WO2017170361A1 - 流体圧シリンダ - Google Patents

流体圧シリンダ Download PDF

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Publication number
WO2017170361A1
WO2017170361A1 PCT/JP2017/012323 JP2017012323W WO2017170361A1 WO 2017170361 A1 WO2017170361 A1 WO 2017170361A1 JP 2017012323 W JP2017012323 W JP 2017012323W WO 2017170361 A1 WO2017170361 A1 WO 2017170361A1
Authority
WO
WIPO (PCT)
Prior art keywords
cushion
ring
piston rod
fluid pressure
pressure cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/012323
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
靖仁 高井
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
KYB Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by KYB Corp filed Critical KYB Corp
Priority to DE112017001603.7T priority Critical patent/DE112017001603T5/de
Priority to CN201780019665.9A priority patent/CN108779789B/zh
Publication of WO2017170361A1 publication Critical patent/WO2017170361A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
    • F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/222—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which throttles the main fluid outlet as the piston approaches its end position

Definitions

  • the present invention relates to a fluid pressure cylinder.
  • JP2012-172893A discloses a fluid pressure cylinder having a cushion mechanism.
  • the cushion mechanism disclosed in JP2012-172893A has a rod recess opened on the outer circumferential surface of the piston rod, a movable sleeve slidably fitted on the outer circumferential surface of the piston rod, and an opening on the inner circumferential surface of the sleeve of the movable sleeve.
  • the cushion mechanism is an operation in which the movable sleeve is directly discharged from the rod chamber to the supply / discharge port when the movable sleeve comes into contact with the cylinder head in the vicinity of the stroke end during the extension operation.
  • the flow of the fluid is switched to the flow of the working fluid flowing out to the supply / discharge port through the slit and the rod recess.
  • the piston rod is smoothly decelerated by the resistance applied to the flow of the working fluid passing through the slit, and the cushion function is exhibited.
  • the movable sleeve and the piston rod are moved relative to each other in the vicinity of the stroke end during the extension operation to exert a cushion function, and the movable sleeve and the piston rod are moved together during the contraction operation.
  • the movable sleeve is supported by a spring provided in the rod chamber.
  • the present invention aims to reduce the size of the fluid pressure cylinder.
  • a fluid pressure cylinder is a cylinder tube, a piston rod inserted into the cylinder tube, and connected to the tip of the piston rod, and the inside of the cylinder tube is divided into a rod side chamber and a bottom side chamber.
  • a piston a cushion provided on the outer periphery of the piston rod and decelerating the piston rod in the vicinity of a stroke end during extension operation; a supply / exhaust passage communicating with the rod side chamber and through which a working fluid supplied to and discharged from the rod side chamber passes; A contact portion that is provided on the tube and abuts against the cushion portion near the stroke end during the extension operation, and the cushion portion includes a cushion ring that abuts the contact portion near the stroke end during the extension operation, and a piston rod.
  • FIG. 1 is a cross-sectional view of a fluid pressure cylinder according to a first embodiment of the present invention.
  • FIG. 2 is an enlarged cross-sectional view showing a cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention.
  • FIG. 3A is a plan view showing a cushion ring of the fluid pressure cylinder according to the first embodiment of the present invention.
  • FIG. 3B is a plan view showing a modification of the cushion ring of the fluid pressure cylinder according to the first embodiment of the present invention.
  • FIG. 4 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and is a view showing the length of the regulation pin.
  • FIG. 5 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, showing a state where the piston rod is in the vicinity of the stroke end during the extension operation.
  • FIG. 6 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and shows a state in which the relative movement of the cushion ring with respect to the piston rod is allowed.
  • FIG. 7 is an enlarged cross-sectional view showing a cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and is a view showing a state of contraction operation from the stroke end of the extension operation.
  • FIG. 8 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and shows a state where the regulation pin faces the annular groove.
  • FIG. 9 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and shows a modification in which the cushion passage is formed in the cushion ring.
  • FIG. 10 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and shows a modification in which the cushion passage is formed in the piston rod.
  • FIG. 11 is an enlarged cross-sectional view showing the cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and shows a first modification in which the cushion passage is formed in the contact portion.
  • FIG. 12 is an enlarged cross-sectional view showing a cushion portion of the fluid pressure cylinder according to the first embodiment of the present invention, and shows a second modification in which the cushion passage is formed in the contact portion.
  • FIG. 13 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to the second embodiment of the present invention.
  • FIG. 14 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to the second embodiment of the present invention, and shows a first modification of the regulating ring.
  • FIG. 15 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to a second embodiment of the present invention, and shows a second modification of the regulating ring.
  • FIG. 16 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to a second embodiment of the present invention, showing a state where the piston rod is in the vicinity of the stroke end during the extension operation.
  • FIG. 17 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to a second embodiment of the present invention, and shows a state where relative movement of the cushion ring with respect to the piston rod is allowed.
  • FIG. 18 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to a third embodiment of the present invention.
  • FIG. 19 is a plan view showing an expansion / contraction ring of the fluid pressure cylinder according to the third embodiment of the present invention.
  • FIG. 20 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to a third embodiment of the present invention, showing a state where the piston rod is in the vicinity of the stroke end during the extension operation.
  • FIG. 21 is an enlarged cross-sectional view showing a cushion portion of a fluid pressure cylinder according to a third embodiment of the present invention, and is a view showing a state in which the contraction operation is performed from the stroke end of the extension operation.
  • FIG. 22 is a cross-sectional view showing a fluid pressure cylinder according to a comparative example of the present invention.
  • a fluid pressure cylinder according to an embodiment of the present invention will be described with reference to the drawings.
  • a fluid pressure cylinder is a hydraulic cylinder which drives hydraulic oil as a working fluid is demonstrated.
  • the hydraulic cylinder 100 As shown in FIG. 1, the hydraulic cylinder 100 according to the first embodiment includes a cylindrical cylinder tube 10, a piston rod 20 inserted into the cylinder tube 10, and a tip of the piston rod 20. A piston 30 that slides along the inner peripheral surface and a cushion portion 40 provided on the outer periphery of the piston rod 20 are provided.
  • the interior of the cylinder tube 10 is partitioned by the piston 30 into two fluid pressure chambers, a rod side chamber 1 and a bottom side chamber 2.
  • the hydraulic cylinder 100 is expanded and contracted by the hydraulic pressure guided from the hydraulic source (working fluid pressure source) to the rod side chamber 1 or the bottom side chamber 2.
  • the space between the inner periphery of the cylinder tube 10 and the outer periphery of the piston 30 is sealed by a seal member (not shown). Thereby, the communication between the rod side chamber 1 and the bottom side chamber 2 between the inner periphery of the cylinder tube 10 and the outer periphery of the piston 30 is blocked.
  • the inner peripheral surface of the cylinder tube 10 includes a sliding surface 11 on which the piston 30 slides, a large-diameter surface 12 formed with an inner diameter larger than the sliding surface 11, and the sliding surface 11 and the large-diameter surface 12. And an inner circumferential step portion 13 formed therebetween.
  • the large diameter surface 12 is formed continuously from the opening 10 ⁇ / b> A at one end of the cylinder tube 10.
  • the inner circumferential step 13 is formed with a tapered surface 13 ⁇ / b> A that decreases in inner diameter from the large-diameter surface 12 toward the sliding surface 11.
  • the cylinder tube 10 is provided with a cylindrical cylinder head 50 that seals the opening 10A at one end and slidably supports the piston rod 20.
  • the cylinder head 50 has a contact portion 51 that contacts the cushion portion 40 in the vicinity of the stroke end of the piston rod 20 during the extension operation.
  • the contact portion 51 is formed in a cylindrical shape and is inserted inside the cylinder tube 10.
  • the cylinder head 50 is fastened to the cylinder tube 10 via a plurality of fastening bolts (not shown) arranged in the circumferential direction.
  • the bush 55, the sub seal 56, the main seal 57, and the dust seal 58 are interposed on the inner periphery of the cylinder head 50.
  • the cylinder head 50 is formed with a supply / discharge port 3 communicating with a hydraulic pressure source.
  • the cylinder head 50 defines a supply / exhaust passage 4 that communicates the supply / exhaust port 3 and the rod side chamber 1 with the piston rod 20 by a passage groove 50 ⁇ / b> A formed on the inner peripheral surface.
  • the hydraulic oil is supplied / discharged from the supply / discharge port 3 to the rod side chamber 1 through the supply / discharge passage 4.
  • the piston rod 20 includes a main body portion 21 that is in sliding contact with the inner periphery of the cylinder head 50, a small diameter portion 22 that has a smaller outer diameter than the main body portion 21, and an annular shape that is formed between the main body portion 21 and the small diameter portion 22. It has a stepped portion 23 and a threaded portion 24 formed at the tip of the piston rod 20 to which the piston 30 is fastened.
  • annular groove 25 as a recess is formed in the small diameter portion 22 at a position adjacent to the step portion 23.
  • the annular groove 25 has a groove taper portion 25A that is connected to the outer peripheral surface of the small-diameter portion 22 and has a depth that decreases toward the piston 30 side.
  • the piston 30 is screwed into the threaded portion 24 of the piston rod 20 and fastened to the piston rod 20 with a predetermined tightening force.
  • the cushion part 40 is provided on the outer periphery of the small diameter part 22 of the piston rod 20 and between the step part 23 and the piston 30 in the axial direction.
  • the cushion portion 40 includes a cushion ring 41 that defines a cushion passage 42 that provides resistance to the passing hydraulic oil, and a small diameter in the piston rod 20 that is locked to the cushion ring 41.
  • a restriction pin 45 as a restriction part for restricting relative movement of the cushion ring 41 with respect to the piston rod 20 in a state where a part thereof is accommodated in the annular groove 25 of the part 22.
  • the cushion ring 41 is slidably fitted into the small diameter portion 22 of the piston rod 20 as shown in FIG.
  • the cushion ring 41 is formed so that the outer diameter is smaller than the inner diameter of the sliding surface 11 of the cylinder tube 10.
  • a plurality of cushion passages 42 are defined by a plurality of through holes penetrating in the axial direction.
  • the cushion passage 42 communicates the rod side chamber 1 and the supply / discharge passage 4 even when the cushion ring 41 is in contact with the contact portion 51 (see FIG. 5). That is, the cushion passage 42 is formed so as to open at a position facing the supply / discharge passage 4 on the end face of the cushion ring 41 facing the cylinder head 50.
  • a plurality of radial grooves 46 extending in the radial direction and communicating with the cushion passage 42 are formed on the end face of the cushion ring 41 facing the piston 30.
  • the radial groove 46 may not be communicated with the cushion passage 42 and may be formed at a position shifted from the cushion passage 42 as shown in FIG. 3B. Further, the radial groove 46 may open on the outer peripheral surface of the cushion ring 41. As described above, at least a part of the radial groove 46 is formed on the end face of the cushion ring 41 facing the piston 30 in the cushion ring 41, and guides the pressure of the hydraulic oil to separate the cushion ring 41 and the piston 30. As long as it is formed so as to promote, it can be formed in an arbitrary shape. 2 and 4 to 8, the cushion passage 42 and the radial groove 46 are schematically shown by broken lines.
  • the cushion ring 41 is formed with an insertion hole 47 that opens to the inner peripheral surface and the outer peripheral surface. As shown in FIG. 2, the regulation pin 45 is inserted into the insertion hole 47 of the cushion ring 41 and passes through the inner and outer peripheral surfaces of the cushion ring 41 in the radial direction. The restriction pin 45 is inserted into the insertion hole 47 so as to be movable in the radial direction of the cushion ring 41.
  • the length L of the restriction pin 45 is longer than the radial width W1 of the annular space between the small diameter portion 22 of the piston rod 20 and the sliding surface 11 of the cylinder tube 10.
  • the regulation pin 45 moves toward the radially outer side of the cylinder tube 10 in a state of facing the sliding surface 11 of the cylinder tube 10, and the end portion 45A of the regulation pin 45 on the radially outer side of the cylinder tube 10 is moved.
  • the state in which the end portion 45 ⁇ / b> B of the restriction pin 45 on the radially inner side is accommodated in the annular groove 25 is maintained.
  • the escape of the regulation pin 45 from the annular groove 25 is regulated. Therefore, the cushion ring 41 is held by the piston rod 20 by the restriction pin 45, and the relative movement of the cushion ring 41 and the piston rod 20 in the axial direction is restricted.
  • restrictive relative movement in the axial direction includes restricting relative movement between the cushion ring 41 and the piston rod 20 while the restriction pin 45 is housed in the annular groove 25. It is not intended to restrict the movement of the restriction pin 45 from the annular groove 25 and relative movement.
  • the length of the regulation pin 45 is shorter than the radial width W2 of the annular space defined between the large diameter surface 12 of the cylinder tube 10 and the small diameter portion 22 of the piston rod 20 (see FIG. 4). Therefore, when the regulation pin 45 is opposed to the large-diameter surface 12 of the cylinder tube 10, the restriction pin 45 moves radially outward so that the radially inner end 45 ⁇ / b> B can escape from the annular groove 25 (see FIG. 5). ). When the restricting pin 45 moves radially outward, the radially inner end 45B escapes from the annular groove 25, and the holding of the cushion ring 41 by the piston rod 20 is released. Thereby, the relative movement of the cushion ring 41 and the piston rod 20 in the axial direction is allowed. Further, in the state where the cushion ring 41 and the contact portion 51 are in contact, the restriction pin 45 is provided with an axial gap between the inner peripheral step portion 13 as shown in FIGS. 5 and 6.
  • the timing at which the restriction pin 45 faces the large diameter surface 12 is slightly smaller than the timing at which the cushion ring 41 and the contact portion 51 contact each other. Configured to be faster.
  • the radially inner end 45B of the regulating pin 45 escapes from the annular groove 25, and the holding of the cushion ring 41 by the piston rod 20 is released. Thereby, relative movement of the piston rod 20 in the extending direction with respect to the cushion ring 41 is allowed.
  • the groove taper portion 25A formed in the annular groove 25 moves the regulating pin 45 in the radial direction along with the movement of the piston rod 20 in the extending direction from the state in which the cushion ring 41 and the contact portion 51 are in contact. It corresponds to an escape guide portion that is pushed outward to escape from the annular groove 25.
  • the radial groove 46 is mainly formed through the gap between the supply / discharge passage 4, the contact portion 51 and the cushion ring 41, and the gap between the outer periphery of the cushion ring 41 and the inner peripheral surface of the cylinder tube 10.
  • the pressure of the hydraulic oil is guided and acts on the end face of the piston 30.
  • the cushion ring 41 and the piston 30 are separated from each other, and the piston rod 20 moves relative to the cushion ring 41 in the contracting direction.
  • the radial groove 46 functions as a pressure introducing groove, and promotes the separation between the cushion ring 41 and the piston 30 during the contraction operation.
  • the restriction pin 45 is unlocked from the inner circumferential step portion 13 of the cylinder tube 10, and the radially inner end portion 45 ⁇ / b> B is accommodated in the annular groove 25 of the piston rod 20 again.
  • the cushion ring 41 held again by the piston rod 20 moves in the contracting direction together with the piston rod 20.
  • the taper surface 13A of the inner circumferential step 13 is moved radially inward with the movement of the piston rod 20 in the contracting direction from the state where the cushion ring 41 and the contact portion 51 are in contact. It corresponds to an accommodation guide portion that is pushed out and accommodated in the annular groove 25.
  • the relative movement of the cushion ring 41 with respect to the piston rod 20 is restricted by the restriction pin 45, so that the cushion ring 41 and the piston rod 20 extend in the extending direction until the contact with the contact portion 51. Move to. In the vicinity of the stroke end during the extension operation, the cushion ring 41 is brought into contact with the contact portion 51 and the relative movement with the piston rod 20 is allowed, so that the cushion function is exhibited. Further, in the hydraulic cylinder 100, since the restriction pin 45 is accommodated again in the piston rod 20 during the contraction operation, the cushion ring 41 can be held again by the piston rod 20 and moved together with the piston rod 20 in the contraction direction.
  • the cushion portion 40 and the piston rod 20 can be moved relative to each other when the cushion function is exerted, and can be moved together with the piston rod 20 in the contracting direction during the contracting operation. Therefore, the overall length of the hydraulic cylinder 100 can be shortened and downsized.
  • a pressure difference may occur between the inside and the outside of the spring, particularly when the spring contracts and the axial gap between the wires becomes small. If the spring breaks due to such a pressure difference, the operation of the cushion portion 40 becomes unstable, and the cushion function may not be stably exhibited.
  • the hydraulic cylinder 100 does not provide a spring in the rod side chamber 1 and supports the cushion ring 41 by the restriction pin 45, the occurrence of a situation in which the cushion function is not stably exhibited due to breakage of the spring is prevented. Can do.
  • the hydraulic cylinder 400 according to the comparative example includes a cylindrical cushion bearing 340 provided on the outer periphery of the piston rod 20 and a bearing receiving portion 351 that allows the cushion bearing 340 to enter near the end of the extension stroke.
  • the cushion passage 342 is formed by the cushion bearing 340 entering the inside of the bearing receiving portion 351 near the end of the extension stroke.
  • a cushion pressure corresponding to the resistance applied by the cushion passage 342 acts on the rod side chamber 1.
  • the pressure receiving area of the piston 30 on which the cushion pressure acts corresponds to the area between the outer periphery of the cushion bearing 340 and the outer periphery of the piston 30.
  • the pressure receiving area of the cushion pressure is the outer periphery of the small diameter portion 22 of the piston rod 20 and the outer periphery of the piston 30. Corresponds to the area between. For this reason, the pressure receiving area of the hydraulic cylinder 100 can be made larger by the cross-sectional integral of the cushion bearing 340 than the pressure receiving area of the hydraulic cylinder 400 according to the comparative example. Therefore, in the hydraulic cylinder 100, even if the same cushion performance is exhibited, the pressure receiving area is increased, so that the cushion pressure can be made smaller than that of the hydraulic cylinder 400. Since the cushion pressure can be reduced, in the hydraulic cylinder 100, the strength of the cylinder tube 10, the piston 30, and the cylinder head 50 that receive the cushion pressure may be relatively small, and the manufacturing cost can be reduced.
  • the cushion bearing 340 may be sandwiched in the axial direction by the step portion 23 of the piston rod 20 and the piston 30 screwed to the piston rod 20.
  • the supply / discharge passage 4 and the rod side chamber 1 communicate with each other through the cushion passage 342 until the cushion bearing 340 comes out of the bearing receiving portion 351.
  • the flow area of the hydraulic oil is suddenly expanded, and sudden pressure fluctuations and fluctuations in the operating speed (moving speed of the piston 30) occur in the rod side chamber 1. May cause abnormal noise.
  • the cushion ring 41 and the contact portion 51 are quickly separated and the supply / exhaust passage 4 and the rod side chamber 1 directly communicate with each other. Occurrence of abnormal noise or the like due to speed fluctuation can be prevented.
  • the cushion bearing 340 is provided with a gap in the axial direction between the step portion 23 of the piston rod 20 and the piston 30 screwed to the piston rod 20 (so-called Floating support structure).
  • a groove is formed on the outer peripheral surface of the piston rod 20, and a cushion seal having a joint gap may be provided in the groove of the piston rod 20.
  • the hydraulic oil in the rod side chamber 1 exerts a cushion function by imparting resistance to the hydraulic oil by the cushion passage 342 and the joint gap of the cushion seal.
  • the cushion performance of the hydraulic cylinder 400 can be easily adjusted by adjusting the size of the joint gap with the cushion bearing 340 in common.
  • the cushion performance can be easily adjusted by adjusting the size of the cushion passage 42. Therefore, it is not necessary to form the cushion seal and the groove of the piston rod 20 that accommodates the cushion seal. . Therefore, in the hydraulic cylinder 100, the cushion performance can be easily adjusted, and the number of processing steps can be reduced, so that the manufacturing cost can be further reduced.
  • the cushion passage 42 is a through hole formed in the cushion ring 41.
  • the cushion passage 42 may be formed in an orifice plug that is detachably attached to the cushion ring 41.
  • the cushion performance can be easily adjusted, and the cushion ring 41 can be used in common, thereby reducing the manufacturing cost. be able to.
  • the number of orifice plugs and sealing plugs attached to the cushion ring 41 can be arbitrarily changed. The cushion performance may be adjusted.
  • the cushion passage 42 may be a single through hole. Furthermore, the cushion passage 42 may not be a through hole.
  • an annular passage defined by the outer peripheral surface of the piston rod 20 and the inner peripheral surface of the cushion ring 41 may be used as the cushion passage 42.
  • the cushion passage 42 may be a slit formed on the end surface of the cushion ring 41 facing the contact portion 51.
  • the cushion passage 42 is preferably formed in the cushion ring 41. Since the cushion ring 41 is smaller than the piston rod 20 and the cylinder head 50 and has a size that is easy to process, the cushion passage 42 can be easily formed with high accuracy. However, the cushion passage 42 may be formed in the piston rod 20, for example, as shown in FIG. As shown in FIGS. 11 and 12, the cushion passage 42 may be a passage or slit formed in the contact portion 51.
  • the recess does not have to be the annular groove 25 and can be formed in any shape as long as it can accommodate the regulation pin 45.
  • the recess may be a recess formed in a part in the circumferential direction, instead of an annular shape over the entire circumference of the piston rod 20.
  • a plurality of restriction pins 45 may be provided. By providing the plurality of restricting pins 45, the force acting on each restricting pin 45 when being locked to the annular groove 25 or the inner circumferential step portion 13 can be dispersed.
  • the escape guide portion is the groove taper portion 25 ⁇ / b> A of the annular groove 25 of the piston rod 20, and the accommodation guide portion is the taper surface 13 ⁇ / b> A of the inner circumferential step portion 13 of the cylinder tube 10.
  • the escape guide portion and the accommodation guide portion may be formed on the restriction pin 45, respectively.
  • the escape guide portion and the accommodation guide portion may be formed in each of the regulation pin 45, the annular groove 25, and the inner circumferential step portion 13.
  • the escape guide part and the accommodation guide part are not limited to the tapered surface, and may be any one that presses and pushes out the regulating pin 45 in the radial direction as the piston rod 20 moves, and may be, for example, a curved surface.
  • the radially outer end 45A and the inner end 45B of the restriction pin 45 may be formed in a hemispherical shape, and the spherical surfaces of the ends 45A and 45B may be used as the escape guide portion and the accommodation guide portion.
  • the cushion ring 41 is held by the piston rod 20 by the restriction pin 45, so that a spring for supporting the cushion ring 41 is not provided in the rod side chamber 1, and in the vicinity of the stroke end during the extension operation, The cushion function is demonstrated. Therefore, the hydraulic cylinder 100 can be reduced in size.
  • the hydraulic cylinder 100 does not need to provide a spring for supporting the cushion ring 41 in the rod side chamber 1, the operation of the cushion portion 40 is prevented from becoming unstable due to breakage of the spring, and the cushion is stably cushioned. Function can be demonstrated.
  • the hydraulic cylinder 100 does not define the cushion passage 341 by the cushion bearing 340 entering the bearing receiving portion 351, a cushion seal inside the cushion bearing 340 is not necessary, and the manufacturing cost can be reduced. Further, it is possible to prevent the generation of abnormal noise when the cushion bearing 340 comes out of the bearing receiving portion 351.
  • the pressure receiving area for receiving the cushion pressure in the cylinder head 50 and the piston 30 can be increased as compared with the case where the cushion passage 341 is defined by the cushion bearing 340. it can. For this reason, cushion pressure can be reduced and the cylinder tube 10, the cylinder head 50, and piston 30 can be formed in comparatively low intensity
  • the restricting portion is the restricting pin 45 that passes through the inner and outer peripheral surfaces of the cushion ring 41.
  • the hydraulic cylinder 200 according to the second embodiment has a pair of restriction rings 145 provided on the outer periphery and the inner periphery of the cushion ring 141, respectively, in the hydraulic cylinder 100 according to the first embodiment. Is different.
  • the outer peripheral surface and the inner peripheral surface of the cushion ring 141 of the hydraulic cylinder 200 are provided with an outer peripheral groove 141A and an inner peripheral groove 141B formed in an annular shape, respectively.
  • the cushion ring 141 is formed with a cushion passage 42 and a radial groove 46 as in the first embodiment, and has a plurality of main passages 142 with less resistance to the flow of hydraulic oil than the cushion passage 42. Is formed.
  • the main passage 142 is blocked by the contact portion 51 (see FIG. 16). 13 to 17, only the single main passage 142 is shown, and the others are not shown.
  • the plurality of main passages 142 only need to be configured so that the resistance applied to the flow of hydraulic oil is smaller than that of the cushion passage 42 as a whole.
  • the pair of regulating rings 145 includes an outer peripheral ring 145A provided in the outer peripheral groove 141A of the cushion ring 141 and an inner peripheral ring 145B provided in the inner peripheral groove 141B.
  • the outer ring 145A and the inner ring 145B are each formed in a C-ring shape that has a gap (not shown) and can be expanded and contracted.
  • the outer ring 145A and the inner ring 145B may be made of metal such as a snap ring or may be made of resin.
  • the outer ring 145A and the inner ring 145B have a circular cross section as shown in FIG. 13, but the present invention is not limited to this, and other cross sectional shapes (for example, a rectangular shape shown in FIG. 14). It may have. Further, as shown in FIG.
  • biasing members 145C and 145D such as rubber and spring are provided between the outer ring 145A and the outer groove 141A and between the inner ring 145B and the inner groove 141B, and the outer ring 145A. May be urged radially outward, and the inner ring 145B may be urged radially inward.
  • the outer ring 145A is in contact with the inner circumferential surface of the cylinder tube 10, and further expansion is restricted by the inner circumferential surface of the cylinder tube 10.
  • the outer peripheral ring 145A has a shape that protrudes radially outward from the outer peripheral groove 141A in a free state, and is compressed by being radially contracted by the inner peripheral surface of the cylinder tube 10 to cause the outer peripheral groove 141A. Is housed.
  • the inner ring 145B contacts the outer circumferential surface of the piston rod 20, and further contraction is restricted by the outer circumferential surface of the piston rod 20.
  • the inner ring 145B is shaped so as to protrude radially inward from the inner groove 141B in a free state, and is pressed radially outward by the outer peripheral surface of the piston rod 20 to expand the inner periphery. It is accommodated in the groove 141B.
  • the outer peripheral ring 145A contacts the inner peripheral surface of the cylinder tube 10, and the inner peripheral ring 145B contacts the outer peripheral surface of the piston rod 20. Therefore, the rod side chamber 1 is partitioned into a first rod side chamber 1A and a second rod side chamber 1B by the cushion portion 140.
  • the first rod side chamber 1 ⁇ / b> A and the second rod side chamber 1 ⁇ / b> B communicate with each other through the main passage 142 of the cushion ring 141.
  • the inner peripheral part of the inner ring 145B is accommodated in the annular groove 25 of the piston rod 20, and the cushion ring 141 is held by the piston rod 20. More specifically, the inner ring 145B accommodated in the inner groove 141B in a state of being expanded by the outer peripheral surface of the piston rod 20 is restricted from escaping from the annular groove 25 by the elastic force in the contracting direction. The Thereby, the state in which the cushion ring 141 is held by the piston rod 20 is maintained, and the relative movement in the axial direction between the cushion ring 141 and the piston rod 20 is restricted.
  • the outer peripheral ring 145 ⁇ / b> A of the cushion portion 140 faces the large-diameter surface 12 of the cylinder tube 10, and the cushion ring 141 is the contact portion of the cylinder head 50. 51 abuts.
  • the cushion oil is provided by the amount of axial clearance between the outer ring 145A and the inner step 13 by the hydraulic oil guided from the supply / discharge passage 4.
  • Both 141 and the piston rod 20 move in the contraction direction. Thereby, the cushion ring 141 and the contact portion 51 are separated from each other, and the supply / discharge passage 4 and the first rod side chamber 1A are directly communicated with each other.
  • the pressure of the hydraulic fluid guided from the supply / discharge passage 4 is guided to the radial groove 46 through the first rod side chamber 1A, the main passage 142, and the second rod side chamber 1B, and acts on the end face of the piston 30.
  • the cushion ring 141 and the piston 30 are separated from each other, and the piston rod 20 moves relative to the cushion ring 141 in the contracting direction.
  • the contact between the inner peripheral ring 145B and the annular groove 25 is a line contact.
  • the force which escapes the inner peripheral ring 145B from the annular groove 25 is provided. It can be dispersed and the durability can be improved.
  • the restricting portion is a pair of restricting rings (an outer ring 145A and an inner ring 145B), but instead of this, the biasing members 145C and 145D (see FIG. 15) are used in the radial direction.
  • One or a plurality of spheres (steel balls or the like) that are urged to the outside and the inside may be used as the restricting portion.
  • the restricting portion is the restricting pin 45 that passes through the inner and outer peripheral surfaces of the cushion ring 41.
  • the restricting portion of the hydraulic cylinder 300 according to the third embodiment is a single expansion / contraction ring 245 that is provided adjacent to the cushion ring 241 and has an abutment gap 245A and can be expanded / contracted. This is different from the hydraulic cylinder 100 according to the first embodiment.
  • the cushion ring 241 of the hydraulic cylinder 300 is provided between the stepped portion 23 of the piston rod 20 and the expansion / contraction ring 245.
  • a cushion passage 242 and a radial groove 46 are formed in the cushion ring 241 as in the first embodiment, and an annular central recess 243 is formed radially inward at the end face facing the expansion / contraction ring 245.
  • the cushion passage 242 is formed in communication with the space inside the central recess 243.
  • the central recess 243 opens on the end surface of the cushion ring 241 facing the expansion / contraction ring 245 and opens on the inner peripheral surface of the cushion ring 241.
  • the expansion / contraction ring 245 adjacent in the axial direction functions as a pressing member that prevents the orifice plug from coming off from the cushion ring 241.
  • the expansion / contraction ring 245 is formed in a C-ring shape having a joint gap 245 ⁇ / b> A that can be expanded / contracted.
  • the inner peripheral portion is accommodated in the annular groove 25 as shown in FIG. A gap is formed in
  • the outer diameter of the central step 246 is formed to be smaller than the inner diameter of the central recess 243 of the cushion ring 241 when the expansion / contraction ring 245 is accommodated in the annular groove 25. Therefore, in the state where the expansion / contraction ring 245 is accommodated in the annular groove 25, a radial gap is provided between the central recess 243 of the cushion ring 241 and the central step 246 of the expansion / contraction ring 245. Further, when the cushion ring 241 and the expansion / contraction ring 245 are in contact with each other, the central step portion 246 forms a gap in the axial direction without contacting the central concave portion 243. Therefore, the cushion passage 242 communicates with the joint gap 245A (see FIG. 19) of the expansion / contraction ring 245 through the radial gap and the axial gap between the central step 246 and the central recess 243.
  • the center step 246 contacts the center recess 243 of the cushion ring 241.
  • the center step 246 of the expansion / contraction ring 245 contacts the central recess 243 of the cushion ring 241, thereby preventing the center of the expansion / contraction ring 245 from being shifted from the center of the piston rod 20.
  • the central recess 243 of the cushion ring 241 exhibits a centering function that prevents the centering of the expansion / contraction ring 245 accompanying expansion and stabilizes the slidability between the expansion / contraction ring 245 and the cushion ring 241.
  • the expansion / contraction ring 245 In a state where the expansion / contraction ring 245 faces the sliding surface 11 of the cylinder tube 10, the expansion / contraction ring 245 is accommodated in the annular groove 25 of the piston rod 20 so that the cushion ring 241 is sandwiched between the stepped portion 23 of the piston rod 20. 241 is locked. Thereby, the cushion ring 241 is held by the piston rod 20.
  • the expansion / contraction ring 245 has an outer diameter smaller than the inner diameter of the sliding surface 11 when the inner peripheral surface is in contact with the annular groove 25 (the state shown in FIG. 18).
  • the expansion / contraction ring 245 has an outer diameter that is larger than the inner diameter of the sliding surface 11 and smaller than the inner diameter of the large-diameter surface 12 in a state where it has escaped from the annular groove 25 (the state shown in FIG. In a state where the inner peripheral surface of the expansion / contraction ring 245 contacts the annular groove 25, a gap is formed between the outer peripheral surface of the expansion / contraction ring 245 and the sliding surface 11 of the cylinder tube 10.
  • the expansion / contraction ring 245 faces the large-diameter surface 12 of the cylinder tube 10
  • the expansion / contraction ring 245 is allowed to expand by the large-diameter surface 12, and the expansion / contraction ring 245 can escape from the annular groove 25. Therefore, as shown in FIG. 20, the cushion ring 241 is released from the holding by the piston rod 20 when the expansion / contraction ring 245 expands and escapes from the annular groove 25.
  • the expansion / contraction ring 245 of the cushion portion 40 faces the large-diameter surface 12 of the cylinder tube 10, and the cushion ring 241 contacts the contact portion 51 of the cylinder head 50.
  • the hydraulic oil in the rod side chamber 1 becomes a gap in the radial direction between the joint gap 245A of the expansion / contraction ring 245 and the central step 246 of the expansion / contraction ring 245 and the central recess 243 of the cushion ring 241. And the axial clearance and is guided to the cushion passage 242.
  • the hydraulic oil in the rod side chamber 1 is guided to the supply / discharge passage 4 and the supply / discharge port 3 through the cushion passage 242 and is discharged from the rod side chamber 1. Therefore, a cushion pressure corresponding to the resistance applied by the cushion passage 242 acts on the rod side chamber 1. In this way, the cushioning action in the vicinity of the extension stroke end of the piston rod 20 is exhibited.
  • the cushion oil is provided by an amount corresponding to the axial clearance between the expansion / contraction ring 245 and the inner circumferential step portion 13 by the hydraulic oil guided from the supply / discharge passage 4.
  • Both 241 and the piston rod 20 move in the contraction direction. Accordingly, as shown in FIG. 21, the cushion ring 241 and the contact portion 51 are separated from each other, and the supply / discharge passage 4 and the first rod side chamber 1A are directly communicated with each other.
  • the pressure of the hydraulic oil guided from the supply / discharge passage 4 is guided to the radial groove 46 through the joint gap 245A of the rod side chamber 1 and the expansion / contraction ring 245 and acts on the end face of the piston 30.
  • the cushion ring 241 and the piston 30 are separated from each other, and the piston rod 20 moves relative to the cushion ring 241 in the contracting direction.
  • the expansion / contraction ring 245 When the piston rod 20 moves in the contraction direction until the expansion / contraction ring 245 faces the annular groove 25 of the piston rod 20, the expansion / contraction ring 245 is pressed radially inward by the tapered surface 13 ⁇ / b> A of the inner circumferential step portion 13 and its own. It contracts by the elastic force and is accommodated in the annular groove 25. As a result, the engagement between the expansion / contraction ring 245 and the inner circumferential step portion 13 of the cylinder tube 10 is released, and the expansion / contraction ring 245 is accommodated again in the annular groove 25 of the piston rod 20. In this way, the cushion ring 241 held again by the piston rod 20 moves in the contracting direction together with the piston rod 20.
  • the expansion / contraction ring 245 is formed in the annular groove 25 as compared with the first embodiment. It is possible to disperse the force of escaping from the environment and improve the durability.
  • the hydraulic cylinders 100, 200, and 300 are connected to a cylinder tube 10, a piston rod 20 inserted into the cylinder tube 10, and a tip of the piston rod 20, and divide the inside of the cylinder tube 10 into a rod side chamber 1 and a bottom side chamber 2.
  • the piston 30, the cushion portions 40, 140, 240 that are provided on the outer periphery of the piston rod 20 and decelerate the piston rod 20 near the stroke end during the extension operation, and the operation that communicates with the rod side chamber 1 and is supplied to and discharged from the rod side chamber 1.
  • Cushion rings 41, 141, 241 that contact the contact portion 51 near the stroke end of the hour A restricting portion (a restricting pin 45, a pair of restricting rings 145, restricting relative movement of the cushion rings 41, 141, 241 with respect to the piston rod 20 while being accommodated in an annular groove 25 formed on the outer peripheral surface of the piston rod 20.
  • the inner peripheral surface of the cylinder tube 10 includes a sliding surface 11 on which the piston 30 slides, a large-diameter surface 12 that has a larger inner diameter than the sliding surface 11,
  • the restricting portion (the restricting pin 45, the pair of restricting rings 145, and the expansion / contraction ring 245) is restricted from coming out of the annular groove 25 by contact with the sliding surface 11, and faces the large diameter surface 12. Thus, escape from the annular groove 25 is allowed.
  • the hydraulic oil discharged from the rod side chamber 1 is guided to the supply / discharge passage 4 through the cushion passages 42 and 242, and the cushion function for decelerating the piston rod 20 is exhibited.
  • the relative movement of the cushion rings 41, 141, 241 with respect to the piston rod 20 is restricted by the restriction portions (the restriction pins 45, the pair of restriction rings 145, the expansion / contraction ring 245), thereby the cushion rings 41, 141, 241.
  • the cushion function is exhibited in the vicinity of the stroke end during the extension operation. Therefore, the fluid pressure cylinders 100, 200, and 300 can be reduced in size.
  • the cushion rings 41, 141, and 241 and the contact portion 51 are provided in at least one of the restriction portion (the restriction pin 45, the pair of restriction rings 145, the expansion / contraction ring 245) or the annular groove 25.
  • the restricting portion (the restricting pin 45, the inner peripheral ring 145B, the expansion / contraction ring 245) is pressed radially outward to escape from the annular groove 25.
  • a tapered portion 25A is formed.
  • the restriction portion (the restriction pin 45, the inner peripheral ring 145 B, expansion / contraction)
  • the ring 245) can surely escape from the annular groove 25.
  • the inner peripheral surface of the cylinder tube 10 further includes an inner peripheral step 13 formed between the sliding surface 11 and the large-diameter surface 12. At least one of the pin 45, the outer ring 145A, the expansion / contraction ring 245) or the inner step 13 is in the contraction direction of the piston rod 20 from the state in which the cushion rings 41, 141, 241 and the contact portion 51 are in contact.
  • an accommodation guide portion is formed in which the restriction portions (restriction pin 45, outer ring 145A, expansion / contraction ring 245) are pressed radially inward to be accommodated in the annular groove 25.
  • the restriction portions (the restriction pin 45, the outer ring 145 ⁇ / b> A, the expansion / contraction ring). 245) can be reliably accommodated in the annular groove 25, and the piston rod 20 can be moved in the contraction direction.
  • the restriction portion (the restriction pin 45, the outer ring 145 ⁇ / b> A, the expansion / contraction ring 245) and the inner step portion 13. A gap in the axial direction is formed between them.
  • the cushion passages 42, 242 may be formed as orifice plugs that are detachably provided in the cushion rings 41, 141, 241.
  • the cushion performance can be easily adjusted by exchanging the orifice plug.
  • the restricting portion is a restricting pin 45 that is inserted through the outer peripheral surface and the inner peripheral surface of the cushion ring 41 and is movable in the radial direction.
  • the restricting portions are provided on the outer periphery and the inner periphery of the cushion ring 141, respectively, and a pair of restricting rings 145 (an outer ring 145A and an inner ring 145B) are formed so as to be able to expand and contract. It is.
  • the restricting portion is an expansion / contraction ring 245 provided adjacent to the cushion ring 241 in the axial direction and having a joint gap 245A so as to be expandable / contractible.
  • the cushion ring 241 has a central recess 243 formed on the inner side of the end surface facing the expansion / contraction ring 245, and the expansion / contraction ring 245 has a central step 246 inserted into the central recess 243.
  • a radial gap is formed between the central recess 243 and the central step 246, and the expansion / contraction ring 245 expands to form the annular groove 25.
  • the central step 246 contacts the central recess 243.
  • the expansion / contraction ring 245 can be expanded while being aligned by contacting the central recess 243 of the cushion ring 241 and the central step 246 of the expansion / contraction ring 245. Therefore, the slidability between the cushion ring 41 and the expansion / contraction ring 245 can be stabilized.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Actuator (AREA)
  • Fluid-Damping Devices (AREA)
PCT/JP2017/012323 2016-03-31 2017-03-27 流体圧シリンダ Ceased WO2017170361A1 (ja)

Priority Applications (2)

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DE112017001603.7T DE112017001603T5 (de) 2016-03-31 2017-03-27 Fluiddruckzylinder
CN201780019665.9A CN108779789B (zh) 2016-03-31 2017-03-27 流体压缸

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JP2016072428A JP6255440B2 (ja) 2016-03-31 2016-03-31 流体圧シリンダ
JP2016-072428 2016-03-31

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115956164A (zh) * 2020-08-24 2023-04-11 Ｋｙｂ株式会社 多级式流体压力缸

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7323103B2 (ja) * 2020-07-22 2023-08-08 Smc株式会社 流体圧シリンダ

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60125404A (ja) * 1983-12-12 1985-07-04 Kayaba Ind Co Ltd シリンダのクツシヨン装置

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009639A (en) * 1973-08-09 1977-03-01 Kayabakogyo-Kabushiki-Kaisha Hydraulic swing motor
KR100386185B1 (ko) * 1998-05-29 2003-06-02 히다치 겡키 가부시키 가이샤 유압 실린더
KR20040072846A (ko) * 2003-02-11 2004-08-19 현대모비스 주식회사 댐퍼
CN101761520A (zh) * 2010-02-06 2010-06-30 楼天汝 减压缓冲油缸
JP5730058B2 (ja) * 2011-02-17 2015-06-03 Ｋｙｂ−Ｙｓ株式会社 流体圧シリンダ
JP5789456B2 (ja) * 2011-09-06 2015-10-07 カヤバ工業株式会社 流体圧シリンダ
WO2014124519A1 (en) * 2013-02-13 2014-08-21 Messier-Dowty Inc. Modular actuator with snubbing arrangement
CN203743126U (zh) * 2013-12-30 2014-07-30 中船重工中南装备有限责任公司 一种双浮动缓冲液压缸
JP2016072428A (ja) 2014-09-30 2016-05-09 株式会社ディスコ ウエーハの保持方法
CN105090159A (zh) * 2015-08-29 2015-11-25 济南大学 一种基于颤振机理的低摩擦快启液压缸

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60125404A (ja) * 1983-12-12 1985-07-04 Kayaba Ind Co Ltd シリンダのクツシヨン装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115956164A (zh) * 2020-08-24 2023-04-11 Ｋｙｂ株式会社 多级式流体压力缸

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CN108779789B (zh) 2020-07-14
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CN108779789A (zh) 2018-11-09
DE112017001603T5 (de) 2018-12-13

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