EP1717451A2 - Vérin - Google Patents

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Publication number
EP1717451A2
EP1717451A2 EP06112109A EP06112109A EP1717451A2 EP 1717451 A2 EP1717451 A2 EP 1717451A2 EP 06112109 A EP06112109 A EP 06112109A EP 06112109 A EP06112109 A EP 06112109A EP 1717451 A2 EP1717451 A2 EP 1717451A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
pressure
damping
projection
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.)
Withdrawn
Application number
EP06112109A
Other languages
German (de)
English (en)
Other versions
EP1717451A3 (fr
Inventor
Michel Duby
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1717451A2 publication Critical patent/EP1717451A2/fr
Publication of EP1717451A3 publication Critical patent/EP1717451A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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 invention relates to a fluid-actuated working cylinder having the features of the preamble of claim 1, in which therefore the piston is decelerated when entering an end position by throttling the pressure fluid outflow from the decreasing cylinder chamber.
  • throttling the outflowing pressure medium flow pressure is built up in the decreasing cylinder chamber, which generates a force on the piston, which is opposite to the movement of the piston.
  • the so-called damping pressure building up in the cylinder chamber should not exceed a maximum value which is 1.5 to 2 times as great as the nominal pressure of the working cylinder.
  • the cylinder has maximum damping capacity when the damping pressure during the entire damping distance has the maximum value.
  • this ideal course of the damping pressure can only be achieved by designing the throttle cross-sections and the throttle lengths between the damping element and the passage opening, if the same boundary conditions are always met, ie if the working cylinder, for example, is always driven at the same speed and moves the same mass.
  • a fluid-actuated working cylinder having a piston with the features of the preamble of claim 1 is known from DE 198 36 422 A1 known.
  • a damping element is arranged, which at the inlet of the piston in the one end position dips into a passage opening between the cylinder chamber and a cylinder port and forms with the passage opening an annular throttle gap for throttled outflow of pressure medium from the cylinder chamber to the cylinder port.
  • the outer surface of the damping element in the axial direction is shaped such that, viewed at fully immersed damping element, at the chamber-side beginning of the passage opening has a maximum diameter and after a surface portion with a small Diameter or small diameters in large immersion depth of the damping element over a short distance has an average diameter which is between the maximum diameter and the small diameter.
  • the object of the present invention is to eliminate the disadvantages of the prior art and to provide a fluid-operated cylinder, by which an overpressure is controlled degradable during a movement of a piston.
  • a throttle gap is provided by the interaction of an inner peripheral wall of the passage opening with the outer peripheral wall of the piston whose cross-section is maximum, if this is limited by a recess on the inner peripheral wall or the outer peripheral wall with a projection on the other peripheral wall, and its Cross-section is minimal, if radially offset by displacement of the piston projections of the two peripheral walls.
  • the recess By forming the recess in the form of mutually spaced annular grooves, between which the projections are present, a meandering design of the throttle gap is made, whereby a good controllability for the reduction of the overpressure during the movement of the piston is ensured.
  • the maximum throttle gap ie a throttle gap with a maximum clearance
  • a projection on the other circumferential wall is disposed opposite to a respective annular groove on a circumferential wall, while a minimum throttle gap is present when a projection on a circumferential wall is opposed to a projection on the other circumferential wall.
  • a trapezoidal configuration of the annular groove ensures a uniform transition between states with maximum and minimum throttle gap.
  • axial length of the groove bottom of the annular groove in a circumferential wall is equal to or greater than the axial length of the apex of the projection on the other circumferential wall, a constant cross section can be achieved at the maximum throttle gap via the axial extent of the passage opening.
  • Fig. 1 shows a hydraulically operated cylinder of the so-called rotary type, wherein on the left side of the sectional view of the extended position is shown and on the right side of the sectional view of the retracted position is shown.
  • the cylinder housing 10 has as essential components a cylinder tube 11, a cylinder head 12 which is placed on the one end, and a cylinder bottom 13 which is placed on the other end of the cylinder tube 11.
  • the cylinder tube 11, the cylinder head 12 and the cylinder bottom 13 are fastened together.
  • a piston 20 is slidably guided axially, which divides the interior of the cylinder tube into two cylinder chambers 21 and 22 whose volumes change in opposite directions during a movement of the piston.
  • hydraulic pressure medium can be supplied to the cylinder chamber 21 and removed therefrom.
  • the radially arranged cylinder port 23 initially opens into a chamber 24 in the cylinder head 12, which is fluidically connected to the cylinder chamber 21 via an axial passage opening 25 of certain diameter.
  • the piston 20 carries a piston rod 35 which passes through the cylinder head 12 to the outside and forms with the chamber 24 and the passage opening 25 of the cylinder head 12 annular spaces.
  • the piston 20 is screwed from the inner end to a reduced-diameter portion of the piston rod 35.
  • a damping bush 36 is guided on the piston rod 35.
  • the damping bush 36 is axially movable by a small distance.
  • the shoulder 35b facing end face is smooth and level and can be sealing against the shoulder 35b.
  • the piston 20 facing end side of the damping bushing 36 has two opposing radially extending recesses 29.
  • the damping bushing has on its inside two opposing axially extending grooves 30, which have the same angular position as the two recesses in the piston-facing end face and a central circumferential recess 31 on the inside to cross. In Figure 1, only one of the grooves is drawn to show that the damping bushing is guided.
  • an axially projecting damping pin 37 is formed, which dips into the passage opening 28 when the cylinder is retracted (right in Fig. 1).
  • a fluid channel leading through the damping pin 37 is created between the cylinder chamber 22 and the cylinder port 26.
  • a check valve 34 is arranged, which closes to the cylinder port 26 through.
  • the damping bushing 36 can dive into the passage opening 25 with little radial clearance and has the function of a throttle body.
  • the damping pin 37 can dive with little radial clearance in the passage opening 28 and also has the function of a throttle body.
  • FIG. 2 shows a plan view of the damping bushing 36 and the damping pin 37 in a schematic representation, in which the length of the cylinder tube 11 is shown shortened. From Fig. 2 it is apparent that extending in the axial direction of the piston rod 35 peripheral surfaces of damping bush 36 and damping pin 37 with grooves, ie with a sequence of annular grooves, are provided. The remaining between the annular grooves Sections are referred to below as projections. These allow for improved damping.
  • 3A shows a sectional view of the throttle gap, which is provided between the damping bushing 36 and the axial passage opening 25, more precisely between the peripheral walls 36a and 25a of the damping bushing 36 and the axial passage opening 25, in the axial direction of the piston rod 36.
  • the peripheral wall 36a of the damper bush 36 has projections 1 and grooves 2 formed between projections 1 adjacent to the piston rod in the axial direction.
  • the grooves 2 are preferably trapezoidal in axial section, wherein the leading from the grooves 2 to a vertex 1a of the projection 1 flanks 2b, 2c are inclined with respect to the axial direction of the piston rod at an acute angle.
  • the groove bottom 2a of the groove 2 preferably extends parallel to the apex 1a of the projection 1.
  • the peripheral wall 25a of the passage opening 25 has, in the same way as the peripheral wall 36a of the damping bushing 36, projections 3 and annular grooves 4 with a vertex 3a and flanks 4b, 4c of the annular grooves 4 leading to the vertex.
  • the axial length l n of the groove bottom 2a of the circumferential wall 36a of the damping bush 36 is greater than the axial length l s of the apex 3a of the peripheral wall 25a of the passage opening 25, as shown in Fig. 3C.
  • the axial length of the groove bottom 4a of the peripheral wall 25a of the passage opening 25a is greater than the axial length of the apex 1a of the peripheral wall 36a of the damping bushing 36.
  • the sum of the axial dimensions of groove base 4a, vertex 3a and flanks 4b and 4c of the circumferential wall 25a of the passage opening 25 is equal to the sum of the axial lengths of groove base 2a, vertex 1a and flanks 2b and 2c of the circumferential wall 36a of the damping bush 36 at the furthest opened throttle gap, a meandering opening for the pressure medium, as shown in Fig. 3A.
  • the axial length of the apex of the peripheral wall of the passage opening is equal to the axial length of the groove bottom of the circumferential wall of the damping bushing. This results in a smaller cross-section of the throttle gap in the areas between vertex and groove bottom of the peripheral walls, which must be taken into account in the dimensioning of the other parameters of the throttle gap.
  • the grooves 2 and 4 on the peripheral walls 25a, 36a are formed with the same pitch over the axial length and rotationally symmetrical.
  • the grooves 4 can be formed, for example, in the manufacture of the passage opening 25, while the grooves 2 in the limiting section 36a by the introduction into a planar peripheral surface of the damping bushing 36 are formed.
  • the present invention is not limited thereto, and the peripheral walls 25a, 36a can be manufactured by any manufacturing method for properly forming the throttle gap.
  • the dimensions of the projections 5, 7 and the grooves 6, 8 on the damping pin 37 and the passage opening 28 may be the same as in the damping bush 36 and the passage opening 25 or different from these.
  • the number of projections at the passage opening 28 (right in Fig. 1) is lower than that of the projections at the passage opening 25 (left in Fig. 1), whereby a faster reduction of the overpressure in the in Fig. 1 right cylinder chamber 22 results.
  • the number of protrusions may be the same.
  • the damping pin 37 is located in the cylinder bottom 13, as can also be seen from the schematic illustration in FIG. 2, but with its side of the stator at a distance from a wall of the cylinder bottom 13. If pressure medium is now supplied to the cylinder port 26, pressure medium can flow unthrottled into the cylinder chamber 32 through the bores 32 and 33 and the check valve 34. The piston 20 moves with one of the flowing over the cylinder port 26 pressure medium quantity speed to the cylinder head 12, wherein pressure medium from the decreasing cylinder chamber 21 via the passage opening 25 and the cylinder port 23 is displaced. Towards the end of the maximum stroke of the piston 20, the damping bush 36 begins to immerse in the passage opening 25.
  • the cylinder port 23 is supplied with pressurized fluid.
  • An overpressure subsequent to the pressure in the cylinder chamber 21 presses the damping bushing away from the shoulder 35b of the piston rod and against the piston 20.
  • the radial gap between the shoulder 35b and the corresponding end face of the damping bush 36 and over the grooves 30, Auswindung 31 and the recesses 29 in the damping bushing open a further unthrottled fluid path from the cylinder port 23 to the cylinder chamber 21.
  • the damping bush 36 thus operates as part of a throttle check valve. In one direction, pressurized fluid can largely unthrottled in the other direction flow only throttled.
  • the throttle gap can be formed in different ways.
  • the axial length of the apex 1a at the peripheral wall 36a of the damping bush 36 with a smaller distance to the piston 20 compared to the axial length of the vertex on the peripheral wall boundary portion 36a be spaced apart from the piston 20, whereby the paths in which the pressure medium is compressed, are increased, while the ways in which the pressure is reduced, can be reduced ,
  • the number of recesses on the circumferential walls of the damping bush 36, the damping pin 37 and the passage openings 25, 28 is determined by the desired path / pressure curve.
  • the invention relates to a fluid-actuated working cylinder with a piston which is axially displaceable in a cylinder space.
  • a throttle gap is effective, which is limited by recesses and depressions in the throttle gap forming peripheral walls.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
EP06112109A 2005-04-01 2006-03-31 Vérin Withdrawn EP1717451A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510015091 DE102005015091A1 (de) 2005-04-01 2005-04-01 Druckmittelbetätigter Arbeitszylinder

Publications (2)

Publication Number Publication Date
EP1717451A2 true EP1717451A2 (fr) 2006-11-02
EP1717451A3 EP1717451A3 (fr) 2007-04-04

Family

ID=36649154

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06112109A Withdrawn EP1717451A3 (fr) 2005-04-01 2006-03-31 Vérin

Country Status (2)

Country Link
EP (1) EP1717451A3 (fr)
DE (1) DE102005015091A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102108990B (zh) * 2010-07-23 2011-12-28 三一重工股份有限公司 一种液压油缸及液压缓冲系统、挖掘机和混凝土泵车
CN102108991B (zh) * 2010-07-23 2012-09-12 三一重工股份有限公司 一种液压油缸及液压缓冲系统、挖掘机和混凝土泵车
CN102108989B (zh) * 2010-07-23 2011-12-28 三一重工股份有限公司 一种液压油缸及液压缓冲系统、挖掘机和混凝土泵车
DE102012217531A1 (de) * 2012-09-27 2014-03-27 Jungheinrich Aktiengesellschaft Hydraulikzylinder mit unter Verwendung einer Spiralnut realisierter Ausfahrdämpfung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3913451A (en) * 1974-08-30 1975-10-21 Cincinnati Milacron Inc Hydraulic cylinder with cushioning means
JPS56164209A (en) * 1980-05-23 1981-12-17 Toshiba Mach Co Ltd Cylinder
JPS61124706A (ja) * 1984-11-16 1986-06-12 Taiyo Tekko Kk クツシヨン装置付きエア−シリンダ
US4651623A (en) * 1984-12-07 1987-03-24 American Standard Inc. Work cylinder having a piston member with an integral cushioning arrangement

Also Published As

Publication number Publication date
EP1717451A3 (fr) 2007-04-04
DE102005015091A1 (de) 2006-10-05

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