, so that the buffer performance can be effectively exhibited.
  • the opening / closing body 5 is locked in a state in which the opening 3 is closed by a locking device or the like (not shown). May resonate.
  • the hydraulic damper 10 such vibration of the opening / closing body 5 can be prevented. That is, when the piston rod 23 that is in contact with the opening / closing body 5 via the elastic contact member 59 slides due to the vibration of the opening / closing body 5 and the piston body 21 moves in the cylinder body 43, the oil that passes through the orifice 21a. Since the braking force acts on the piston body 21 due to the flow resistance of O, the vibration of the opening / closing body 5 can be attenuated, and the resonance of the opening / closing body 5 can be prevented. Further, as described above, in the hydraulic damper 10, since the oil O is filled in the hydraulic chamber 51 without a gap, the damping performance can be effectively exhibited.
  • the outer diameter D2 of the partition wall 29 provided between the first annular groove 27 and the second annular groove 31 of the piston rods 23, 25 is the piston rod 23.
  • 25 is formed smaller than the outer diameter D1 of the portion slidably supported by the cylinder portions 41, 47 of the cylinder 40, so that the capacity of the space 52 for holding the oil O leaked from the first seal ring 35 is sufficient. Can be secured.
  • the seal pressure of the first seal ring 35 is set to be larger than the seal pressure of the second seal ring 37, the first seal ring 35 having a high seal pressure causes the pressure from the hydraulic chamber 51. Oil leakage can be effectively prevented and the oil O leaked from the first seal ring 35 can be held only by holding the seal pressure of the second seal ring 37 low so that the oil O leaks to the outside. The sliding resistance when the piston rods 23 and 25 slide with respect to the cylindrical portions 41 and 47 can be reduced.
  • the flange portion 49 is joined via the gasket 54 by caulking the peripheral edge portion 45a of the joint portion 45 of the first body 40A so as to cover the flange portion 49 of the second body 40B. Since it is in close contact with the portion 45, the first body 40A and the second body 40B can be hermetically sealed. Further, when the joint 45 is caulked, the gasket 54 is crushed, the volume in the hydraulic chamber 51 is reduced, the pressure in the hydraulic chamber 51 is increased, and when the pressure exceeds the seal pressure of the first seal ring 35, the oil O May leak from the first seal ring 35, but the oil O leaked from the first seal ring 35 is held in the space 52 between the first seal ring 35 and the second seal ring 37, and then to the outside.
  • FIG. 10 shows another embodiment of the hydraulic damper and the manufacturing method thereof according to the present invention. Note that substantially the same parts as those of the above-described embodiment are denoted by the same reference numerals, and description thereof is omitted.
  • the structure of the second annular groove 31a for mounting the second seal ring 37 provided on the piston rods 23 and 25 is different from that of the embodiment in the hydraulic damper 10a of this embodiment.
  • the second annular groove 31 a is formed such that its axial length (length along the axial direction of the rod) is longer than the axial length of the first annular groove 27, and the second seal ring 37.
  • a gap 31b capable of holding the oil O is provided in the state where the oil is attached.
  • FIG. 11 shows still another embodiment of the hydraulic damper and the manufacturing method thereof according to the present invention. Note that substantially the same parts as those of the above-described embodiment are denoted by the same reference numerals, and description thereof is omitted.
  • the hydraulic damper 10b of this embodiment is different from that of the above embodiment in the structure of the partition wall provided on the piston rods 23 and 25 and defining the first annular groove 27 and the second annular groove 31.
  • a plurality of partition walls 29, 29 are formed between the first annular groove 27 and the second annular groove 31, and an annular groove capable of holding the oil O between these partition walls 29, 29. 29a is provided.

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

Abstract

L'invention porte sur un amortisseur hydraulique, qui permet à de l'huile de remplir complètement l'intérieur d'une chambre hydraulique, et qui peut empêcher l'huile de fuir vers l'extérieur pendant le coulissement d'un piston ou pendant la fabrication. L'invention porte également sur un procédé pour fabriquer l'amortisseur hydraulique. L'amortisseur hydraulique (10) a : un piston (20) ayant un corps de piston (21) et des tiges de piston (23, 25) ; un cylindre (40) ayant un corps de cylindre (43) et des parties cylindriques (41, 47), le cylindre (40) étant rempli intérieurement par une huile (O) ; des premières bagues d'étanchéité (35) pour sceller hermétiquement l'espace entre les tiges de piston (23, 25) et les parties cylindriques (41, 47) de façon à former une chambre hydraulique (51), les premières bagues d'étanchéité (35) étant positionnées plus près du corps de cylindre ; et des secondes bagues d'étanchéité (37) positionnées plus loin vers l'extérieur du corps de cylindre que ne le sont les premières bagues d'étanchéité (35). Quand l'huile (O) remplit complètement l'intérieur de la chambre hydraulique (51), un espace (52) pour contenir de l'huile (O) qui fuit à partir des premières bagues d'étanchéité (35) est constitué entre les premières bagues d'étanchéité (35) et les secondes bagues d'étanchéité (37).
PCT/JP2013/083865 2013-01-11 2013-12-18 Amortisseur hydraulique et procédé pour sa fabrication Ceased WO2014109189A1 (fr)

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JP2013003514 2013-01-11
JP2013-003514 2013-01-11

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WO2014109189A1 true WO2014109189A1 (fr) 2014-07-17

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104806692A (zh) * 2015-04-20 2015-07-29 天津大学仁爱学院 一种自复位油阻尼器
CN105697637A (zh) * 2015-04-24 2016-06-22 北京京西重工有限公司 磁流变阻尼器的闭合组件
CN114688198A (zh) * 2022-05-09 2022-07-01 沈阳鑫通电站设备制造有限公司 一种用于液压阻尼器的密封环组及密封结构
CN119745294A (zh) * 2024-12-30 2025-04-04 宁波方太厨具有限公司 一种清洗机

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Publication number Priority date Publication date Assignee Title
JPS5954235U (ja) * 1982-10-04 1984-04-09 日産自動車株式会社 振動体の支持装置
JPS60131737U (ja) * 1984-02-13 1985-09-03 エヌオーケー株式会社 シヨツクアブソ−バ用シ−ル
JPH0196542U (fr) * 1987-12-18 1989-06-27
JP2010276062A (ja) * 2009-05-27 2010-12-09 Kayaba Ind Co Ltd 空圧緩衝器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5954235U (ja) * 1982-10-04 1984-04-09 日産自動車株式会社 振動体の支持装置
JPS60131737U (ja) * 1984-02-13 1985-09-03 エヌオーケー株式会社 シヨツクアブソ−バ用シ−ル
JPH0196542U (fr) * 1987-12-18 1989-06-27
JP2010276062A (ja) * 2009-05-27 2010-12-09 Kayaba Ind Co Ltd 空圧緩衝器

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104806692A (zh) * 2015-04-20 2015-07-29 天津大学仁爱学院 一种自复位油阻尼器
CN104806692B (zh) * 2015-04-20 2017-01-11 天津大学仁爱学院 一种自复位油阻尼器
CN105697637A (zh) * 2015-04-24 2016-06-22 北京京西重工有限公司 磁流变阻尼器的闭合组件
JP2016205615A (ja) * 2015-04-24 2016-12-08 ベイジンウェスト・インダストリーズ・カンパニー・リミテッドＢｅｉｊｉｎｇｗｅｓｔ Ｉｎｄｕｓｔｒｉｅｓ Ｃｏ．， Ｌｔｄ． 磁気粘性流体ダンパの閉塞アッセンブリ
US10072723B2 (en) 2015-04-24 2018-09-11 Beijingwest Industries Co., Ltd. Closing assembly for a magneto-rheological damper
CN114688198A (zh) * 2022-05-09 2022-07-01 沈阳鑫通电站设备制造有限公司 一种用于液压阻尼器的密封环组及密封结构
CN114688198B (zh) * 2022-05-09 2025-10-17 沈阳鑫通电站设备制造有限公司 一种用于液压阻尼器的密封环组及密封结构
CN119745294A (zh) * 2024-12-30 2025-04-04 宁波方太厨具有限公司 一种清洗机

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