WO2012114943A1 - Damper - Google Patents
Damper Download PDFInfo
- Publication number
- WO2012114943A1 WO2012114943A1 PCT/JP2012/053413 JP2012053413W WO2012114943A1 WO 2012114943 A1 WO2012114943 A1 WO 2012114943A1 JP 2012053413 W JP2012053413 W JP 2012053413W WO 2012114943 A1 WO2012114943 A1 WO 2012114943A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- bladder
- piston rod
- tip
- distal end
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/362—Combination of sealing and guide arrangements for piston rods
Definitions
- the present invention relates to a damper having an accumulator in a cylinder, and more particularly, to a damper having an accumulator in which a bladder is wound around a cylindrical liner fitted on a piston rod.
- FIG. 4A is a cross-sectional view showing the internal structure of the damper
- FIG. 4B is a diagram illustrating a process in which the accumulator constituting the damper is incorporated into the cylinder.
- a cap CP for enclosing each component inside the cylinder C is fitted into the base end of the cylinder C formed in a bottomed two-stage cylindrical shape.
- a piston rod R extending along the center axis of the cylinder C is inserted into the cylinder C so as to penetrate the cap CP.
- a cylindrical piston P is fitted inside the small diameter portion C1 of the cylinder C, and among the piston rod R, the large diameter portion C2 of the cylinder C has a large diameter portion.
- a spool-shaped liner 50 positioned in C2 is fitted.
- a seal ring SR that seals between the liner 50 and the piston rod R is fitted on the base end of the liner 50 in the piston rod R.
- the piston P is formed in a slidable cylindrical shape on the inner peripheral surface of the small diameter portion C1, and the internal space of the small diameter portion C1 is divided into a distal end side of the piston P and a proximal end side of the piston P.
- the piston P has a throttle PH extending in the axial direction of the piston rod R, so that silicon oil is generated between the space on the tip end side of the piston P and the space on the base end side of the piston P under a predetermined fluid resistance. Circulate.
- a cylindrical sleeve portion 51 is fitted on the piston rod R at the center in the axial direction of the piston rod R.
- a distal end flange portion 52 having a diameter larger than that of the sleeve portion 51 and a proximal end flange portion 53 having a diameter larger than that of the sleeve portion 51 are connected to both end portions in the axial direction of the sleeve portion 51.
- the front end flange portion 52 has a flow path 52H extending in the axial direction of the piston rod R, and silicon between the inside of the small diameter portion C1 which is the front end side of the front end flange portion 52 and the outside in the radial direction of the sleeve portion 51. Distribute the oil.
- a bladder 60 is wound around the outer peripheral surface of the liner 50 so as to cover the entire outer peripheral surface.
- the bladder 60 is an elastic body formed of an elastomer, a resin, or the like, and is formed in a bobbin shape extending in the axial direction of the piston rod R.
- the opening on the distal end side of the bladder 60 is bent to the inside in the radial direction of the piston rod R, and is hooked to the distal end of the distal flange portion 52 so that the distal end side of the flow path 52H is opened.
- the opening on the base end side of the bladder 60 is also bent inward in the radial direction and is hooked to the base end of the base end flange portion 53.
- the space in the cylinder C is divided into the following four spaces by the piston P and the bladder 60.
- a space on the tip side with respect to the piston P (first space S1) in the small diameter portion C1.
- a space on the proximal end side with respect to the piston P (second space S2) in the small diameter portion C1.
- a space outside the bladder 60 (fourth space S4) in the large-diameter portion C2.
- silicon oil flows through the throttle PH of the piston P under a predetermined fluid resistance. Further, silicon oil circulates between the second space S2 and the third space S3 via the flow path 52H.
- the bladder 60 partitions the space between the second space S2 and the fourth space S4 and the space between the third space S3 and the fourth space S4.
- the front end side of the bladder 60 is required to have a function of sealing between the second space S2 and the third space S3 and between the second space S2 and the fourth space S4. . Therefore, the distance between the outer peripheral surface of the front end flange portion 52 and the inner peripheral surface of the large diameter portion C2 is usually designed such that the front end side of the bladder 60 is crushed in the radial direction so as to ensure these seals. ing.
- a large frictional force F in the direction opposite to the direction in which the piston rod R is inserted acts on the bladder 60. Become.
- the present invention has been made in view of such circumstances, and an object of the present invention is to provide a damper capable of suppressing a decrease in fluid sealing performance in a cylinder.
- a cylinder in which a cap into which a piston rod is inserted is fitted at a proximal end, and an annular concentric with the piston rod accommodated in the cylinder.
- An accumulator the accumulator being pinched between the liner and the cylinder, the liner being a thread-wound cylindrical body fitted around the piston rod, and the outer peripheral surface of the liner and the cylinder
- a cylindrical bladder that divides a fluid chamber having a variable volume in an annular space between the inner circumferential surface and a fluid flowing in and out of the fluid chamber to circulate the fluid in the cylinder
- a damper that brakes the piston rod by a fluid resistance of a fluid, wherein the bladder projects outward in a radial direction of the bladder and is
- the cylinder has an inner diameter that is greater than or equal to the outer diameter of the sliding protrusion at the accommodating portion where the accumulator is accommodated, and
- a damper having an annular pressing ridge that protrudes toward the proximal end side of the housing portion and presses the sliding ridge toward the proximal end side is provided on the end surface on the distal end side of the portion.
- the piston rod is inserted from the base end of the cylinder into the cylinder while the accumulator is fitted on the piston rod.
- the front end of the bladder constituting the accumulator slides on the inner peripheral surface of the cylinder. Accordingly, the front end of the bladder has a frictional force that shifts the front end of the bladder toward the base end. Will be added.
- the damper according to the first aspect of the present invention since the inner diameter of the housing portion is equal to or larger than the outer diameter of the sliding protrusion, the above-described inner peripheral surface of the housing portion is described above on the tip side of the accumulator. Only the sliding ridge will come into contact predominantly.
- a cylinder in which a cap into which a piston rod is inserted is fitted at a base end, and an accumulator that is accommodated in the cylinder and has an annular shape concentric with the piston rod, The accumulator is inserted between the liner and the cylinder, the liner being a thread-wound cylindrical body fitted on the piston rod, and between the outer peripheral surface of the liner and the inner peripheral surface of the cylinder.
- a cylindrical bladder that divides a fluid chamber having a variable volume in the annular space, and causes the fluid to flow into and out of the fluid chamber to circulate the fluid in the cylinder, and the piston by the fluid resistance of the fluid
- a damper for braking a rod wherein the bladder protrudes outward in the radial direction of the bladder and has an annular sliding protrusion whose outer diameter is maximized by the bladder.
- the cylinder has an annular shape that protrudes toward the proximal end side of the accommodating portion and pushes the sliding protrusion toward the proximal end side on the distal end side surface of the accommodating portion in which the accumulator is accommodated.
- a frictional force is applied to the distal end portion of the bladder so as to shift the distal end portion of the bladder toward the proximal end side.
- the pressing ridge presses the sliding ridge on the distal end side of the housing portion. Therefore, the sealing performance of the fluid chamber is ensured by the contact between the annular pressing protrusion and the annular sliding protrusion. Then, the pressing protrusion presses the sliding protrusion with a force larger than the force with which the sliding protrusion presses the inner peripheral surface of the cylinder. Therefore, it is possible to suppress the force with which the sliding protrusions press the inner peripheral surface of the cylinder, that is, to suppress the above-described frictional force. As a result, it is possible to suppress a decrease in fluid sealing performance in the cylinder.
- the cylinder has a small-diameter portion having an inner diameter smaller than the accommodating portion connected to the distal end side of the accommodating portion concentrically with the accommodating portion, and the pressing ridge is formed on the piston rod. It is an annular ridge protruding in the axial direction, and is preferably provided on the end surface of the accommodating portion to which the small diameter portion is connected.
- a small diameter portion having an inner diameter smaller than the housing portion is connected to the distal end side of the housing portion, and projects inward in the radial direction.
- a protrusion is formed in the internal peripheral surface of a cylinder.
- the ridge protruding inward in the radial direction is formed on the inner peripheral surface of the cylinder, for example, when resin molding the cylinder, it is difficult to pull out the mold from the base end side of the cylinder, It becomes difficult to manufacture the cylinder itself integrally.
- the small-diameter portion having an inner diameter smaller than the housing portion is connected to the distal end side of the housing portion concentrically with the housing portion and toward the proximal end side of the housing portion.
- a pressing ridge protruding in a protruding manner is provided on the end face of the accommodating portion connected to the small diameter portion.
- an opening end formed by bending an opening edge on the tip end side of the bladder radially inward is formed on the tip end side of the sliding protrusion. It is preferable that the portion is hooked to the end surface on the front end side of the liner and is sandwiched between the end surface on the front end side of the liner and the end surface on the front end side of the housing portion.
- the sliding protrusion on the bladder is pressed by the pressing protrusion, and the opening end of the bladder is sandwiched between the liner and the accommodating portion. Then, on the front end side of the accumulator, the sealing performance between the bladder and the cylinder is ensured at two locations of the sliding protrusion and the opening end. As a result, it is possible to more reliably suppress a decrease in fluid sealing performance in the cylinder.
- the liner has a sleeve portion fitted on the piston rod, and the sleeve portion has a distal end flange portion that presses the distal end portion of the bladder against the cylinder at the distal end.
- a base end flange portion that presses the base end portion of the bladder against the cylinder is provided at the base end, and the fluid chamber is partitioned by the sleeve portion, the front end flange portion, the base end flange portion, and the bladder.
- the distal end flange portion has a latching groove over the entire circumferential direction of the distal end flange portion, and the opening end portion on the distal end side of the bladder is latched by the latching groove.
- the opening end portion on the distal end side of the bladder is latched in the retaining groove over the entire distal end flange portion, it is possible to make the position displacement of the bladder more difficult to occur due to the frictional force described above. It is.
- the distal end flange portion has a plurality of distal end flange pieces that press the distal end portion of the bladder against the cylinder at the distal end, and the plurality of distal end flange pieces are proximal end portions of the distal end flange piece.
- the liner is arranged in the circumferential direction of the liner in the form of a cantilever that is supported by.
- the front end of the liner is formed with a plurality of front end flange pieces that press the front end of the bladder against the cylinder in the circumferential direction, and each of the front end flange pieces is supported at the base end. It is formed in a cantilever shape. According to such a structure, the frictional force mentioned above will be converted into the force which bends a some front-end
- the damper of the present invention is embodied
- the damper is installed between an opening / closing body such as a drawer or a door of a housing facility and a fixed-side member that fixes the opening / closing body, and the impact and noise when the opening / closing body and the fixing member collide with each other.
- an opening / closing body such as a drawer or a door of a housing facility
- a fixed-side member that fixes the opening / closing body
- a thread-wound bladder 20 is wound around a resin liner 10 fitted on the piston rod R.
- the bladder 20 is an elastic body made of an elastomer or a resin, and covers the entire liner 10 on the outer peripheral surface of the liner 10, while opening both ends of the liner 10 in the axial direction of the piston rod R. Is formed.
- a rod insertion hole 10H through which the piston rod R is inserted passes through the center of the liner 10 which is a pincushion-shaped cylinder so as to extend along the axial direction of the piston rod R. Further, in the liner 10, a cylindrical sleeve portion 11 is fitted on the piston rod R at the center in the axial direction of the piston rod R.
- a cylindrical tip flange portion 12 having an outer diameter larger than the outer diameter of the sleeve portion 11 is formed integrally with the sleeve portion 11 at one end portion in the axial direction of the piston rod R of the sleeve portion 11. ing.
- the distal end flange portion 12 has a flow path 12H extending in the axial direction of the piston rod R, and between the inside of the small diameter portion C1 on the distal end side of the distal end flange portion 12 and the radially outer side of the sleeve portion 11. Circulate.
- a proximal flange portion 13 having an outer diameter larger than the outer diameter of the sleeve portion 11 is also integrated with the sleeve portion 11 at the other end portion in the axial direction of the piston rod R. Molded.
- the piston rod R is concentric between the outer peripheral surface of the sleeve portion 11 and the inner peripheral surface of the cylinder C. Is formed so as to be sandwiched between the distal end flange portion 12 and the proximal end flange portion 13.
- the side of the distal end flange portion 12 with respect to the sleeve portion 11 is defined as the distal end side
- the side of the proximal end flange portion 13 with respect to the sleeve portion 11 is defined as the proximal end side.
- a fitting hole 13H for fitting a seal ring SR that seals between the proximal flange portion 13 and the piston rod R is formed in the proximal end portion of the proximal flange portion 13 along the axial direction of the piston rod R. It is extended.
- the piston rod R inserted through the liner 10 moves in the axial direction with respect to the liner 10 while maintaining the sealing performance with the liner 10 through the seal ring SR fitted in the fitting hole 13H.
- the outer shape of the bladder 20 wound around the liner 10 is formed in a bobbin shape so as to follow the outer peripheral surface of the liner 10 described above.
- an expansion / contraction part 21 which is a region bent inward in the radial direction of the piston rod R, is defined in the center of the piston rod R in the axial direction.
- the stretchable part 21 allows a transition between a state bent inward in the radial direction and a state displaced from the state outward in the radial direction.
- a cylindrical tip gripping portion 22 having an inner diameter larger than the inner diameter of the extension / contraction portion 21 is partitioned at the tip end side of the extension / contraction portion 21 so as to be in close contact with the outer peripheral surface of the tip flange portion 12.
- the inner diameter of the distal end gripping portion 22 is smaller than the outer diameter of the distal end flange portion 12, so that the distal end gripping portion 22 has a contracting force that contracts inward in the radial direction, and the distal end flange portion 12. To come to grip. Further, a tip opening end portion 22 ⁇ / b> E which is an opening portion on the tip end side in the tip gripping portion 22 is bent inward in the radial direction of the piston rod R.
- the opening inner diameter DL which is the inner diameter of the tip opening end 22E, is smaller than the inner diameter of the small-diameter portion C1 described above.
- the distal end opening end portion 22E of the distal end gripping portion 22 is latched to the end face on the distal end side of the distal end flange portion 12. Then, the hooked tip opening end 22E is pressed by the tip end surface CS of the large diameter portion C2 that is the housing portion and the tip end surface of the tip flange portion 12.
- a tip sliding ridge 22 ⁇ / b> T which is a ridge protruding outward in the radial direction, is provided so as to protrude over the entire circumferential direction of the tip gripping portion 22.
- the tip sliding protrusion 22T is formed in an arc shape in a cross section including the axial direction of the piston rod R, and is a portion slightly proximal to the tip of the tip gripping portion 22 in the axial direction of the piston rod R. It is arranged.
- the outer diameter DH which is the outer diameter of the tip sliding protrusion 22T, is larger than the outer diameter DB of the other part of the bladder 20 and is the same as the cylinder inner diameter DC, which is the inner diameter of the large diameter portion C2.
- a cylindrical base end gripping portion 23 having an inner diameter larger than the inner diameter of the stretchable portion 21 is partitioned so as to be in close contact with the outer peripheral surface of the base end flange portion 13. .
- the inner diameter of the proximal end gripping portion 23 is smaller than the outer diameter of the proximal end flange portion 13, so that the proximal end gripping portion 23 has a contracting force that contracts radially inward, and thus the proximal end flange 23 The part 13 is gripped.
- a base end sliding protrusion 23T which is a protrusion protruding outward in the radial direction, is provided so as to protrude over the entire circumferential direction of the base end gripping portion 23.
- the outer surface of the proximal end sliding protrusion 23T is formed in an arc shape in a cross section including the axial direction of the piston rod R, and the proximal end gripping in the axial direction of the piston rod R is the same as the distal end sliding protrusion 22T.
- the holding portion 23 is disposed at a position slightly closer to the distal end side than the proximal end.
- the outer diameter of the base end sliding protrusion 23T is larger than the protrusion outer diameter DH of the above-described distal end sliding protrusion 22T and larger than the cylinder inner diameter DC.
- the opening on the base end side in the base end gripping portion 23 is bent inward in the radial direction of the piston rod R, like the opening on the tip end side in the tip gripping portion 22.
- the inner diameter of the opening edge on the distal end side in the proximal end gripping portion 23 is larger than the inner diameter of the fitting hole 13H described above and smaller than the outer diameter of the proximal flange portion 13 described above.
- an annular pressing ridge CT extending toward the proximal end along the axial direction of the piston rod R is provided on the end face CS on the distal end side.
- the pressing protrusion CT is disposed outside the distal end opening end 22E in the radial direction so as to be separated from the distal end opening end 22E of the bladder 20.
- the protruding amount of the pressing protrusion CT having such a configuration is defined as follows.
- the front end side of the above-described front end sliding protrusion 22T is pressed by the pressing protrusion CT.
- the protruding amount of the pressing protrusion CT is defined.
- the bladder 20 is wound around the outer peripheral surface of the liner 10 that is externally fitted to the piston rod R.
- a seal ring SR that seals between the liner 10 and the piston rod R is fitted into the fitting hole 13H of the liner 10, and a cap CP is attached to the piston rod R on the proximal end side of the seal ring SR. It is inserted.
- the piston rod R is inserted into the cylinder C into which oil as fluid is injected into the small diameter portion C1 from the opening which is the base end of the cylinder C.
- the distal end gripping portion 22 of the bladder 20 slides on the inner peripheral surface of the large diameter portion C2 until the distal end opening end portion 22E of the bladder 20 contacts the end surface CS on the distal end side of the large diameter portion C2. Keep doing.
- the frictional force F in the direction opposite to the insertion direction in which the piston rod R is inserted continues to act on the tip gripping portion 22.
- the frictional force F increases as the force with which the tip gripping portion 22 presses the inner peripheral surface of the large diameter portion C2 increases, and the contact area between the tip gripping portion 22 and the large diameter portion C2 increases. The larger the area, the larger the area of action.
- the outer diameter DH of the tip sliding protrusion 22T is the same as the cylinder inner diameter DC of the large diameter portion C2, so that the tip sliding protrusion 22T has the large diameter portion C2.
- the pressing force is naturally small.
- the tip sliding protrusion 22T is in sliding contact with the inner peripheral surface of the large-diameter portion C2 on the tip side, while the other portion is in contact with the inner peripheral surface of the large-diameter portion C2. This makes it difficult for the bladder 20 to slide. Therefore, as compared with the configuration without the tip sliding protrusion 22T, it is possible to suppress the above-described frictional force F acting as a force for scooping the tip gripping portion 22, and to suppress it.
- the tip opening end 22E of the bladder 20 abuts on the end surface CS of the large diameter portion C2, and the cap CP is fitted into the cylinder C, whereby the accumulator constituted by the liner 10 and the bladder 20 is Fixed in C2.
- the tip sliding protrusion 22T is within the large diameter portion C2. The force that presses the peripheral surface is very small.
- the tip opening end 22E is pressed by the tip end face of the liner 10 and the end face CS of the large diameter portion C2.
- the tip side of the above-described tip sliding protrusion 22T is pressed by the pressing protrusion CT.
- the bladder 20 hardly presses the inner peripheral surface of the large-diameter portion C2
- it is between the tip sliding protrusion 22T and the pressing protrusion CT and between the tip opening end 22E and the end surface CS.
- the sealing performance between the distal end side of the large-diameter portion C2 and the bladder 20 is ensured.
- the sealing performance between the base end flange portion 13 and the large diameter portion C2 is ensured between the inner peripheral surface of the large diameter portion C2 and the base end sliding protrusion 23T.
- the sleeve portion 11, the distal end flange portion 12, the proximal end flange portion 13, and the bladder 20 define a third space S3 serving as a fluid chamber.
- the third space S3 communicates with the outside of the accumulator via the flow path 12H.
- the fourth space S4 serving as an air chamber is defined by the large-diameter portion C2, the distal end flange portion 12, the proximal end flange portion 13, and the bladder 20.
- the outside of the cylinder C communicates with the fourth space S4 through a communication hole CH formed in the large diameter portion C2.
- the effects listed below can be obtained.
- the protrusion outer diameter DH of the tip sliding protrusion 22T is the same as the cylinder inner diameter DC, the bladder 20 can be prevented from being displaced by the frictional force F.
- the pressing protrusion CT presses the distal sliding protrusion 22T toward the proximal end side at the distal end side of the large diameter portion C2. Therefore, the sealing property of the fluid chamber is ensured by the contact between the pressing protrusion CT and the tip sliding protrusion 22T. As a result, it is possible to suppress a decrease in the sealing performance of the fluid in the cylinder C.
- a pressing protrusion CT that protrudes toward the base end side of the large-diameter portion C2 is provided so as to protrude from the end face CS on the distal end side of the large-diameter portion C2.
- a front end retaining groove 12 ⁇ / b> G extending in the entire circumferential direction is recessed in the outer peripheral surface of the front end flange portion 12.
- the outer diameter on the distal end side with respect to the distal end retaining groove 12G is larger by the thickness of the bladder 20 than the outer diameter on the proximal end side with respect to the distal end retaining groove 12G.
- the shape of the pair of side walls sandwiching both axial sides of the piston rod R is different.
- the groove sidewall on the proximal end side is orthogonal to the axial direction of the piston rod R, while the groove sidewall on the distal end side is proximal to the groove opening from the groove bottom surface. It is formed in a tapered shape that tilts to the side.
- a base end latching groove is also provided in the outer peripheral surface of the base end flange portion 13 over the entire circumferential direction of the base end flange portion 13.
- the shape of the proximal end latching groove is symmetrical to the distal end latching groove 12G with respect to a plane orthogonal to the axial direction of the piston rod R.
- the distal end opening end portion 22 ⁇ / b> E over the entire circumferential direction of the opening portion is bent inward in the radial direction of the piston rod R.
- the pair of end faces sandwiching both axial sides of the piston rod R have different shapes. Specifically, of the pair of end surfaces described above, the end surface on the proximal end side is orthogonal to the axial direction of the piston rod R, while the end surface on the distal end side is inclined toward the proximal end from the outer surface toward the opening edge. It is formed in such a taper shape.
- a proximal end opening end portion that is bent inward in the radial direction of the piston rod R is also formed in the proximal end opening portion of the proximal end gripping portion 23.
- the relationship between the shape of the proximal end opening end and the shape of the distal end opening end 22E is a surface orthogonal to the axial direction of the piston rod R, as in the relationship between the distal end retaining groove 12G and the proximal end retaining groove. Is symmetric.
- an annular pressing ridge CT extending toward the proximal end along the axial direction of the piston rod R is provided on the above-described end surface CS on the distal end side.
- the inner diameter of the pressing ridge CT is substantially the same as the largest outer diameter at the distal flange portion 12, and the distal end portion of the distal flange portion 12 is fitted inside the pressing ridge CT.
- the protruding amount of the pressing protrusion CT having such a configuration is defined such that the tip side of the tip sliding protrusion 22T described above is pressed by the pressing protrusion CT.
- the distal end opening end portion 22E is latched to the distal end retaining groove 12G of the distal end flange portion 12. Then, the pair of end surfaces sandwiching both axial sides at the tip opening end 22E come into close contact with the pair of end surfaces sandwiching both axial sides at the tip latching groove 12G.
- the contact area between the tip flange portion 12 and the tip gripping portion 22 increases, and as a result, the gripping force of the tip flange portion 12 is strengthened, and the tip gripping portion 22 is further prevented from being bent. It becomes possible to do.
- the force with which the proximal flange portion 13 is gripped is also increased in the proximal flange portion 13.
- the distal end sliding portion of the distal end gripping portion 22 is displaced.
- the outer surface other than the ridge 22T and the outer surface on the distal end side of the distal flange portion 12 are substantially flush. Therefore, when the liner 10 is incorporated into the cylinder C, the tip of the tip gripping portion 22 is less likely to interfere with the inner peripheral surface of the large-diameter portion C2 in the axial direction of the piston rod R. It is possible to prevent the tip gripping portion 22 from being bent due to the interference.
- the effects listed below can be obtained.
- each of the four slits 12S is a notch extending along the axial direction of the piston rod R, and is continuous over the entire width of the tip flange portion 12 in the axial direction of the piston rod R. That is, the entire front end flange portion 12 is divided in the circumferential direction by the four slits 12S.
- each of the four tip flange pieces 12 ⁇ / b> B which is a divided portion of the tip flange portion 12, is connected in a cantilever shape at the tip portion of the sleeve portion 11.
- each of the four front end flange pieces 12B receives an external force toward the inside in the radial direction of the piston rod R, each of the four front end flange pieces 12B is formed between the front end flange piece 12B and the sleeve portion 11.
- the connecting portion becomes a fixed end and bends inward in the radial direction.
- such a frictional force F acts on the tip gripping portion 22 as a force for pinching the tip gripping portion 22, and also causes the tip flange portion 12 to move radially inside (through the tip gripping portion 22 ( This also acts on the tip flange portion 12 as a force for displacement in the direction of the arrow in FIG.
- each of the four tip flange pieces 12B constituting the tip flange portion 12 has a cantilever structure. Therefore, as compared with a configuration that does not have such a cantilever structure, the above-described frictional force F is easily converted into a force that bends the tip flange portion 12. Further, if the tip flange piece 12B bends, the contact area between the outer peripheral surface of the tip gripping portion 22 and the inner peripheral surface of the large diameter portion C2 is reduced, so that the frictional force F itself is held by the tip gripping portion. The action on the portion 22 is suppressed.
- the frictional force F described above acts as a force that squeezes the tip gripping portion 22 as much as the tip flange piece 12B is bent, and this is suppressed. It becomes possible. As a result, it is possible to suppress the tip gripping portion 22 from being detached from the tip flange portion 12.
- a plurality of distal end flange pieces 12B that press the distal end portion of the bladder 20 against the cylinder C are formed in the circumferential direction, and each of the plurality of distal end flange pieces 12B is supported at the proximal end. It is shaped like a cantilever. According to such a configuration, the frictional force F described above is converted into a force that bends the plurality of front end flange pieces 12B.
- each said embodiment can also be changed and implemented as follows.
- the protrusion outer diameter DH which is the outer diameter of the tip sliding protrusion 22T, may be smaller than the cylinder inner diameter DC, which is the inner diameter of the large diameter portion C2 (DH ⁇ DC). Even with such a configuration, it is possible to ensure the function as an accumulator as long as the sealing property between the bladder 20 and the large diameter portion C2 is ensured by the tip sliding protrusion 22T and the pressing protrusion CT. It is.
- the outer diameter DH of the protrusion which is the outer diameter of the tip sliding protrusion 22T, may be larger than the cylinder inner diameter DC, which is the inner diameter of the large diameter portion C2, (DH> DC).
- Any configuration may be used as long as the pressing ridge CT presses the tip sliding ridge 22T with a force larger than the force pressing the inner peripheral surface. Even in such a configuration, as long as the sealing performance between the bladder 20 and the large-diameter portion C2 is ensured by the tip sliding protrusion 22T and the pressing protrusion CT, the inner peripheral surface of the cylinder C and the tip sliding protrusion It is possible to suppress the adhesion with the strip 22T.
- the base end sliding protrusion 23T described above is omitted. There may be.
- the inner diameter of the cylinder C becomes smaller at the distal end side of the housing portion in which the accumulator is housed.
- the cylinder C is composed of the small-diameter portion C1 and the large-diameter portion C2.
- the above-described pressing protrusion CT may be configured to be a protrusion protruding into the cylinder C, and the proximal end side of the accommodating portion is disposed on the end surface of the accommodating portion where the accumulator is accommodated. What is necessary is just the cyclic
- the shape on the tip sliding ridge 22T side of the pressing ridge CT may be any shape as long as the pressing ridge CT is pressed against the tip sliding ridge 22T.
- the pressing protrusion CT and the tip sliding protrusion 22T are in point contact, the surface pressure on the surface in contact with the pressing protrusion CT and the tip sliding protrusion 22T is increased, and the sealing performance can be improved.
- the inner diameter of the pressing protrusion CT may be the same as the outer diameter of the tip of the accumulator, or may be larger than the outer diameter of the tip.
- the direction in which the pressing protrusion CT is extended may be a direction different from the axial direction of the piston rod R.
- the pressing protrusion CT has an inner diameter that decreases toward the base end of the large-diameter portion C2.
- a cylindrical shape or a cylindrical shape whose inner diameter increases toward the proximal end of the large-diameter portion C2 may be used.
- the pressing protrusion CT may have a shape that extends from the end surface CS of the large-diameter portion C2 toward the base end.
- tip latching grooves 12G There may be two or more tip latching grooves 12G formed in the tip flange portion 12. In this case, it is preferable that the protrusion hooked in each of the tip latching grooves 12G is formed on the inner peripheral surface of the tip gripping portion 22. With such a configuration, it is possible to further suppress the tip gripping portion 22 from falling.
- the number of slits 12S formed in the distal end flange portion 12 may be two or more, and the slits 12S may be equally arranged, and a cantilevered distal end flange piece 12B is formed. Any configuration may be used.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
A damper for circulating a fluid within a cylinder by allowing the fluid to flow in and out of a fluid chamber and for braking a piston rod by means of the fluid resistance of the fluid, wherein: a bladder has, on the tip, an annular tip-sliding protrusion of which the outer diameter becomes the largest at the bladder and which protrudes outward in the radial direction of the bladder; the cylinder has an inner diameter that is equal to or larger than the outer diameter of the tip-sliding protrusion at a large diameter section in which an accumulator is housed; and an annular pressing protrusion extending towards the base end side of the large diameter section and for pressing the tip-sliding protrusion towards the base end side is disposed on the edge surface on the tip of the large diameter section.
Description
本発明は、シリンダー内にアキュムレーターを有するダンパーに関するものであって、特に、ピストンロッドに外嵌された筒状のライナーにブラダが巻装されてなるアキュムレーターを有するダンパーに関するものである。
The present invention relates to a damper having an accumulator in a cylinder, and more particularly, to a damper having an accumulator in which a bladder is wound around a cylindrical liner fitted on a piston rod.
従来から、例えば特許文献1に記載のように、物体同士の衝撃力を緩和するダンパーが知られている。図4(a)は、ダンパーの内部構造を示す断面図であり、図4(b)は、ダンパーを構成するアキュムレーターがシリンダーに組み込まれる過程を説明する図である。
Conventionally, as described in Patent Document 1, for example, a damper that reduces the impact force between objects is known. FIG. 4A is a cross-sectional view showing the internal structure of the damper, and FIG. 4B is a diagram illustrating a process in which the accumulator constituting the damper is incorporated into the cylinder.
図4(a)に示されるように、有底の二段円筒状に形成されたシリンダーCの基端には、シリンダーCの内部に各構成部品を封入するためのキャップCPが嵌め込まれている。
このシリンダーCの内部には、シリンダーCの中心軸に沿って延びるピストンロッドRが、キャップCPを貫挿するように挿設されている。このピストンロッドRのうち、シリンダーCの小径部分C1内には、円柱状のピストンPが外嵌されて、また、ピストンロッドRのうち、シリンダーCの大径部分C2内には、大径部分C2内に位置決めされた糸巻き状のライナー50が外嵌されている。また、ピストンロッドRのうち、ライナー50の基端には、ライナー50とピストンロッドRとの間をシールするシールリングSRが外嵌されている。 As shown in FIG. 4A, a cap CP for enclosing each component inside the cylinder C is fitted into the base end of the cylinder C formed in a bottomed two-stage cylindrical shape. .
A piston rod R extending along the center axis of the cylinder C is inserted into the cylinder C so as to penetrate the cap CP. Of this piston rod R, a cylindrical piston P is fitted inside the small diameter portion C1 of the cylinder C, and among the piston rod R, the large diameter portion C2 of the cylinder C has a large diameter portion. A spool-shaped liner 50 positioned in C2 is fitted. In addition, a seal ring SR that seals between the liner 50 and the piston rod R is fitted on the base end of the liner 50 in the piston rod R.
このシリンダーCの内部には、シリンダーCの中心軸に沿って延びるピストンロッドRが、キャップCPを貫挿するように挿設されている。このピストンロッドRのうち、シリンダーCの小径部分C1内には、円柱状のピストンPが外嵌されて、また、ピストンロッドRのうち、シリンダーCの大径部分C2内には、大径部分C2内に位置決めされた糸巻き状のライナー50が外嵌されている。また、ピストンロッドRのうち、ライナー50の基端には、ライナー50とピストンロッドRとの間をシールするシールリングSRが外嵌されている。 As shown in FIG. 4A, a cap CP for enclosing each component inside the cylinder C is fitted into the base end of the cylinder C formed in a bottomed two-stage cylindrical shape. .
A piston rod R extending along the center axis of the cylinder C is inserted into the cylinder C so as to penetrate the cap CP. Of this piston rod R, a cylindrical piston P is fitted inside the small diameter portion C1 of the cylinder C, and among the piston rod R, the large diameter portion C2 of the cylinder C has a large diameter portion. A spool-
上記ピストンPは、小径部分C1の内周面を摺動可能な円筒状に形成され、小径部分C1の内部空間をピストンPの先端側とピストンPの基端側とに分割している。ピストンPは、ピストンロッドRの軸方向に延びる絞りPHを有することにより、ピストンPの先端側の空間とピストンPの基端側の空間との間で、所定の流体抵抗のもと、シリコンオイルを流通させる。
The piston P is formed in a slidable cylindrical shape on the inner peripheral surface of the small diameter portion C1, and the internal space of the small diameter portion C1 is divided into a distal end side of the piston P and a proximal end side of the piston P. The piston P has a throttle PH extending in the axial direction of the piston rod R, so that silicon oil is generated between the space on the tip end side of the piston P and the space on the base end side of the piston P under a predetermined fluid resistance. Circulate.
上記ライナー50のうち、ピストンロッドRの軸方向における中央には、円筒状のスリーブ部51がピストンロッドRに外嵌されている。スリーブ部51における軸方向の両端部には、スリーブ部51よりも大径の先端フランジ部52と、同じく、スリーブ部51よりも大径の基端フランジ部53とが連結されている。また、先端フランジ部52は、ピストンロッドRの軸方向に延びる流路52Hを有し、先端フランジ部52の先端側である小径部分C1内とスリーブ部51の径方向の外側との間でシリコンオイルを流通させる。
In the liner 50, a cylindrical sleeve portion 51 is fitted on the piston rod R at the center in the axial direction of the piston rod R. A distal end flange portion 52 having a diameter larger than that of the sleeve portion 51 and a proximal end flange portion 53 having a diameter larger than that of the sleeve portion 51 are connected to both end portions in the axial direction of the sleeve portion 51. Further, the front end flange portion 52 has a flow path 52H extending in the axial direction of the piston rod R, and silicon between the inside of the small diameter portion C1 which is the front end side of the front end flange portion 52 and the outside in the radial direction of the sleeve portion 51. Distribute the oil.
ライナー50の外周面には、該外周面の全体が覆われるように、ブラダ60が巻装されている。ブラダ60は、エラストマーや樹脂などから形成される弾性体であって、ピストンロッドRの軸方向に延びる糸巻き状に形成されている。このブラダ60における先端側の開口部は、ピストンロッドRの径方向の内側に折り曲げられて、流路52Hの先端側が開放されるように、先端フランジ部52の先端に掛け止めされている。また、ブラダ60における基端側の開口部は、これもまた径方向の内側に折り曲げられて、基端フランジ部53の基端に掛け止めされている。こうしたブラダ60のうち、一対のフランジ部52,53の外周面を覆う部位は、該外周面と大径部分C2の内周面とに押圧されている。そして、このような構成からなるダンパーでは、シリンダーC内の空間がピストンPとブラダ60とによって、下記四つの空間に分割される。
小径部分C1内のうち、ピストンPに対する先端側の空間(第一空間S1)。
小径部分C1内のうち、ピストンPに対する基端側の空間(第二空間S2)。
大径部分C2内のうち、ブラダ60の内側の空間(第三空間S3)。
大径部分C2内のうち、ブラダ60の外側の空間(第四空間S4)。 Abladder 60 is wound around the outer peripheral surface of the liner 50 so as to cover the entire outer peripheral surface. The bladder 60 is an elastic body formed of an elastomer, a resin, or the like, and is formed in a bobbin shape extending in the axial direction of the piston rod R. The opening on the distal end side of the bladder 60 is bent to the inside in the radial direction of the piston rod R, and is hooked to the distal end of the distal flange portion 52 so that the distal end side of the flow path 52H is opened. In addition, the opening on the base end side of the bladder 60 is also bent inward in the radial direction and is hooked to the base end of the base end flange portion 53. The part which covers the outer peripheral surface of a pair of flange parts 52 and 53 among such a bladder 60 is pressed by this outer peripheral surface and the inner peripheral surface of the large diameter part C2. In the damper having such a configuration, the space in the cylinder C is divided into the following four spaces by the piston P and the bladder 60.
A space on the tip side with respect to the piston P (first space S1) in the small diameter portion C1.
A space on the proximal end side with respect to the piston P (second space S2) in the small diameter portion C1.
A space (third space S3) inside thebladder 60 in the large-diameter portion C2.
A space outside the bladder 60 (fourth space S4) in the large-diameter portion C2.
小径部分C1内のうち、ピストンPに対する先端側の空間(第一空間S1)。
小径部分C1内のうち、ピストンPに対する基端側の空間(第二空間S2)。
大径部分C2内のうち、ブラダ60の内側の空間(第三空間S3)。
大径部分C2内のうち、ブラダ60の外側の空間(第四空間S4)。 A
A space on the tip side with respect to the piston P (first space S1) in the small diameter portion C1.
A space on the proximal end side with respect to the piston P (second space S2) in the small diameter portion C1.
A space (third space S3) inside the
A space outside the bladder 60 (fourth space S4) in the large-diameter portion C2.
上記第一空間S1と第二空間S2との間では、ピストンPの絞りPHを介し、所定の流体抵抗のもと、シリコンオイルが流通する。また、第二空間S2と第三空間S3との間では、流路52Hを介し、シリコンオイルが流通する。これに対して、第二空間S2と第四空間S4との間、及び第三空間S3と第四空間S4との間は、ブラダ60によって区画されている。
Between the first space S1 and the second space S2, silicon oil flows through the throttle PH of the piston P under a predetermined fluid resistance. Further, silicon oil circulates between the second space S2 and the third space S3 via the flow path 52H. On the other hand, the bladder 60 partitions the space between the second space S2 and the fourth space S4 and the space between the third space S3 and the fourth space S4.
そして、ピストンロッドRがシリンダーC内に押し込まれると、絞りPHにてシリコンオイルの流通が制限され、こうしたシリコンオイルの流体抵抗によって、ピストンロッドRが制動される。この際、第一空間S1の容積が減少するものの、こうした容積の変化は、ブラダ60がピストンロッドRの径方向の外側へ撓むことによって吸収される。また、ピストンロッドRがシリンダーC内から引き出されると、これもまたシリコンオイルの流体抵抗によって、ピストンロッドRが制動される。そして、第一空間S1の容積が拡大するものの、こうした容積の変化は、ブラダ60がピストンロッドRの径方向の内側へ撓むことによって吸収される。
When the piston rod R is pushed into the cylinder C, the flow of silicone oil is restricted by the restriction PH, and the piston rod R is braked by the fluid resistance of the silicone oil. At this time, although the volume of the first space S1 is reduced, such a change in volume is absorbed by the bladder 60 being bent outward in the radial direction of the piston rod R. When the piston rod R is pulled out from the cylinder C, the piston rod R is also braked by the fluid resistance of silicon oil. And although the volume of 1st space S1 expands, such a change of the volume is absorbed when the bladder 60 bends to the inner side of the radial direction of the piston rod R.
ところで、上述したライナー50とブラダ60とから構成されるアキュムレーターがシリンダーC内に組み込まれる過程では、図4(b)に示されるように、ピストンPとアキュムレーターとがピストンロッドRに外嵌された状態で、大径部分C2の内部にピストンロッドRが挿入される。この際、大径部分C2の内部にライナー50が固定されるまで、ブラダ60の先端側は、シリンダーCの内周面を摺動し続ける。
By the way, in the process in which the accumulator composed of the liner 50 and the bladder 60 is incorporated in the cylinder C, the piston P and the accumulator are fitted on the piston rod R as shown in FIG. In this state, the piston rod R is inserted into the large-diameter portion C2. At this time, the front end side of the bladder 60 continues to slide on the inner peripheral surface of the cylinder C until the liner 50 is fixed inside the large diameter portion C2.
一方、ブラダ60の先端側には、上述したように、第二空間S2と第三空間S3との間、及び第二空間S2と第四空間S4との間をシールする機能が必要とされる。それゆえに、先端フランジ部52の外周面と大径部分C2の内周面との間隔は、通常、これらのシールが確保されるべく、ブラダ60の先端側が径方向に押し潰されるように設計されている。しかしながら、このような設計のもと、ブラダ60がシリンダーCの内周面を摺動すると、ピストンロッドRが挿入される方向とは反対方向の大きな摩擦力Fが、ブラダ60に作用することとなる。その結果、ブラダ60のうち、先端フランジ部52に掛け止めされた部位(図4(b)の二点鎖線で囲まれた部位)が、先端フランジ部52から捲れてしまう場合がある。ひいては、ダンパーが組み立てられる過程において、第二空間S2と第三空間S3との間のシール性や第二空間S2と第四空間S4との間のシール性が失われる虞がある。
On the other hand, as described above, the front end side of the bladder 60 is required to have a function of sealing between the second space S2 and the third space S3 and between the second space S2 and the fourth space S4. . Therefore, the distance between the outer peripheral surface of the front end flange portion 52 and the inner peripheral surface of the large diameter portion C2 is usually designed such that the front end side of the bladder 60 is crushed in the radial direction so as to ensure these seals. ing. However, under such a design, when the bladder 60 slides on the inner peripheral surface of the cylinder C, a large frictional force F in the direction opposite to the direction in which the piston rod R is inserted acts on the bladder 60. Become. As a result, a portion of the bladder 60 that is hooked to the tip flange portion 52 (a portion surrounded by a two-dot chain line in FIG. 4B) may be bent from the tip flange portion 52. As a result, in the process of assembling the damper, the sealing property between the second space S2 and the third space S3 and the sealing property between the second space S2 and the fourth space S4 may be lost.
本発明は、こうした実情に鑑みてなされたものであり、その目的は、シリンダー内にて流体のシール性が低下することを抑えることの可能なダンパーを提供することにある。
The present invention has been made in view of such circumstances, and an object of the present invention is to provide a damper capable of suppressing a decrease in fluid sealing performance in a cylinder.
こうした目的を達成するため、本発明の第1観点によれば、ピストンロッドが貫挿されるキャップが基端に嵌め込まれたシリンダーと、該シリンダー内に収容されて前記ピストンロッドと同心の環状をなすアキュムレーターとを備え、前記アキュムレーターは、前記ピストンロッドに外嵌された糸巻き状の筒体であるライナーと、前記ライナーと前記シリンダーとの間に挟入され、前記ライナーの外周面と前記シリンダーの内周面との間の環状空間に容積の可変な流体室を区画する筒状のブラダとを備え、前記流体室に流体を流入及び流出させて前記シリンダー内で流体を流通させるとともに、該流体の流体抵抗によって前記ピストンロッドを制動するダンパーであって、前記ブラダは、該ブラダの径方向の外側に突出して該ブラダにて外径が最大となる環状の摺動突条を先端側に有し、前記シリンダーは、前記アキュムレーターの収容される収容部分にて前記摺動突条の外径以上の内径を有し、且つ該収容部分における先端側の端面には、前記収容部分の基端側に向けて突出して前記摺動突条を基端側へ押圧する環状の押圧突条を有するダンパーが提供される。
In order to achieve such an object, according to a first aspect of the present invention, a cylinder in which a cap into which a piston rod is inserted is fitted at a proximal end, and an annular concentric with the piston rod accommodated in the cylinder. An accumulator, the accumulator being pinched between the liner and the cylinder, the liner being a thread-wound cylindrical body fitted around the piston rod, and the outer peripheral surface of the liner and the cylinder A cylindrical bladder that divides a fluid chamber having a variable volume in an annular space between the inner circumferential surface and a fluid flowing in and out of the fluid chamber to circulate the fluid in the cylinder, A damper that brakes the piston rod by a fluid resistance of a fluid, wherein the bladder projects outward in a radial direction of the bladder and is The cylinder has an inner diameter that is greater than or equal to the outer diameter of the sliding protrusion at the accommodating portion where the accumulator is accommodated, and A damper having an annular pressing ridge that protrudes toward the proximal end side of the housing portion and presses the sliding ridge toward the proximal end side is provided on the end surface on the distal end side of the portion.
上述したダンパーの製造過程では、アキュムレーターがピストンロッドに外嵌された状態で、シリンダーの基端から該シリンダーの内部へピストンロッドが挿入されることになる。この際、アキュムレーターを構成するブラダの先端部がシリンダーの内周面を摺動するため、これに伴い、ブラダの先端部には、該ブラダの先端部を基端側にずらすような摩擦力が加わることになる。この点、本発明の第1観点によるダンバーによれば、収容部分の内径が摺動突条の外径以上であるため、アキュムレーターにおける先端側では、収容部分の内周面に対して上述した摺動突条のみが支配的に接触することとなる。それゆえに、上述した摺動突条と該摺動突条以外の部位とがシリンダーの内周面に接触する場合と比較して、ブラダとシリンダーとが互いに接触する面積を抑えることが可能である。その結果、ブラダの先端部を基端側へずらすような摩擦力がブラダに作用し続けることを抑えることが可能である。そのうえ、収容部分にアキュムレーターが配置された状態では、収容部分の先端側にて押圧突条が摺動突条を押圧することとなる。そのため、シリンダーの内周面と摺動突条との間には、相対的に高いシール性が得られがたいものの、これら環状の押圧突条と環状の摺動突条との接触によって、流体室のシール性が確保されるようになる。ひいては、シリンダー内にて流体のシール性が低下することを抑えることが可能である。
In the above-described damper manufacturing process, the piston rod is inserted from the base end of the cylinder into the cylinder while the accumulator is fitted on the piston rod. At this time, the front end of the bladder constituting the accumulator slides on the inner peripheral surface of the cylinder. Accordingly, the front end of the bladder has a frictional force that shifts the front end of the bladder toward the base end. Will be added. In this respect, according to the damper according to the first aspect of the present invention, since the inner diameter of the housing portion is equal to or larger than the outer diameter of the sliding protrusion, the above-described inner peripheral surface of the housing portion is described above on the tip side of the accumulator. Only the sliding ridge will come into contact predominantly. Therefore, it is possible to suppress the area in which the bladder and the cylinder are in contact with each other as compared with the case where the sliding protrusion and the portion other than the sliding protrusion are in contact with the inner peripheral surface of the cylinder. . As a result, it is possible to suppress the frictional force that shifts the distal end portion of the bladder toward the proximal end from continuing to act on the bladder. In addition, in a state where the accumulator is disposed in the housing portion, the pressing ridge presses the sliding ridge on the distal end side of the housing portion. Therefore, although it is difficult to obtain a relatively high sealing property between the inner peripheral surface of the cylinder and the sliding ridge, fluid contact is caused by contact between the annular pressing ridge and the annular sliding ridge. The sealing property of the chamber is ensured. As a result, it is possible to suppress a decrease in fluid sealing performance in the cylinder.
本発明の第2観点によれば、ピストンロッドが貫挿されるキャップが基端に嵌め込まれたシリンダーと、該シリンダー内に収容されて前記ピストンロッドと同心の環状をなすアキュムレーターとを備え、前記アキュムレーターは、前記ピストンロッドに外嵌された糸巻き状の筒体であるライナーと、前記ライナーと前記シリンダーとの間に挟入され、前記ライナーの外周面と前記シリンダーの内周面との間の環状空間に容積の可変な流体室を区画する筒状のブラダとを備え、前記流体室に流体を流入及び流出させて前記シリンダー内で流体を流通させるとともに、該流体の流体抵抗によって前記ピストンロッドを制動するダンパーであって、前記ブラダは、該ブラダの径方向の外側に突出して該ブラダにて外径が最大となる環状の摺動突条を先端側に有し、前記シリンダーは、前記アキュムレーターの収容される収容部分の先端側の端面に該収容部分の基端側に向けて突出して前記摺動突条を基端側へ押圧する環状の押圧突条を有し、前記押圧突条は、前記摺動突条が前記シリンダーの内周面を押圧する力よりも大きな力で前記摺動突条を押圧するダンパーが提供される。
According to a second aspect of the present invention, there is provided a cylinder in which a cap into which a piston rod is inserted is fitted at a base end, and an accumulator that is accommodated in the cylinder and has an annular shape concentric with the piston rod, The accumulator is inserted between the liner and the cylinder, the liner being a thread-wound cylindrical body fitted on the piston rod, and between the outer peripheral surface of the liner and the inner peripheral surface of the cylinder. A cylindrical bladder that divides a fluid chamber having a variable volume in the annular space, and causes the fluid to flow into and out of the fluid chamber to circulate the fluid in the cylinder, and the piston by the fluid resistance of the fluid A damper for braking a rod, wherein the bladder protrudes outward in the radial direction of the bladder and has an annular sliding protrusion whose outer diameter is maximized by the bladder. The cylinder has an annular shape that protrudes toward the proximal end side of the accommodating portion and pushes the sliding protrusion toward the proximal end side on the distal end side surface of the accommodating portion in which the accumulator is accommodated. There is provided a damper that presses the sliding protrusion with a force larger than a force with which the sliding protrusion presses the inner peripheral surface of the cylinder.
上述したように、ダンパーの製造過程では、ブラダの先端部に対して、該ブラダの先端部を基端側にずらすような摩擦力が加わることになる。この点、本発明の第2観点によるダンパーによれば、収容部分にアキュムレーターが配置された状態では、収容部分の先端側にて押圧突条が摺動突条を押圧する。そのため、これら環状の押圧突条と環状の摺動突条との接触によって、流体室のシール性が確保されるようになる。そして、摺動突条がシリンダーの内周面を押圧する力よりも大きな力によって、押圧突条が摺動突条を押圧することになる。そのため、摺動突条がシリンダーの内周面を押圧する力を抑えること、すなわち、上述した摩擦力を抑えることが可能となる。その結果、シリンダー内にて流体のシール性が低下することを抑えることが可能である。
As described above, in the damper manufacturing process, a frictional force is applied to the distal end portion of the bladder so as to shift the distal end portion of the bladder toward the proximal end side. In this regard, according to the damper according to the second aspect of the present invention, in the state where the accumulator is arranged in the housing portion, the pressing ridge presses the sliding ridge on the distal end side of the housing portion. Therefore, the sealing performance of the fluid chamber is ensured by the contact between the annular pressing protrusion and the annular sliding protrusion. Then, the pressing protrusion presses the sliding protrusion with a force larger than the force with which the sliding protrusion presses the inner peripheral surface of the cylinder. Therefore, it is possible to suppress the force with which the sliding protrusions press the inner peripheral surface of the cylinder, that is, to suppress the above-described frictional force. As a result, it is possible to suppress a decrease in fluid sealing performance in the cylinder.
本発明のダンパーにおいて、前記シリンダーには、前記収容部分よりも小さい内径を有する小径部分が、前記収容部分の先端側に該収容部分と同心に連結され、前記押圧突条は、前記ピストンロッドの軸方向に突出する環状の突条であって、前記小径部分が連結された前記収容部分の端面に突設されていることが好ましい。
In the damper of the present invention, the cylinder has a small-diameter portion having an inner diameter smaller than the accommodating portion connected to the distal end side of the accommodating portion concentrically with the accommodating portion, and the pressing ridge is formed on the piston rod. It is an annular ridge protruding in the axial direction, and is preferably provided on the end surface of the accommodating portion to which the small diameter portion is connected.
収容部分の先端側にてシリンダーの内径が小さくなる構成としては、収容部分よりも小さい内径を有する小径部分が、収容部分の先端側に連結されるという構成の他、径方向の内側に突出する突条が、シリンダーの内周面に形成されるという構成がある。ただし、径方向の内側に突出する突条が、シリンダーの内周面に形成されるという構成では、例えば、シリンダーを樹脂成形する際に、金型をシリンダーの基端側から引き抜くことが難しく、シリンダーそのものを一体的に製造することが困難となる。この点、上述した好ましい態様では、収容部分よりも小さい内径を有する小径部分が、収容部分の先端側に該収容部分と同心に連結される構成であって、且つ収容部分の基端側に向けて突出する押圧突条が、小径部分の連結された収容部分の端面に突設されている。このような構成によれば、シリンダーそのものを樹脂成形する際に、金型をシリンダーの基端側から引き抜くことが可能にもなる。それゆえに、ダンパーを構成する部材の点数やダンパーの製造に必要とされる時間を少なくすることが可能となる。
As a configuration in which the inner diameter of the cylinder becomes smaller at the distal end side of the housing portion, a small diameter portion having an inner diameter smaller than the housing portion is connected to the distal end side of the housing portion, and projects inward in the radial direction. There exists a structure that a protrusion is formed in the internal peripheral surface of a cylinder. However, in the configuration in which the ridge protruding inward in the radial direction is formed on the inner peripheral surface of the cylinder, for example, when resin molding the cylinder, it is difficult to pull out the mold from the base end side of the cylinder, It becomes difficult to manufacture the cylinder itself integrally. In this regard, in the preferred embodiment described above, the small-diameter portion having an inner diameter smaller than the housing portion is connected to the distal end side of the housing portion concentrically with the housing portion and toward the proximal end side of the housing portion. A pressing ridge protruding in a protruding manner is provided on the end face of the accommodating portion connected to the small diameter portion. According to such a configuration, when the cylinder itself is resin-molded, the mold can be pulled out from the base end side of the cylinder. Therefore, the number of members constituting the damper and the time required for manufacturing the damper can be reduced.
本発明の第2観点によるダンパーにおいて、前記摺動突条の先端側には、前記ブラダの先端側の開口縁が、径方向の内側に折り曲げられてなる開口端部が形成され、前記開口端部が、前記ライナーの先端側の端面に掛け止めされて、前記ライナーの先端側の端面と前記収容部分の先端側の端面との間に挟入されていることが好ましい。
In the damper according to the second aspect of the present invention, an opening end formed by bending an opening edge on the tip end side of the bladder radially inward is formed on the tip end side of the sliding protrusion. It is preferable that the portion is hooked to the end surface on the front end side of the liner and is sandwiched between the end surface on the front end side of the liner and the end surface on the front end side of the housing portion.
この好ましい態様では、ブラダにおける摺動突条が押圧突条によって押圧され、且つブラダにおける開口端部がライナーと収容部分との間に挟入される。そして、アキュムレーターの先端側では、これら摺動突条と開口端部との二カ所にて、ブラダとシリンダーとの間のシール性が確保される。その結果、シリンダー内にて流体のシール性が低下することをより確実に抑えることが可能である。
In this preferred embodiment, the sliding protrusion on the bladder is pressed by the pressing protrusion, and the opening end of the bladder is sandwiched between the liner and the accommodating portion. Then, on the front end side of the accumulator, the sealing performance between the bladder and the cylinder is ensured at two locations of the sliding protrusion and the opening end. As a result, it is possible to more reliably suppress a decrease in fluid sealing performance in the cylinder.
本発明のダンパーにおいて、前記ライナーは、前記ピストンロッドに外嵌されたスリーブ部を有し、前記スリーブ部は、前記ブラダの先端部を前記シリンダーに押圧する先端フランジ部を先端に有するとともに、前記ブラダの基端部を前記シリンダーに押圧する基端フランジ部を基端に有し、前記流体室は、前記スリーブ部と、前記先端フランジ部と、前記基端フランジ部と、前記ブラダとによって区画され、前記先端フランジ部は、該先端フランジ部の周方向の全体にわたり掛止溝を有し、前記ブラダの先端側の開口端部は、前記掛止溝に掛け止めされていることが好ましい。
In the damper of the present invention, the liner has a sleeve portion fitted on the piston rod, and the sleeve portion has a distal end flange portion that presses the distal end portion of the bladder against the cylinder at the distal end. A base end flange portion that presses the base end portion of the bladder against the cylinder is provided at the base end, and the fluid chamber is partitioned by the sleeve portion, the front end flange portion, the base end flange portion, and the bladder. Preferably, the distal end flange portion has a latching groove over the entire circumferential direction of the distal end flange portion, and the opening end portion on the distal end side of the bladder is latched by the latching groove.
この好ましい態様によれば、先端フランジ部の全体にわたる掛止溝にブラダの先端側の開口端部が掛け止めされるため、上述した摩擦力によるブラダの位置ずれをより発生し難くすることが可能である。
According to this preferable aspect, since the opening end portion on the distal end side of the bladder is latched in the retaining groove over the entire distal end flange portion, it is possible to make the position displacement of the bladder more difficult to occur due to the frictional force described above. It is.
本発明のダンパーにおいて、前記先端フランジ部が、前記ブラダの先端部を前記シリンダーに押圧する複数の先端フランジ片を先端に有し、前記複数の先端フランジ片が、該先端フランジ片の基端部にて支持される片持ち梁状に前記ライナーの周方向に配列されていることが好ましい。
In the damper of the present invention, the distal end flange portion has a plurality of distal end flange pieces that press the distal end portion of the bladder against the cylinder at the distal end, and the plurality of distal end flange pieces are proximal end portions of the distal end flange piece. It is preferable that the liner is arranged in the circumferential direction of the liner in the form of a cantilever that is supported by.
この好ましい態様によれば、ライナーの先端には、ブラダの先端部をシリンダーに押圧する複数の先端フランジ片が周方向に形成され、且つ複数の先端フランジ片の各々が、基端で支持された片持ち梁状に形成されている。このような構成によれば、上述した摩擦力が、複数の先端フランジ片を撓ませる力に変換されることとなる。そして、複数の先端フランジ片の各々が径方向の内側に撓むことによって、ライナーにおける先端部の外径が縮小するため、上述した摩擦力がブラダの先端部を基端側へずらす力として作用すること、それを抑えることが可能である。ひいては、シリンダー内にて流体のシール性が低下することを抑えることが可能である。
According to this preferred embodiment, the front end of the liner is formed with a plurality of front end flange pieces that press the front end of the bladder against the cylinder in the circumferential direction, and each of the front end flange pieces is supported at the base end. It is formed in a cantilever shape. According to such a structure, the frictional force mentioned above will be converted into the force which bends a some front-end | tip flange piece. Then, since the outer diameter of the front end portion of the liner is reduced by bending each of the plurality of front end flange pieces in the radial direction, the above-described frictional force acts as a force for shifting the front end portion of the bladder toward the base end side. It is possible to suppress it. As a result, it is possible to suppress a decrease in fluid sealing performance in the cylinder.
(第1実施形態)
以下、本発明のダンパーを具体化した第1実施形態について、図1を参照して説明する。本実施形態では、ダンパーが、住宅設備の引出しや扉等の開閉体と、開閉体を固定する固定側部材との間に架設され、開閉体と固定部材とが衝突する際の衝撃や騒音を緩衝するものとして説明する。 (First embodiment)
Hereinafter, a first embodiment in which the damper of the present invention is embodied will be described with reference to FIG. In this embodiment, the damper is installed between an opening / closing body such as a drawer or a door of a housing facility and a fixed-side member that fixes the opening / closing body, and the impact and noise when the opening / closing body and the fixing member collide with each other. Explanation will be made assuming that the buffering is performed.
以下、本発明のダンパーを具体化した第1実施形態について、図1を参照して説明する。本実施形態では、ダンパーが、住宅設備の引出しや扉等の開閉体と、開閉体を固定する固定側部材との間に架設され、開閉体と固定部材とが衝突する際の衝撃や騒音を緩衝するものとして説明する。 (First embodiment)
Hereinafter, a first embodiment in which the damper of the present invention is embodied will be described with reference to FIG. In this embodiment, the damper is installed between an opening / closing body such as a drawer or a door of a housing facility and a fixed-side member that fixes the opening / closing body, and the impact and noise when the opening / closing body and the fixing member collide with each other. Explanation will be made assuming that the buffering is performed.
図1に示されるように、ピストンロッドRに外嵌された樹脂製のライナー10には、糸巻き状のブラダ20が巻装されている。ブラダ20は、エラストマーや樹脂などからなる弾性体であって、ライナー10の外周面上では、ライナー10の全体を覆う一方、ピストンロッドRの軸方向では、ライナー10の両端部を開放するように形成されている。
As shown in FIG. 1, a thread-wound bladder 20 is wound around a resin liner 10 fitted on the piston rod R. The bladder 20 is an elastic body made of an elastomer or a resin, and covers the entire liner 10 on the outer peripheral surface of the liner 10, while opening both ends of the liner 10 in the axial direction of the piston rod R. Is formed.
糸巻き状の筒体であるライナー10の中心には、ピストンロッドRの貫挿されるロッド貫挿孔10Hが、ピストンロッドRの軸方向に沿って延びるように貫通している。また、ライナー10のうち、ピストンロッドRの軸方向における中央では、円筒状のスリーブ部11が、ピストンロッドRに外嵌されている。
A rod insertion hole 10H through which the piston rod R is inserted passes through the center of the liner 10 which is a pincushion-shaped cylinder so as to extend along the axial direction of the piston rod R. Further, in the liner 10, a cylindrical sleeve portion 11 is fitted on the piston rod R at the center in the axial direction of the piston rod R.
上記スリーブ部11のうち、ピストンロッドRの軸方向における一端部には、スリーブ部11の外径よりも大きな外径からなる円筒状の先端フランジ部12が、スリーブ部11と一体的に成形されている。先端フランジ部12は、ピストンロッドRの軸方向に延びる流路12Hを有し、先端フランジ部12の先端側である小径部分C1の内部とスリーブ部11の径方向の外側との間でシリコンオイルを流通させる。
A cylindrical tip flange portion 12 having an outer diameter larger than the outer diameter of the sleeve portion 11 is formed integrally with the sleeve portion 11 at one end portion in the axial direction of the piston rod R of the sleeve portion 11. ing. The distal end flange portion 12 has a flow path 12H extending in the axial direction of the piston rod R, and between the inside of the small diameter portion C1 on the distal end side of the distal end flange portion 12 and the radially outer side of the sleeve portion 11. Circulate.
また、スリーブ部11のうち、ピストンロッドRの軸方向における他端部には、スリーブ部11の外径よりも大きな外径からなる基端フランジ部13が、これもまた、スリーブ部11と一体的に成形されている。そして、このような外形を有したライナー10が、円筒状のシリンダーC内に配設されると、スリーブ部11の外周面とシリンダーCの内周面との間には、ピストンロッドRと同心の環状空間が、上記先端フランジ部12と基端フランジ部13とに挟まれるように形成される。
Further, in the sleeve portion 11, a proximal flange portion 13 having an outer diameter larger than the outer diameter of the sleeve portion 11 is also integrated with the sleeve portion 11 at the other end portion in the axial direction of the piston rod R. Molded. When the liner 10 having such an outer shape is disposed in the cylindrical cylinder C, the piston rod R is concentric between the outer peripheral surface of the sleeve portion 11 and the inner peripheral surface of the cylinder C. Is formed so as to be sandwiched between the distal end flange portion 12 and the proximal end flange portion 13.
なお、ピストンロッドRの軸方向のうち、スリーブ部11に対する先端フランジ部12の側を先端側とし、スリーブ部11に対する基端フランジ部13の側を基端側とする。
基端フランジ部13の基端部には、基端フランジ部13とピストンロッドRとの間をシールするシールリングSRを嵌め込むための嵌合孔13Hが、ピストンロッドRの軸方向に沿って延設されている。ライナー10に挿通されるピストンロッドRは、この嵌合孔13Hに嵌め込まれるシールリングSRを介して、ライナー10とのシール性を保ちつつ、ライナー10に対して軸方向へ移動する。 In the axial direction of the piston rod R, the side of the distalend flange portion 12 with respect to the sleeve portion 11 is defined as the distal end side, and the side of the proximal end flange portion 13 with respect to the sleeve portion 11 is defined as the proximal end side.
Afitting hole 13H for fitting a seal ring SR that seals between the proximal flange portion 13 and the piston rod R is formed in the proximal end portion of the proximal flange portion 13 along the axial direction of the piston rod R. It is extended. The piston rod R inserted through the liner 10 moves in the axial direction with respect to the liner 10 while maintaining the sealing performance with the liner 10 through the seal ring SR fitted in the fitting hole 13H.
基端フランジ部13の基端部には、基端フランジ部13とピストンロッドRとの間をシールするシールリングSRを嵌め込むための嵌合孔13Hが、ピストンロッドRの軸方向に沿って延設されている。ライナー10に挿通されるピストンロッドRは、この嵌合孔13Hに嵌め込まれるシールリングSRを介して、ライナー10とのシール性を保ちつつ、ライナー10に対して軸方向へ移動する。 In the axial direction of the piston rod R, the side of the distal
A
上述したライナー10に巻装されるブラダ20の外形は、上述したライナー10の外周面に倣うように糸巻き状に形成されている。このブラダ20のうち、ピストンロッドRの軸方向における中央には、ピストンロッドRの径方向の内側に撓んだ領域である伸縮部21が区画されている。伸縮部21は、径方向の内側に撓んだ状態と、該状態から径方向の外側に変位した状態との間の遷移を許容する。この伸縮部21の先端側には、伸縮部21の内径よりも大きな内径からなる円筒状の先端掴持部22が、先端フランジ部12の外周面に密着するように区画されている。
The outer shape of the bladder 20 wound around the liner 10 is formed in a bobbin shape so as to follow the outer peripheral surface of the liner 10 described above. In the bladder 20, an expansion / contraction part 21, which is a region bent inward in the radial direction of the piston rod R, is defined in the center of the piston rod R in the axial direction. The stretchable part 21 allows a transition between a state bent inward in the radial direction and a state displaced from the state outward in the radial direction. A cylindrical tip gripping portion 22 having an inner diameter larger than the inner diameter of the extension / contraction portion 21 is partitioned at the tip end side of the extension / contraction portion 21 so as to be in close contact with the outer peripheral surface of the tip flange portion 12.
先端掴持部22の内径は、先端フランジ部12の外径よりも小さく、これにより、先端掴持部22は、径方向の内側に収縮する収縮力を有した状態で、上記先端フランジ部12を掴持するようになる。また、先端掴持部22における先端側の開口部である先端開口端部22Eは、ピストンロッドRにおける径方向の内側へ折り曲げられている。先端開口端部22Eの内径である開口内径DLは、上述した小径部分C1の内径よりも小さい。このような構成によれば、先端掴持部22における先端開口端部22Eは、先端フランジ部12における先端側の端面に掛け止められる。そして、掛け止めされた先端開口端部22Eは、収容部分である大径部分C2の先端側の端面CSと、先端フランジ部12における先端側の端面とによって押圧されることになる。
The inner diameter of the distal end gripping portion 22 is smaller than the outer diameter of the distal end flange portion 12, so that the distal end gripping portion 22 has a contracting force that contracts inward in the radial direction, and the distal end flange portion 12. To come to grip. Further, a tip opening end portion 22 </ b> E which is an opening portion on the tip end side in the tip gripping portion 22 is bent inward in the radial direction of the piston rod R. The opening inner diameter DL, which is the inner diameter of the tip opening end 22E, is smaller than the inner diameter of the small-diameter portion C1 described above. According to such a configuration, the distal end opening end portion 22E of the distal end gripping portion 22 is latched to the end face on the distal end side of the distal end flange portion 12. Then, the hooked tip opening end 22E is pressed by the tip end surface CS of the large diameter portion C2 that is the housing portion and the tip end surface of the tip flange portion 12.
先端掴持部22の外周面には、径方向の外側に突出する突条である先端摺動突条22Tが、先端掴持部22の周方向の全体にわたり凸設されている。先端摺動突条22Tは、ピストンロッドRの軸方向を含む断面にて円弧状に形成され、また、ピストンロッドRの軸方向における先端掴持部22の先端よりも若干基端側となる部位に配設されている。この先端摺動突条22Tの外径である突条外径DHは、ブラダ20における他の部位の外径DBよりも大きく、大径部分C2の内径であるシリンダー内径DCと同じである。
On the outer peripheral surface of the tip gripping portion 22, a tip sliding ridge 22 </ b> T, which is a ridge protruding outward in the radial direction, is provided so as to protrude over the entire circumferential direction of the tip gripping portion 22. The tip sliding protrusion 22T is formed in an arc shape in a cross section including the axial direction of the piston rod R, and is a portion slightly proximal to the tip of the tip gripping portion 22 in the axial direction of the piston rod R. It is arranged. The outer diameter DH, which is the outer diameter of the tip sliding protrusion 22T, is larger than the outer diameter DB of the other part of the bladder 20 and is the same as the cylinder inner diameter DC, which is the inner diameter of the large diameter portion C2.
上記伸縮部21の基端側には、伸縮部21の内径よりも大きな内径からなる円筒状の基端掴持部23が、基端フランジ部13の外周面に密着するように区画されている。基端掴持部23の内径は、基端フランジ部13の外径よりも小さく、これにより、基端掴持部23は、径方向の内側に収縮する収縮力を有した状態で基端フランジ部13を掴持するようになる。また、基端掴持部23の外周面には、径方向の外側に突出する突条である基端摺動突条23Tが、基端掴持部23の周方向の全体にわたり凸設されている。基端摺動突条23Tの外表面は、先端摺動突条22Tと同じく、ピストンロッドRの軸方向を含む断面にて円弧状に形成され、また、ピストンロッドRの軸方向における基端掴持部23の基端よりも若干先端側となる部位に配設されている。この基端摺動突条23Tの外径は、上述した先端摺動突条22Tの突条外径DHよりも大きく、シリンダー内径DCよりも大きい。
On the base end side of the stretchable portion 21, a cylindrical base end gripping portion 23 having an inner diameter larger than the inner diameter of the stretchable portion 21 is partitioned so as to be in close contact with the outer peripheral surface of the base end flange portion 13. . The inner diameter of the proximal end gripping portion 23 is smaller than the outer diameter of the proximal end flange portion 13, so that the proximal end gripping portion 23 has a contracting force that contracts radially inward, and thus the proximal end flange 23 The part 13 is gripped. Further, on the outer peripheral surface of the base end gripping portion 23, a base end sliding protrusion 23T, which is a protrusion protruding outward in the radial direction, is provided so as to protrude over the entire circumferential direction of the base end gripping portion 23. Yes. The outer surface of the proximal end sliding protrusion 23T is formed in an arc shape in a cross section including the axial direction of the piston rod R, and the proximal end gripping in the axial direction of the piston rod R is the same as the distal end sliding protrusion 22T. The holding portion 23 is disposed at a position slightly closer to the distal end side than the proximal end. The outer diameter of the base end sliding protrusion 23T is larger than the protrusion outer diameter DH of the above-described distal end sliding protrusion 22T and larger than the cylinder inner diameter DC.
また、基端掴持部23における基端側の開口部は、先端掴持部22における先端側の開口部と同じく、ピストンロッドRにおける径方向の内側へ折り曲げられている。基端掴持部23における先端側の開口縁の内径は、上述した嵌合孔13Hの内径よりも大きく、且つ上述した基端フランジ部13の外径よりも小さい。これにより、基端掴持部における基端側の開口部は、基端フランジ部13における基端側の端面に掛け止めされるようになる。
Further, the opening on the base end side in the base end gripping portion 23 is bent inward in the radial direction of the piston rod R, like the opening on the tip end side in the tip gripping portion 22. The inner diameter of the opening edge on the distal end side in the proximal end gripping portion 23 is larger than the inner diameter of the fitting hole 13H described above and smaller than the outer diameter of the proximal flange portion 13 described above. Thereby, the opening part of the base end side in a base end holding part comes to be latched by the end surface of the base end side in the base end flange part 13. FIG.
大径部分C2の内側面のうち、上述した先端側の端面CSには、ピストンロッドRの軸方向に沿って基端側に延びる環状の押圧突条CTが突設されている。押圧突条CTは、ブラダ20の先端開口端部22Eから離間するように、該先端開口端部22Eの径方向の外側に配設されている。このような構成からなる押圧突条CTの突出する量は、以下のように規定されている。すなわち、ライナー10における先端側の端面と大径部分C2の端面CSとによって先端開口端部22Eが押圧される状態では、上述した先端摺動突条22Tの先端側が押圧突条CTによって押圧されるように、上記押圧突条CTの突出量が規定されている。
Of the inner surface of the large-diameter portion C2, an annular pressing ridge CT extending toward the proximal end along the axial direction of the piston rod R is provided on the end face CS on the distal end side. The pressing protrusion CT is disposed outside the distal end opening end 22E in the radial direction so as to be separated from the distal end opening end 22E of the bladder 20. The protruding amount of the pressing protrusion CT having such a configuration is defined as follows. That is, in the state where the end opening end 22E is pressed by the end surface on the front end side of the liner 10 and the end surface CS of the large-diameter portion C2, the front end side of the above-described front end sliding protrusion 22T is pressed by the pressing protrusion CT. As described above, the protruding amount of the pressing protrusion CT is defined.
次に、上述した構成からなるダンパーの作用のうち、特に、シリンダーC内にアキュムレーターが組み込まれる際の作用を説明する。
上述したダンパーが組み立てられる際には、まず、ピストンロッドRに外嵌されたライナー10の外周面に、ブラダ20が巻装される。次いで、同ライナー10の嵌合孔13Hには、ライナー10とピストンロッドRとの間をシールするシールリングSRが嵌め込まれ、さらに、シールリングSRの基端側のピストンロッドRに、キャップCPが貫挿される。そして、流体としてのオイルが小径部分C1に注入されたシリンダーCに対し、該シリンダーCの基端である開口部からピストンロッドRが挿入される。 Next, among the actions of the damper having the above-described configuration, particularly the action when the accumulator is incorporated in the cylinder C will be described.
When the above-described damper is assembled, first, thebladder 20 is wound around the outer peripheral surface of the liner 10 that is externally fitted to the piston rod R. Next, a seal ring SR that seals between the liner 10 and the piston rod R is fitted into the fitting hole 13H of the liner 10, and a cap CP is attached to the piston rod R on the proximal end side of the seal ring SR. It is inserted. Then, the piston rod R is inserted into the cylinder C into which oil as fluid is injected into the small diameter portion C1 from the opening which is the base end of the cylinder C.
上述したダンパーが組み立てられる際には、まず、ピストンロッドRに外嵌されたライナー10の外周面に、ブラダ20が巻装される。次いで、同ライナー10の嵌合孔13Hには、ライナー10とピストンロッドRとの間をシールするシールリングSRが嵌め込まれ、さらに、シールリングSRの基端側のピストンロッドRに、キャップCPが貫挿される。そして、流体としてのオイルが小径部分C1に注入されたシリンダーCに対し、該シリンダーCの基端である開口部からピストンロッドRが挿入される。 Next, among the actions of the damper having the above-described configuration, particularly the action when the accumulator is incorporated in the cylinder C will be described.
When the above-described damper is assembled, first, the
この際、ブラダ20における先端開口端部22Eが、大径部分C2の先端側の端面CSに当接するまでは、ブラダ20の先端掴持部22が、大径部分C2の内周面を摺動し続ける。そして、ピストンロッドRが挿入される挿入方向とは反対方向の摩擦力Fが、この先端掴持部22に作用し続ける。一方、このような摩擦力Fは、先端掴持部22が大径部分C2の内周面を押圧する力が大きくなるほど大きくなり、また先端掴持部22と大径部分C2との接触面積が大きくなるほど、その作用する領域が大きくなる。この点、上述したダンパーにおいては、先端摺動突条22Tの突条外径DHが、大径部分C2のシリンダー内径DCと同じであるため、こうした先端摺動突条22Tが大径部分C2を押圧する力も自ずと小さいものとなる。また、ブラダ20の外周面のうち、その先端側では、先端摺動突条22Tが大径部分C2の内周面と摺接する一方、その他の部位では、大径部分C2の内周面に対してブラダ20が摺接し難くなる。そのため、こうした先端摺動突条22Tを有しない構成と比較して、上述した摩擦力Fが先端掴持部22を捲る力として作用すること、それを抑えることが可能となる。
At this time, the distal end gripping portion 22 of the bladder 20 slides on the inner peripheral surface of the large diameter portion C2 until the distal end opening end portion 22E of the bladder 20 contacts the end surface CS on the distal end side of the large diameter portion C2. Keep doing. The frictional force F in the direction opposite to the insertion direction in which the piston rod R is inserted continues to act on the tip gripping portion 22. On the other hand, the frictional force F increases as the force with which the tip gripping portion 22 presses the inner peripheral surface of the large diameter portion C2 increases, and the contact area between the tip gripping portion 22 and the large diameter portion C2 increases. The larger the area, the larger the area of action. In this regard, in the above-described damper, the outer diameter DH of the tip sliding protrusion 22T is the same as the cylinder inner diameter DC of the large diameter portion C2, so that the tip sliding protrusion 22T has the large diameter portion C2. The pressing force is naturally small. Of the outer peripheral surface of the bladder 20, the tip sliding protrusion 22T is in sliding contact with the inner peripheral surface of the large-diameter portion C2 on the tip side, while the other portion is in contact with the inner peripheral surface of the large-diameter portion C2. This makes it difficult for the bladder 20 to slide. Therefore, as compared with the configuration without the tip sliding protrusion 22T, it is possible to suppress the above-described frictional force F acting as a force for scooping the tip gripping portion 22, and to suppress it.
そして、ブラダ20における先端開口端部22Eが大径部分C2の端面CSに当接し、キャップCPがシリンダーCに嵌め込まれることによって、ライナー10とブラダ20とから構成されるアキュムレーターが、大径部分C2内に固定される。この際、上述したように、先端摺動突条22Tの突条外径DHと大径部分C2のシリンダー内径DCとが互いに同じであるため、先端摺動突条22Tが大径部分C2の内周面を押圧する力は、非常に小さいものとなる。一方、先端開口端部22Eは、ライナー10における先端側の端面と大径部分C2の端面CSとによって押圧されることになる。また、これに加えて、上述した先端摺動突条22Tの先端側が押圧突条CTによって押圧されるようになる。その結果、ブラダ20が大径部分C2の内周面を殆ど押圧しない状態であっても、先端摺動突条22Tと押圧突条CTとの間、及び先端開口端部22Eと端面CSとの間、これらにおいて、大径部分C2の先端側とブラダ20との間のシール性が確保されることとなる。なお、基端フランジ部13と大径部分C2との間のシール性は、大径部分C2の内周面と基端摺動突条23Tとの間で確保されるようになる。
Then, the tip opening end 22E of the bladder 20 abuts on the end surface CS of the large diameter portion C2, and the cap CP is fitted into the cylinder C, whereby the accumulator constituted by the liner 10 and the bladder 20 is Fixed in C2. At this time, as described above, since the protrusion outer diameter DH of the tip sliding protrusion 22T and the cylinder inner diameter DC of the large diameter portion C2 are the same, the tip sliding protrusion 22T is within the large diameter portion C2. The force that presses the peripheral surface is very small. On the other hand, the tip opening end 22E is pressed by the tip end face of the liner 10 and the end face CS of the large diameter portion C2. In addition to this, the tip side of the above-described tip sliding protrusion 22T is pressed by the pressing protrusion CT. As a result, even when the bladder 20 hardly presses the inner peripheral surface of the large-diameter portion C2, it is between the tip sliding protrusion 22T and the pressing protrusion CT and between the tip opening end 22E and the end surface CS. In these cases, the sealing performance between the distal end side of the large-diameter portion C2 and the bladder 20 is ensured. In addition, the sealing performance between the base end flange portion 13 and the large diameter portion C2 is ensured between the inner peripheral surface of the large diameter portion C2 and the base end sliding protrusion 23T.
このようにして、先端フランジ部12と大径部分C2との間、及び基端フランジ部13と大径部分C2との間がシールされると、ライナー10の外周面とシリンダーCの内周面との間に形成された環状空間が、上述したブラダ20によって二層の環状に分割される。
In this way, when the gap between the distal end flange portion 12 and the large diameter portion C2 and the gap between the proximal end flange portion 13 and the large diameter portion C2 are sealed, the outer peripheral surface of the liner 10 and the inner peripheral surface of the cylinder C are sealed. The annular space formed between the two is divided into two layers by the bladder 20 described above.
具体的には、スリーブ部11、先端フランジ部12、基端フランジ部13、及びブラダ20によって、流体室となる第三空間S3が区画される。なお、この第三空間S3は、流路12Hを介してアキュムレーターの外側と連通するようになる。また、このような第三空間S3の他、大径部分C2、先端フランジ部12、基端フランジ部13、及びブラダ20によって、空気室となる第四空間S4が区画される。この第四空間S4に対しては、大径部分C2に形成された連通孔CHを介して、シリンダーCの外側が連通するようになる。
Specifically, the sleeve portion 11, the distal end flange portion 12, the proximal end flange portion 13, and the bladder 20 define a third space S3 serving as a fluid chamber. The third space S3 communicates with the outside of the accumulator via the flow path 12H. In addition to the third space S3, the fourth space S4 serving as an air chamber is defined by the large-diameter portion C2, the distal end flange portion 12, the proximal end flange portion 13, and the bladder 20. The outside of the cylinder C communicates with the fourth space S4 through a communication hole CH formed in the large diameter portion C2.
そして、このようにして組み立てられたダンパーにて、ピストンロッドRがシリンダーC内に押し込まれると、シリコンオイルの流体抵抗によって、ピストンロッドRが制動される。この際、シリンダーC内のシリコンオイルの一部が、上述したスリット12Sを介して第三空間S3に流入し、第三空間S3が大きくなることによって、小径部分C1内における容積の変化がアキュムレーターに吸収される。また、ピストンロッドRがシリンダーC内から引き出されると、これもまたシリコンオイルの流体抵抗によって、ピストンロッドRが制動される。そして、シリンダーC内のシリコンオイルの一部が、上述したスリット12Sを介して第三空間S3から流出し、第三空間S3が小さくなることによって、小径部分C1内における容積の変化がアキュムレーターに吸収される。
When the piston rod R is pushed into the cylinder C by the damper thus assembled, the piston rod R is braked by the fluid resistance of silicon oil. At this time, a part of the silicon oil in the cylinder C flows into the third space S3 through the slit 12S described above, and the third space S3 becomes larger, so that the volume change in the small diameter portion C1 is changed. To be absorbed. When the piston rod R is pulled out from the cylinder C, the piston rod R is also braked by the fluid resistance of silicon oil. Then, a part of the silicon oil in the cylinder C flows out from the third space S3 through the slit 12S described above, and the third space S3 becomes smaller, so that the change in volume in the small diameter portion C1 becomes an accumulator. Absorbed.
以上、第1実施形態によれば、以下に列記するような効果が得られるようになる。
(1)先端摺動突条22Tにおける突条外径DHがシリンダー内径DCと同じであるため、ブラダ20が摩擦力Fによってずれることを抑えることが可能である。そのうえ、大径部分C2にアキュムレーターが位置決めされた状態では、大径部分C2の先端側にて、押圧突条CTが先端摺動突条22Tを基端側へ押圧するようになる。そのため、押圧突条CTと先端摺動突条22Tとの接触によって、流体室のシール性が確保されるようになる。ひいては、シリンダーC内における流体のシール性の低下を抑えることが可能である。 As described above, according to the first embodiment, the effects listed below can be obtained.
(1) Since the protrusion outer diameter DH of thetip sliding protrusion 22T is the same as the cylinder inner diameter DC, the bladder 20 can be prevented from being displaced by the frictional force F. In addition, in a state where the accumulator is positioned at the large diameter portion C2, the pressing protrusion CT presses the distal sliding protrusion 22T toward the proximal end side at the distal end side of the large diameter portion C2. Therefore, the sealing property of the fluid chamber is ensured by the contact between the pressing protrusion CT and the tip sliding protrusion 22T. As a result, it is possible to suppress a decrease in the sealing performance of the fluid in the cylinder C.
(1)先端摺動突条22Tにおける突条外径DHがシリンダー内径DCと同じであるため、ブラダ20が摩擦力Fによってずれることを抑えることが可能である。そのうえ、大径部分C2にアキュムレーターが位置決めされた状態では、大径部分C2の先端側にて、押圧突条CTが先端摺動突条22Tを基端側へ押圧するようになる。そのため、押圧突条CTと先端摺動突条22Tとの接触によって、流体室のシール性が確保されるようになる。ひいては、シリンダーC内における流体のシール性の低下を抑えることが可能である。 As described above, according to the first embodiment, the effects listed below can be obtained.
(1) Since the protrusion outer diameter DH of the
また、上述のように、ブラダ20が摩擦力Fによってずれることを抑えることが可能であるため、ダンパーの組み立て時におけるブラダ20の捲れの発生が抑えられる。それゆえに、歩留まりを改善してコストダウンを図ることも可能である。
Moreover, since it is possible to suppress the displacement of the bladder 20 due to the frictional force F as described above, the occurrence of bending of the bladder 20 during assembly of the damper can be suppressed. Therefore, it is possible to improve the yield and reduce the cost.
(2)大径部分C2の基端側に向けて突出する押圧突条CTが、大径部分C2の先端側の端面CSに突設されている。このような構成によれば、シリンダーCそのものを樹脂成形する際に、シリンダーCの基端側から金型を引き抜くことが可能にもなる。それゆえに、ダンパーを構成する部材の点数やダンパーの製造に必要とされる時間を少なくすることが可能となる。
(2) A pressing protrusion CT that protrudes toward the base end side of the large-diameter portion C2 is provided so as to protrude from the end face CS on the distal end side of the large-diameter portion C2. According to such a structure, when the cylinder C itself is resin-molded, the mold can be pulled out from the base end side of the cylinder C. Therefore, the number of members constituting the damper and the time required for manufacturing the damper can be reduced.
(3)ブラダ20における先端開口端部22Eが、ライナー10と大径部分C2との間に挟入される。このような構成によれば、先端摺動突条22Tの他、先端開口端部22Eにおいても、ブラダ20とシリンダーCとの間のシール性が確保される。その結果、シリンダーC内にて流体のシール性が低下することをより確実に抑えることが可能である。
(3) The tip opening end 22E of the bladder 20 is sandwiched between the liner 10 and the large diameter portion C2. According to such a configuration, the sealing performance between the bladder 20 and the cylinder C is ensured not only at the tip sliding protrusion 22T but also at the tip opening end 22E. As a result, it is possible to more reliably suppress a decrease in fluid sealing performance in the cylinder C.
(第2実施形態)
以下、本発明のダンパーを具体化した第2実施形態について、図2を参照して説明する。なお、第2実施形態では、先端フランジ部12、基端フランジ部13、先端掴持部22、及び基端掴持部23、これらの構造が、第1実施形態とは異なる。そのため、以下では、これらの構造について主に説明し、第1実施形態と同一部分については、それらの説明を割愛する。 (Second Embodiment)
Hereinafter, a second embodiment in which the damper of the present invention is embodied will be described with reference to FIG. In the second embodiment, the distalend flange portion 12, the proximal end flange portion 13, the distal end gripping portion 22, and the proximal end gripping portion 23, and their structures are different from those in the first embodiment. Therefore, below, these structures are mainly demonstrated and those description is abbreviate | omitted about the same part as 1st Embodiment.
以下、本発明のダンパーを具体化した第2実施形態について、図2を参照して説明する。なお、第2実施形態では、先端フランジ部12、基端フランジ部13、先端掴持部22、及び基端掴持部23、これらの構造が、第1実施形態とは異なる。そのため、以下では、これらの構造について主に説明し、第1実施形態と同一部分については、それらの説明を割愛する。 (Second Embodiment)
Hereinafter, a second embodiment in which the damper of the present invention is embodied will be described with reference to FIG. In the second embodiment, the distal
図2に示されるように、先端フランジ部12の外周面には、周方向の全体にわたる先端掛止溝12Gが凹設されている。先端フランジ部12においては、上記先端掛止溝12Gに対する先端側の外径が、該先端掛止溝12Gに対する基端側の外径よりもブラダ20の厚さだけ大きい。また、この先端掛止溝12Gのうち、ピストンロッドRの軸方向の両側を挟む一対の溝側壁では、その形状が互いに異なる。具体的には、上述した一対の溝側壁のうち、基端側の溝側壁は、ピストンロッドRの軸方向と直交する一方、先端側の溝側壁は、溝底面から溝開口に向けて基端側に傾くようなテーパ状に形成されている。
As shown in FIG. 2, a front end retaining groove 12 </ b> G extending in the entire circumferential direction is recessed in the outer peripheral surface of the front end flange portion 12. In the distal end flange portion 12, the outer diameter on the distal end side with respect to the distal end retaining groove 12G is larger by the thickness of the bladder 20 than the outer diameter on the proximal end side with respect to the distal end retaining groove 12G. Further, in the tip engaging groove 12G, the shape of the pair of side walls sandwiching both axial sides of the piston rod R is different. Specifically, of the pair of groove sidewalls described above, the groove sidewall on the proximal end side is orthogonal to the axial direction of the piston rod R, while the groove sidewall on the distal end side is proximal to the groove opening from the groove bottom surface. It is formed in a tapered shape that tilts to the side.
なお、基端フランジ部13の外周面にも、基端フランジ部13の周方向の全体にわたり、基端掛止溝が凹設されている。この基端掛止溝の形状は、ピストンロッドRの軸方向と直交する面に対して、先端掛止溝12Gと対称である。
In addition, a base end latching groove is also provided in the outer peripheral surface of the base end flange portion 13 over the entire circumferential direction of the base end flange portion 13. The shape of the proximal end latching groove is symmetrical to the distal end latching groove 12G with respect to a plane orthogonal to the axial direction of the piston rod R.
先端掴持部22における先端側の開口部では、該開口部の周方向の全体にわたる先端開口端部22Eが、ピストンロッドRにおける径方向の内側へ折り曲げられている。先端開口端部22Eのうち、ピストンロッドRの軸方向の両側を挟む一対の端面では、その形状が互いに異なる。具体的には、上述した一対の端面のうち、基端側の端面は、ピストンロッドRの軸方向と直交する一方、先端側の端面は、外表面から開口縁に向けて基端側に傾くようなテーパ状に形成されている。
In the opening portion on the distal end side of the distal end gripping portion 22, the distal end opening end portion 22 </ b> E over the entire circumferential direction of the opening portion is bent inward in the radial direction of the piston rod R. Of the tip opening end 22E, the pair of end faces sandwiching both axial sides of the piston rod R have different shapes. Specifically, of the pair of end surfaces described above, the end surface on the proximal end side is orthogonal to the axial direction of the piston rod R, while the end surface on the distal end side is inclined toward the proximal end from the outer surface toward the opening edge. It is formed in such a taper shape.
なお、基端掴持部23における基端側の開口部にも、ピストンロッドRにおける径方向の内側へ折り曲げられた基端開口端部が形成されている。この基端開口端部の形状と先端開口端部22Eの形状との関係は、上述した先端掛止溝12Gと基端掛止溝との関係と同じく、ピストンロッドRの軸方向と直交する面に対して対称である。
A proximal end opening end portion that is bent inward in the radial direction of the piston rod R is also formed in the proximal end opening portion of the proximal end gripping portion 23. The relationship between the shape of the proximal end opening end and the shape of the distal end opening end 22E is a surface orthogonal to the axial direction of the piston rod R, as in the relationship between the distal end retaining groove 12G and the proximal end retaining groove. Is symmetric.
一方、大径部分C2の内側面のうち、上述した先端側の端面CSには、ピストンロッドRの軸方向に沿って基端側に延びる環状の押圧突条CTが突設されている。押圧突条CTの内径は、先端フランジ部12にて最も大きい外径と略同じであり、押圧突条CTの内側には、先端フランジ部12の先端部が嵌め込まれている。このような構成からなる押圧突条CTの突出する量は、上述した先端摺動突条22Tの先端側が押圧突条CTによって押圧されるように規定されている。
On the other hand, of the inner surface of the large-diameter portion C2, an annular pressing ridge CT extending toward the proximal end along the axial direction of the piston rod R is provided on the above-described end surface CS on the distal end side. The inner diameter of the pressing ridge CT is substantially the same as the largest outer diameter at the distal flange portion 12, and the distal end portion of the distal flange portion 12 is fitted inside the pressing ridge CT. The protruding amount of the pressing protrusion CT having such a configuration is defined such that the tip side of the tip sliding protrusion 22T described above is pressed by the pressing protrusion CT.
次に、上述した構成からなるダンパーの作用のうち、特に、シリンダーC内にアキュムレーターが組み込まれる際の作用を説明する。
上述した構造からなる先端フランジ部12と先端掴持部22とによれば、先端開口端部22Eが先端フランジ部12の先端掛止溝12Gに掛け止めされる。そして、先端開口端部22Eにて軸方向の両側を挟む一対の端面が、同じく先端掛止溝12Gにて軸方向の両側を挟む一対の端面と密着するようになる。これによって、先端フランジ部12と先端掴持部22との接触する面積が大きくなる結果、先端フランジ部12の掴持される力が強められて、先端掴持部22が捲れることをさらに抑制することが可能となる。なお、基端フランジ部13においても同様に、基端フランジ部13の掴持される力が強められる。 Next, among the actions of the damper having the above-described configuration, particularly the action when the accumulator is incorporated in the cylinder C will be described.
According to the distalend flange portion 12 and the distal end gripping portion 22 having the above-described structure, the distal end opening end portion 22E is latched to the distal end retaining groove 12G of the distal end flange portion 12. Then, the pair of end surfaces sandwiching both axial sides at the tip opening end 22E come into close contact with the pair of end surfaces sandwiching both axial sides at the tip latching groove 12G. As a result, the contact area between the tip flange portion 12 and the tip gripping portion 22 increases, and as a result, the gripping force of the tip flange portion 12 is strengthened, and the tip gripping portion 22 is further prevented from being bent. It becomes possible to do. Similarly, the force with which the proximal flange portion 13 is gripped is also increased in the proximal flange portion 13.
上述した構造からなる先端フランジ部12と先端掴持部22とによれば、先端開口端部22Eが先端フランジ部12の先端掛止溝12Gに掛け止めされる。そして、先端開口端部22Eにて軸方向の両側を挟む一対の端面が、同じく先端掛止溝12Gにて軸方向の両側を挟む一対の端面と密着するようになる。これによって、先端フランジ部12と先端掴持部22との接触する面積が大きくなる結果、先端フランジ部12の掴持される力が強められて、先端掴持部22が捲れることをさらに抑制することが可能となる。なお、基端フランジ部13においても同様に、基端フランジ部13の掴持される力が強められる。 Next, among the actions of the damper having the above-described configuration, particularly the action when the accumulator is incorporated in the cylinder C will be described.
According to the distal
また、先端掛止溝12Gに対する先端側の外径が、該先端掛止溝12Gに対する基端側の外径よりもブラダ20の厚さだけ大きいため、先端掴持部22のうち、先端摺動突条22T以外の外表面と、先端フランジ部12のうち、先端側の外表面とが、略面一となる。
それゆえに、シリンダーC内にライナー10が組み込まれる際には、ピストンロッドRの軸方向において先端掴持部22の先端が、大径部分C2の内周面と干渉し難くすること、ひいては、こうした干渉に起因する先端掴持部22の捲れを抑えることが可能である。 In addition, since the outer diameter of the distal end side with respect to the distalend retaining groove 12G is larger than the outer diameter of the proximal end side with respect to the distal end retaining groove 12G by the thickness of the bladder 20, the distal end sliding portion of the distal end gripping portion 22 is displaced. The outer surface other than the ridge 22T and the outer surface on the distal end side of the distal flange portion 12 are substantially flush.
Therefore, when theliner 10 is incorporated into the cylinder C, the tip of the tip gripping portion 22 is less likely to interfere with the inner peripheral surface of the large-diameter portion C2 in the axial direction of the piston rod R. It is possible to prevent the tip gripping portion 22 from being bent due to the interference.
それゆえに、シリンダーC内にライナー10が組み込まれる際には、ピストンロッドRの軸方向において先端掴持部22の先端が、大径部分C2の内周面と干渉し難くすること、ひいては、こうした干渉に起因する先端掴持部22の捲れを抑えることが可能である。 In addition, since the outer diameter of the distal end side with respect to the distal
Therefore, when the
以上、第2実施形態によれば、上述した(1)~(3)に加えて、以下に列記するような効果が得られるようになる。
(4)先端フランジ部12の全体にわたる先端掛止溝12Gにブラダ20の先端開口端部22Eが掛け止めされるため、上述した摩擦力Fによるブラダの位置ずれをより発生し難くすることが可能である。その結果、ダンパーの組み立て時におけるブラダ20の捲れの発生が抑えられる。歩留まりを改善してコストダウンを図ることも可能である。 As described above, according to the second embodiment, in addition to the above (1) to (3), the effects listed below can be obtained.
(4) Since the leadingend opening end 22E of the bladder 20 is latched to the leading end engaging groove 12G over the entire distal end flange portion 12, it is possible to make the position displacement of the bladder due to the frictional force F less likely to occur. It is. As a result, the occurrence of wobbling of the bladder 20 during assembly of the damper is suppressed. It is also possible to reduce the cost by improving the yield.
(4)先端フランジ部12の全体にわたる先端掛止溝12Gにブラダ20の先端開口端部22Eが掛け止めされるため、上述した摩擦力Fによるブラダの位置ずれをより発生し難くすることが可能である。その結果、ダンパーの組み立て時におけるブラダ20の捲れの発生が抑えられる。歩留まりを改善してコストダウンを図ることも可能である。 As described above, according to the second embodiment, in addition to the above (1) to (3), the effects listed below can be obtained.
(4) Since the leading
(第3実施形態)
以下、本発明のダンパーを具体化した第3実施形態について、図3を参照して説明する。なお、第3実施形態では、ライナー10における先端フランジ部12の構造が、第2実施形態とは異なる。そのため、以下では、これらの構造について主に説明し、第2実施形態と同一部分については、それらの説明を割愛する。 (Third embodiment)
Hereinafter, a third embodiment in which the damper of the present invention is embodied will be described with reference to FIG. In the third embodiment, the structure of thetip flange portion 12 in the liner 10 is different from that in the second embodiment. Therefore, below, these structures are mainly demonstrated and those description is abbreviate | omitted about the same part as 2nd Embodiment.
以下、本発明のダンパーを具体化した第3実施形態について、図3を参照して説明する。なお、第3実施形態では、ライナー10における先端フランジ部12の構造が、第2実施形態とは異なる。そのため、以下では、これらの構造について主に説明し、第2実施形態と同一部分については、それらの説明を割愛する。 (Third embodiment)
Hereinafter, a third embodiment in which the damper of the present invention is embodied will be described with reference to FIG. In the third embodiment, the structure of the
図3に示されるように、先端フランジ部12の周壁及び底壁には、ピストンロッドRの軸方向に沿って延びる4つのスリット12Sが、ピストンロッドRの周方向に等配されている。4つのスリット12Sの各々は、ピストンロッドRの軸方向に沿って延びる切欠きであって、ピストンロッドRの軸方向においては、先端フランジ部12の全幅にわたり連続している。すなわち先端フランジ部12の全体は、4つのスリット12Sによって周方向に分割されている。また、先端フランジ部12の分割された部分である4つの先端フランジ片12Bの各々は、スリーブ部11の先端部にて片持ち梁状に連結されている。そして、4つの先端フランジ片12Bの各々が、ピストンロッドRの径方向の内側に向けて外力を受けると、これら4つの先端フランジ片12Bの各々は、該先端フランジ片12Bとスリーブ部11との連結箇所を固定端として、径方向の内側へ撓曲するようになる。
As shown in FIG. 3, four slits 12 </ b> S extending along the axial direction of the piston rod R are equally arranged in the circumferential direction of the piston rod R on the peripheral wall and bottom wall of the tip flange portion 12. Each of the four slits 12S is a notch extending along the axial direction of the piston rod R, and is continuous over the entire width of the tip flange portion 12 in the axial direction of the piston rod R. That is, the entire front end flange portion 12 is divided in the circumferential direction by the four slits 12S. Further, each of the four tip flange pieces 12 </ b> B, which is a divided portion of the tip flange portion 12, is connected in a cantilever shape at the tip portion of the sleeve portion 11. When each of the four front end flange pieces 12B receives an external force toward the inside in the radial direction of the piston rod R, each of the four front end flange pieces 12B is formed between the front end flange piece 12B and the sleeve portion 11. The connecting portion becomes a fixed end and bends inward in the radial direction.
次に、上述した構成からなるダンパーの作用のうち、特に、シリンダーC内にアキュムレーターが組み込まれる際の作用を説明する。
シリンダーCの内部にピストンロッドRが挿入される際、ブラダ20における先端側の端面が、大径部分C2の先端側の端面に当接するまでは、ブラダ20の先端掴持部22が大径部分C2の内周面を摺動し続ける。そして、ピストンロッドRが挿入される挿入方向とは反対方向の摩擦力Fが、この先端掴持部22に作用し続ける。一方、このような摩擦力Fは、先端掴持部22を捲る力として該先端掴持部22に作用する他、該先端掴持部22を介して、先端フランジ部12を径方向の内側(図3の矢印方向)へ変位させる力として該先端フランジ部12にも作用する。 Next, among the actions of the damper having the above-described configuration, particularly the action when the accumulator is incorporated in the cylinder C will be described.
When the piston rod R is inserted into the cylinder C, the distalend gripping portion 22 of the bladder 20 is in the large diameter portion until the end surface on the distal end side of the bladder 20 contacts the end surface on the distal end side of the large diameter portion C2. Continue sliding on the inner peripheral surface of C2. The frictional force F in the direction opposite to the insertion direction in which the piston rod R is inserted continues to act on the tip gripping portion 22. On the other hand, such a frictional force F acts on the tip gripping portion 22 as a force for pinching the tip gripping portion 22, and also causes the tip flange portion 12 to move radially inside (through the tip gripping portion 22 ( This also acts on the tip flange portion 12 as a force for displacement in the direction of the arrow in FIG.
シリンダーCの内部にピストンロッドRが挿入される際、ブラダ20における先端側の端面が、大径部分C2の先端側の端面に当接するまでは、ブラダ20の先端掴持部22が大径部分C2の内周面を摺動し続ける。そして、ピストンロッドRが挿入される挿入方向とは反対方向の摩擦力Fが、この先端掴持部22に作用し続ける。一方、このような摩擦力Fは、先端掴持部22を捲る力として該先端掴持部22に作用する他、該先端掴持部22を介して、先端フランジ部12を径方向の内側(図3の矢印方向)へ変位させる力として該先端フランジ部12にも作用する。 Next, among the actions of the damper having the above-described configuration, particularly the action when the accumulator is incorporated in the cylinder C will be described.
When the piston rod R is inserted into the cylinder C, the distal
この点、上述したダンパーにおいては、先端フランジ部12を構成する4つの先端フランジ片12Bの各々が、片持ち梁構造を有している。そのため、こうした片持ち梁構造を有しない構成と比較して、上述した摩擦力Fが、先端フランジ部12を撓ませる力に変換されやすくなる。また、先端フランジ片12Bが撓むことになれば、先端掴持部22の外周面と大径部分C2の内周面との接触面積が小さくなるため、上述した摩擦力Fそのものが先端掴持部22に作用することが抑えられることになる。その結果、こうした片持ち梁構造を有しない先端フランジ部と比較して、先端フランジ片12Bが撓む分、上述した摩擦力Fが先端掴持部22を捲る力として作用すること、それを抑えることが可能となる。ひいては、先端掴持部22が先端フランジ部12から外れることを抑えることが可能となる。
In this respect, in the above-described damper, each of the four tip flange pieces 12B constituting the tip flange portion 12 has a cantilever structure. Therefore, as compared with a configuration that does not have such a cantilever structure, the above-described frictional force F is easily converted into a force that bends the tip flange portion 12. Further, if the tip flange piece 12B bends, the contact area between the outer peripheral surface of the tip gripping portion 22 and the inner peripheral surface of the large diameter portion C2 is reduced, so that the frictional force F itself is held by the tip gripping portion. The action on the portion 22 is suppressed. As a result, as compared with the tip flange portion that does not have such a cantilever structure, the frictional force F described above acts as a force that squeezes the tip gripping portion 22 as much as the tip flange piece 12B is bent, and this is suppressed. It becomes possible. As a result, it is possible to suppress the tip gripping portion 22 from being detached from the tip flange portion 12.
以上、第3実施形態によれば、上述した(1)~(4)に加えて、以下に列記するような効果が得られるようになる。
(5)ライナー10の先端には、ブラダ20の先端部をシリンダーCに押圧する複数の先端フランジ片12Bが周方向に形成され、且つ複数の先端フランジ片12Bの各々が、基端で支持された片持ち梁状に形成されている。このような構成によれば、上述した摩擦力Fが、複数の先端フランジ片12Bを撓ませる力に変換されることとなる。そして、複数の先端フランジ片12Bの各々が径方向の内側に撓むことによって、ライナー10における先端部の外径が縮小するため、上述した摩擦力Fがブラダ20の先端部を基端側へずらす力として作用すること、それを抑えることが可能である。ひいては、シリンダーC内にて流体のシール性が低下することを抑えることが可能である。 As described above, according to the third embodiment, in addition to the above (1) to (4), the effects listed below can be obtained.
(5) At the distal end of theliner 10, a plurality of distal end flange pieces 12B that press the distal end portion of the bladder 20 against the cylinder C are formed in the circumferential direction, and each of the plurality of distal end flange pieces 12B is supported at the proximal end. It is shaped like a cantilever. According to such a configuration, the frictional force F described above is converted into a force that bends the plurality of front end flange pieces 12B. And since each outer diameter of the front-end | tip part in the liner 10 shrink | contracts when each of several front-end | tip flange pieces 12B bends to radial inside, the frictional force F mentioned above makes the front-end | tip part of the bladder 20 the base end side. It can act as a shifting force and suppress it. As a result, it is possible to prevent the fluid sealing performance from deteriorating in the cylinder C.
(5)ライナー10の先端には、ブラダ20の先端部をシリンダーCに押圧する複数の先端フランジ片12Bが周方向に形成され、且つ複数の先端フランジ片12Bの各々が、基端で支持された片持ち梁状に形成されている。このような構成によれば、上述した摩擦力Fが、複数の先端フランジ片12Bを撓ませる力に変換されることとなる。そして、複数の先端フランジ片12Bの各々が径方向の内側に撓むことによって、ライナー10における先端部の外径が縮小するため、上述した摩擦力Fがブラダ20の先端部を基端側へずらす力として作用すること、それを抑えることが可能である。ひいては、シリンダーC内にて流体のシール性が低下することを抑えることが可能である。 As described above, according to the third embodiment, in addition to the above (1) to (4), the effects listed below can be obtained.
(5) At the distal end of the
また、上述のように、ブラダ20が摩擦力Fによってずれることを抑えることが可能であるため、ダンパーの組み立て時におけるブラダ20の捲れの発生が抑えられる。それゆえに、歩留まりを改善してコストダウンを図ることも可能である。
Moreover, since it is possible to suppress the displacement of the bladder 20 due to the frictional force F as described above, the occurrence of bending of the bladder 20 during assembly of the damper can be suppressed. Therefore, it is possible to improve the yield and reduce the cost.
なお、上記各実施形態は、以下のように変更して実施することもできる。
先端摺動突条22Tの外径である突条外径DHは、大径部分C2の内径であるシリンダー内径DCよりも小さくてもよい(DH<DC)。このような構成であっても、ブラダ20と大径部分C2とのシール性が先端摺動突条22Tと押圧突条CTとによって確保される以上、アキュムレーターとしての機能を確保することは可能である。 In addition, each said embodiment can also be changed and implemented as follows.
The protrusion outer diameter DH, which is the outer diameter of thetip sliding protrusion 22T, may be smaller than the cylinder inner diameter DC, which is the inner diameter of the large diameter portion C2 (DH <DC). Even with such a configuration, it is possible to ensure the function as an accumulator as long as the sealing property between the bladder 20 and the large diameter portion C2 is ensured by the tip sliding protrusion 22T and the pressing protrusion CT. It is.
先端摺動突条22Tの外径である突条外径DHは、大径部分C2の内径であるシリンダー内径DCよりも小さくてもよい(DH<DC)。このような構成であっても、ブラダ20と大径部分C2とのシール性が先端摺動突条22Tと押圧突条CTとによって確保される以上、アキュムレーターとしての機能を確保することは可能である。 In addition, each said embodiment can also be changed and implemented as follows.
The protrusion outer diameter DH, which is the outer diameter of the
先端摺動突条22Tの外径である突条外径DHは、大径部分C2の内径であるシリンダー内径DCよりも大きくてもよく(DH>DC)、先端摺動突条22TがシリンダーCの内周面を押圧する力よりも大きな力で押圧突条CTが先端摺動突条22Tを押圧する構成であればよい。このような構成であっても、ブラダ20と大径部分C2とのシール性が先端摺動突条22Tと押圧突条CTとによって確保される以上、シリンダーCの内周面と先端摺動突条22Tとの密着性を抑えることは可能である。
The outer diameter DH of the protrusion, which is the outer diameter of the tip sliding protrusion 22T, may be larger than the cylinder inner diameter DC, which is the inner diameter of the large diameter portion C2, (DH> DC). Any configuration may be used as long as the pressing ridge CT presses the tip sliding ridge 22T with a force larger than the force pressing the inner peripheral surface. Even in such a configuration, as long as the sealing performance between the bladder 20 and the large-diameter portion C2 is ensured by the tip sliding protrusion 22T and the pressing protrusion CT, the inner peripheral surface of the cylinder C and the tip sliding protrusion It is possible to suppress the adhesion with the strip 22T.
基端掴持部23では、基端フランジ部13と大径部分C2とが基端掴持部23によってシールされる構成であれば、上述した基端摺動突条23Tが割愛される構成であってもよい。
In the base end gripping portion 23, if the base end flange portion 13 and the large diameter portion C2 are sealed by the base end gripping portion 23, the base end sliding protrusion 23T described above is omitted. There may be.
アキュムレーターの収容される収容部分の先端側にてシリンダーCの内径が小さくなる構成としては、上述したように、小径部分C1と大径部分C2とによってシリンダーCを構成する他、径方向の内側に突出する突条が、シリンダーCの内周面に形成されるという構成がある。上述した押圧突条CTとは、こうしたシリンダーC内に突出する突条に形成される構成であってもよく、アキュムレーターの収容される収容部分の先端側の端面に該収容部分の基端側に向けて突出し、且つ先端摺動突条22Tを押圧する環状の突条であればよい。
As described above, the inner diameter of the cylinder C becomes smaller at the distal end side of the housing portion in which the accumulator is housed. As described above, the cylinder C is composed of the small-diameter portion C1 and the large-diameter portion C2. There is a configuration in which the protruding ridges are formed on the inner peripheral surface of the cylinder C. The above-described pressing protrusion CT may be configured to be a protrusion protruding into the cylinder C, and the proximal end side of the accommodating portion is disposed on the end surface of the accommodating portion where the accumulator is accommodated. What is necessary is just the cyclic | annular protrusion which protrudes toward the edge and presses the front-end | tip sliding protrusion 22T.
押圧突条CTにおける先端摺動突条22T側の形状は、押圧突条CTが先端摺動突条22Tに押し付けられる形状であればよい。なお、押圧突条CTと先端摺動突条22Tとが点接触する構成であれば、これらが接触する面における面圧が高められ、シール性を高めることが可能にもなる。
The shape on the tip sliding ridge 22T side of the pressing ridge CT may be any shape as long as the pressing ridge CT is pressed against the tip sliding ridge 22T. In addition, if the pressing protrusion CT and the tip sliding protrusion 22T are in point contact, the surface pressure on the surface in contact with the pressing protrusion CT and the tip sliding protrusion 22T is increased, and the sealing performance can be improved.
押圧突条CTの内径は、アキュムレーターにおける先端の外径と同じであってもよく、あるいは同先端の外径よりも大きくてもよい。
押圧突条CTの延設される方向は、ピストンロッドRの軸方向とは異なる方向であってもよく、例えば、押圧突条CTは、大径部分C2の基端に向けて内径が小さくなる筒状、あるいは大径部分C2の基端に向けて内径が大きくなる筒状であってもよい。すなわち、押圧突条CTは、大径部分C2の端面CSから基端に向けて延びるような形状であればよい。 The inner diameter of the pressing protrusion CT may be the same as the outer diameter of the tip of the accumulator, or may be larger than the outer diameter of the tip.
The direction in which the pressing protrusion CT is extended may be a direction different from the axial direction of the piston rod R. For example, the pressing protrusion CT has an inner diameter that decreases toward the base end of the large-diameter portion C2. A cylindrical shape or a cylindrical shape whose inner diameter increases toward the proximal end of the large-diameter portion C2 may be used. In other words, the pressing protrusion CT may have a shape that extends from the end surface CS of the large-diameter portion C2 toward the base end.
押圧突条CTの延設される方向は、ピストンロッドRの軸方向とは異なる方向であってもよく、例えば、押圧突条CTは、大径部分C2の基端に向けて内径が小さくなる筒状、あるいは大径部分C2の基端に向けて内径が大きくなる筒状であってもよい。すなわち、押圧突条CTは、大径部分C2の端面CSから基端に向けて延びるような形状であればよい。 The inner diameter of the pressing protrusion CT may be the same as the outer diameter of the tip of the accumulator, or may be larger than the outer diameter of the tip.
The direction in which the pressing protrusion CT is extended may be a direction different from the axial direction of the piston rod R. For example, the pressing protrusion CT has an inner diameter that decreases toward the base end of the large-diameter portion C2. A cylindrical shape or a cylindrical shape whose inner diameter increases toward the proximal end of the large-diameter portion C2 may be used. In other words, the pressing protrusion CT may have a shape that extends from the end surface CS of the large-diameter portion C2 toward the base end.
先端フランジ部12に形成される先端掛止溝12Gは、2本以上であってもよい。なお、この際、これら先端掛止溝12Gの各々に掛止される突条が、先端掴持部22の内周面に形成される構成が好ましい。このような構成であれば、先端掴持部22が捲れることをさらに抑えることが可能にもなる。
There may be two or more tip latching grooves 12G formed in the tip flange portion 12. In this case, it is preferable that the protrusion hooked in each of the tip latching grooves 12G is formed on the inner peripheral surface of the tip gripping portion 22. With such a configuration, it is possible to further suppress the tip gripping portion 22 from falling.
先端フランジ部12に形成されるスリット12Sは、2本以上であればよく、また、これらのスリット12Sが等配されない構造であってもよく、片持ち梁状の先端フランジ片12Bが形成される構成であればよい。
The number of slits 12S formed in the distal end flange portion 12 may be two or more, and the slits 12S may be equally arranged, and a cantilevered distal end flange piece 12B is formed. Any configuration may be used.
2011年2月21日に出願された日本特許出願第2011-035023号の明細書、特許請求の範囲、図面及び要約書の全内容をここに引用し、本発明の明細書の開示として、取り入れるものである。
The entire contents of the specification, claims, drawings and abstract of Japanese Patent Application No. 2011-035023 filed on Feb. 21, 2011 are incorporated herein as the disclosure of the specification of the present invention. Is.
Claims (6)
- ピストンロッドが貫挿されるキャップが基端に嵌め込まれたシリンダーと、該シリンダー内に収容されて前記ピストンロッドと同心の環状をなすアキュムレーターとを備え、
前記アキュムレーターは、
前記ピストンロッドに外嵌された糸巻き状の筒体であるライナーと、
前記ライナーと前記シリンダーとの間に挟入され、前記ライナーの外周面と前記シリンダーの内周面との間の環状空間に容積の可変な流体室を区画する筒状のブラダとを備え、 前記流体室に流体を流入及び流出させて前記シリンダー内で流体を流通させるとともに、該流体の流体抵抗によって前記ピストンロッドを制動するダンパーであって、
前記ブラダは、該ブラダの径方向の外側に突出して該ブラダにて外径が最大となる環状の摺動突条を先端側に有し、
前記シリンダーは、前記アキュムレーターの収容される収容部分にて前記摺動突条の外径以上の内径を有し、且つ該収容部分における先端側の端面には、前記収容部分の基端側に向けて突出して前記摺動突条を基端側へ押圧する環状の押圧突条を有する
ことを特徴とするダンパー。 A cylinder in which a cap through which the piston rod is inserted is fitted at the base end, and an accumulator housed in the cylinder and concentric with the piston rod,
The accumulator is
A liner that is a thread-like cylindrical body externally fitted to the piston rod;
A cylindrical bladder sandwiched between the liner and the cylinder and defining a fluid chamber having a variable volume in an annular space between the outer peripheral surface of the liner and the inner peripheral surface of the cylinder; A damper that causes fluid to flow in and out of the fluid chamber to flow the fluid in the cylinder and brakes the piston rod by the fluid resistance of the fluid;
The bladder has an annular sliding protrusion on the tip side that projects outward in the radial direction of the bladder and has the largest outer diameter at the bladder.
The cylinder has an inner diameter that is greater than or equal to the outer diameter of the sliding protrusion at the accommodation portion in which the accumulator is accommodated, and the end surface on the distal end side of the accommodation portion has a base end side of the accommodation portion. A damper having an annular pressing protrusion that protrudes toward and presses the sliding protrusion toward the base end. - ピストンロッドが貫挿されるキャップが基端に嵌め込まれたシリンダーと、該シリンダー内に収容されて前記ピストンロッドと同心の環状をなすアキュムレーターとを備え、
前記アキュムレーターは、
前記ピストンロッドに外嵌された糸巻き状の筒体であるライナーと、
前記ライナーと前記シリンダーとの間に挟入され、前記ライナーの外周面と前記シリンダーの内周面との間の環状空間に容積の可変な流体室を区画する筒状のブラダとを備え、 前記流体室に流体を流入及び流出させて前記シリンダー内で流体を流通させるとともに、該流体の流体抵抗によって前記ピストンロッドを制動するダンパーであって、
前記ブラダは、該ブラダの径方向の外側に突出して該ブラダにて外径が最大となる環状の摺動突条を先端側に有し、
前記シリンダーは、前記アキュムレーターの収容される収容部分の先端側の端面に該収容部分の基端側に向けて突出して前記摺動突条を基端側へ押圧する環状の押圧突条を有し、
前記押圧突条は、前記摺動突条が前記シリンダーの内周面を押圧する力よりも大きな力で前記摺動突条を押圧する
ことを特徴とするダンパー。 A cylinder in which a cap through which the piston rod is inserted is fitted at the base end, and an accumulator housed in the cylinder and concentric with the piston rod,
The accumulator is
A liner that is a thread-like cylindrical body externally fitted to the piston rod;
A cylindrical bladder sandwiched between the liner and the cylinder and defining a fluid chamber having a variable volume in an annular space between the outer peripheral surface of the liner and the inner peripheral surface of the cylinder; A damper that causes fluid to flow in and out of the fluid chamber to flow the fluid in the cylinder and brakes the piston rod by the fluid resistance of the fluid;
The bladder has an annular sliding protrusion on the tip side that projects outward in the radial direction of the bladder and has the largest outer diameter at the bladder.
The cylinder has an annular pressing ridge that protrudes toward the proximal end side of the housing portion and presses the sliding ridge toward the proximal end side on an end surface of the housing portion in which the accumulator is housed. And
The damper, wherein the pressing protrusion presses the sliding protrusion with a force larger than a force with which the sliding protrusion presses the inner peripheral surface of the cylinder. - 前記シリンダーには、前記収容部分よりも小さい内径を有する小径部分が、前記収容部分の先端側に該収容部分と同心に連結され、
前記押圧突条は、前記ピストンロッドの軸方向に突出する環状の突条であって、前記小径部分が連結された前記収容部分側の端面に突設されている
請求項1又は2に記載のダンパー。 A small-diameter portion having an inner diameter smaller than that of the housing portion is connected to the cylinder, concentrically with the housing portion on the distal end side of the housing portion,
The said pressing protrusion is an annular protrusion protruding in the axial direction of the said piston rod, Comprising: It protrudes in the end surface by the side of the said accommodation part to which the said small diameter part was connected. Damper. - 前記摺動突条の先端側には、前記ブラダの先端側の開口縁が、径方向の内側に折り曲げられてなる開口端部が形成され、
前記開口端部が、前記ライナーの先端側の端面に掛け止めされて、前記ライナーの先端側の端面と前記収容部分の先端側の端面との間に挟入されている
請求項3に記載のダンパー。 On the distal end side of the sliding ridge, an opening end portion formed by bending the opening edge on the distal end side of the bladder inward in the radial direction is formed,
The end of the opening is hooked to an end surface on the front end side of the liner, and is sandwiched between an end surface on the front end side of the liner and an end surface on the front end side of the housing portion. Damper. - 前記ライナーは、前記ピストンロッドに外嵌されたスリーブ部を有し、
前記スリーブ部は、前記ブラダの先端部を前記シリンダーに押圧する先端フランジ部を先端に有するとともに、前記ブラダの基端部を前記シリンダーに押圧する基端フランジ部を基端に有し、
前記流体室は、前記スリーブ部と、前記先端フランジ部と、前記基端フランジ部と、前記ブラダとによって区画され、
前記先端フランジ部は、該先端フランジ部の周方向の全体にわたり掛止溝を有し、
前記ブラダの先端側の開口端部は、前記掛止溝に掛け止めされている
請求項1~4のいずれか一項に記載のダンパー。 The liner has a sleeve portion fitted on the piston rod;
The sleeve portion has a distal end flange portion that presses the distal end portion of the bladder against the cylinder, and a proximal end flange portion that presses the proximal end portion of the bladder against the cylinder at the proximal end.
The fluid chamber is partitioned by the sleeve portion, the distal flange portion, the proximal flange portion, and the bladder,
The tip flange portion has a latching groove over the entire circumferential direction of the tip flange portion,
The damper according to any one of claims 1 to 4, wherein an opening end portion on a distal end side of the bladder is latched in the latching groove. - 前記先端フランジ部は、
前記ブラダの先端部を前記シリンダーに押圧する複数の先端フランジ片を先端に有し、 前記複数の先端フランジ片は、
該先端フランジ片の基端部にて支持される片持ち梁状に前記ライナーの周方向に配列されている
請求項5に記載のダンパー。 The tip flange portion is
The front end includes a plurality of front end flange pieces that press the front end portion of the bladder against the cylinder.
The damper according to claim 5, wherein the dampers are arranged in a circumferential direction of the liner in a cantilever shape supported by a proximal end portion of the distal end flange piece.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201280009793.2A CN103384779B (en) | 2011-02-21 | 2012-02-14 | Buffer |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011035023A JP2012172755A (en) | 2011-02-21 | 2011-02-21 | Damper |
JP2011-035023 | 2011-02-21 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012114943A1 true WO2012114943A1 (en) | 2012-08-30 |
Family
ID=46720725
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2012/053413 WO2012114943A1 (en) | 2011-02-21 | 2012-02-14 | Damper |
Country Status (3)
Country | Link |
---|---|
JP (1) | JP2012172755A (en) |
CN (1) | CN103384779B (en) |
WO (1) | WO2012114943A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190024748A1 (en) * | 2017-07-24 | 2019-01-24 | Industrias Auxiliares, S.A. | Double-sealed gasket for hydraulic shock absorber for use in self-closers in furniture |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05346132A (en) * | 1991-08-30 | 1993-12-27 | Showa:Kk | Manufacture of buffer |
JP2008025713A (en) * | 2006-07-20 | 2008-02-07 | Fuji Latex Kk | Damper device |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3982804B2 (en) * | 2002-06-05 | 2007-09-26 | カヤバ工業株式会社 | Seal structure |
JP2006132594A (en) * | 2004-11-02 | 2006-05-25 | Showa Corp | Vehicular hydraulic shock absorber |
JP4884790B2 (en) * | 2006-02-02 | 2012-02-29 | 不二ラテックス株式会社 | shock absorber |
JP5016247B2 (en) * | 2006-03-31 | 2012-09-05 | 株式会社ニフコ | Speed response type damper |
JP4999712B2 (en) * | 2008-01-16 | 2012-08-15 | 不二ラテックス株式会社 | shock absorber |
CN201705853U (en) * | 2010-06-29 | 2011-01-12 | 沈秋庆 | Damping buffer |
-
2011
- 2011-02-21 JP JP2011035023A patent/JP2012172755A/en not_active Withdrawn
-
2012
- 2012-02-14 CN CN201280009793.2A patent/CN103384779B/en not_active Expired - Fee Related
- 2012-02-14 WO PCT/JP2012/053413 patent/WO2012114943A1/en active Application Filing
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05346132A (en) * | 1991-08-30 | 1993-12-27 | Showa:Kk | Manufacture of buffer |
JP2008025713A (en) * | 2006-07-20 | 2008-02-07 | Fuji Latex Kk | Damper device |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190024748A1 (en) * | 2017-07-24 | 2019-01-24 | Industrias Auxiliares, S.A. | Double-sealed gasket for hydraulic shock absorber for use in self-closers in furniture |
EP3434929A1 (en) * | 2017-07-24 | 2019-01-30 | Industrias Auxiliares, S.A. | Double-sealed gasket for hydraulic shock absorber for use in self-closers in furniture |
Also Published As
Publication number | Publication date |
---|---|
CN103384779A (en) | 2013-11-06 |
JP2012172755A (en) | 2012-09-10 |
CN103384779B (en) | 2015-08-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5083405B2 (en) | Vibration isolator | |
JP5341938B2 (en) | Radial seal | |
KR101814541B1 (en) | Fluid pressure apparatus | |
JP2016176496A (en) | Power transmission shaft | |
JP5473658B2 (en) | Air damper | |
WO2012114943A1 (en) | Damper | |
JP7518917B2 (en) | Electronic Expansion Valve | |
US9746111B2 (en) | Hydraulic tube for vehicle | |
US11459812B2 (en) | Damper | |
JP2023520121A (en) | Nut assembly and electronic expansion valve | |
JP4999712B2 (en) | shock absorber | |
JP6783748B2 (en) | Hole plug | |
JP2012172754A (en) | Damper | |
WO2018056216A1 (en) | Shock absorber | |
JP5798904B2 (en) | Piston ring and piston structure | |
JP2012180879A (en) | Damper | |
JP2012180880A (en) | Damper | |
JP6238962B2 (en) | Improvements in shock absorbers | |
CN105782219A (en) | Control Cable Liner | |
KR20160027115A (en) | Tampon applicator and method for its assembly | |
JP7337028B2 (en) | Damper and its manufacturing method | |
JP7431993B2 (en) | electronic expansion valve | |
JP5883320B2 (en) | Oil seal | |
WO2023171653A1 (en) | Damper device | |
JP5856678B2 (en) | Damper |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 12750079 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 12750079 Country of ref document: EP Kind code of ref document: A1 |