EP1744062A2 - Vérin avec amortissement de fin de course - Google Patents

Vérin avec amortissement de fin de course Download PDF

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Publication number
EP1744062A2
EP1744062A2 EP06012469A EP06012469A EP1744062A2 EP 1744062 A2 EP1744062 A2 EP 1744062A2 EP 06012469 A EP06012469 A EP 06012469A EP 06012469 A EP06012469 A EP 06012469A EP 1744062 A2 EP1744062 A2 EP 1744062A2
Authority
EP
European Patent Office
Prior art keywords
piston
working cylinder
damping
cylinder according
sleeve
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.)
Granted
Application number
EP06012469A
Other languages
German (de)
English (en)
Other versions
EP1744062B1 (fr
EP1744062A3 (fr
Inventor
Ralph Riedel
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.)
Norgren GmbH
Original Assignee
Norgren GmbH
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 Norgren GmbH filed Critical Norgren GmbH
Publication of EP1744062A2 publication Critical patent/EP1744062A2/fr
Publication of EP1744062A3 publication Critical patent/EP1744062A3/fr
Application granted granted Critical
Publication of EP1744062B1 publication Critical patent/EP1744062B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/082—Characterised by the construction of the motor unit the motor being of the slotted cylinder type
    • 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

  • pressure-actuated working cylinders are often designed with a Endlagendämfpung to ensure a bumpless working of the cylinder.
  • An example of such a fluid-actuated cylinder with cushioning is in the US-PS 6,758,127 described.
  • an axially projecting tubular, cylindrical damping pin is provided on the piston at both end faces, which in the end portion of the cylinder body facing it is associated with a receiving opening into which the damping pin is immersed in the approach of the piston to its end position.
  • the receiving opening is connected to a device for throttled discharge of trapped in the damping chamber pressure medium. This device may for example have a throttle valve.
  • damping stroke The path length, the piston covers when approaching an end position from the position in which the damping pin begins to penetrate straight into the receiving opening and the damping chamber closes up to the position in which the piston has reached its actual end position and, for example, with its end face rests on the end face of the associated end part, is referred to as damping stroke.
  • the length of this damping stroke is determined by the axial length of the damping pin and thus the depth of the receiving opening, which in turn is limited by the axial dimensions, ie the thickness of the end portion. Since the installation length of a working cylinder is often specified, for example by standards, for a given piston stroke and the damping stroke can not be made arbitrarily large.
  • the control piston serves as a shut-off device and valve for outflow channels, which forms a damping storage space at the respective end portion of the working cylinder in the system of the control piston, can flow out of the fluid via a throttled outflow hole. While this cylinder has a longer damping travel or stroke compared to the prior art, the cone spring requires additional installation space, except that the use of spring elements is problematic in many applications because of their limited life.
  • the object of the invention is therefore to provide a cylinder with cushioning, the damping device is characterized by a simple, reliable construction and has a large damping stroke with limited installation length of the entire working cylinder.
  • the working cylinder according to the invention has the features of claim 1.
  • the device for damping the movement of the piston when approaching at least one of its end positions on two cooperating damping elements one of which is provided on one end portion of the working cylinder and the other on the piston on the end portion facing side.
  • the two end parts close at the approach of the piston to its end position a damping chamber, with a device connected to the throttled derivative of enclosed in the damping chamber pressure medium.
  • the two damping elements in the direction of the piston movement telescopically axially inserted into one another by about one of the two damping elements formed in the end part or the piston receiving opening and the other has a sealed inserted into the receiving opening, telescopic damping pin.
  • the damping pin has in a preferred embodiment, a sleeve which is mounted axially limited displaceable on a to the piston or the end portion axially projecting rod-shaped bearing member.
  • the bearing part can be directly part of the piston rod.
  • damping elements at least one of the end part or the piston between two axially spaced apart end positions relative to the piston or the end part limited longitudinally displaceable.
  • Both damping elements are provided with cooperating inhibiting means under the action of the longitudinally displaceable damping element is adjustable in a movement of the piston from its end position to an end position which is further away from the piston or the end portion as a first end position, which normally occupies the damping element.
  • the displaceability of the one damping element with respect to the piston or the end part results in an additional damping stroke by a telescopic action of the telescoping action of the piston as it approaches its end position: parts.
  • the inhibitor ensures that when moving away of the piston from its end position, the longitudinally displaceable damping element returns to its original position, without the need for additional actuation devices, such as spring elements or the like. This also no additional installation space is required.
  • the simple design also allows the use of near-serial parts for large damping strokes, ie long damping paths.
  • the working cylinder may be both a single-acting and double-acting working cylinder with a piston rod brought out through at least one of its end parts, but the idea according to the invention can likewise be applied to rodless cylinders.
  • the working cylinders are usually pressure medium actuated, for example. Pneumatic cylinder, but a corresponding device for cushioning can also be provided in working cylinders or linear drives, which have a different form of operation, for example. Over cables and the like.
  • Figures 1 to 7 illustrate a working cylinder in the form of a pneumatic cylinder having a cylinder body in the form of a cylinder tube 1 and two sealed with the cylinder tube 1 end portions 2, 3.
  • the cylinder tube 1 encloses a cylinder space in which a piston 4 is guided longitudinally displaceable, which is sealed against the inner wall of the cylinder tube 1 via piston ring seals 5.
  • the piston 4 divides the cylinder space into two cylinder or pressure chambers 6, 7, which are separated by the piston 4.
  • a coaxial cylindrical piston rod 8 is fixedly connected, which is sealed by the end part 2 is guided by.
  • a piston rod seal is illustrated at 9.
  • the cylinder chamber 6 passing through the piston rod 8 is extended on the opposite side of the piston.
  • On its extension 10 a coaxial cylindrical sleeve 11 is placed, which projects into the cylinder chamber 7 and is fixed by a 12 indicated, bolted to the piston rod extension 10 screw on the piston 4.
  • each opening into a threaded bore 13 connecting channel 14 is formed, which via a corresponding screwed connection fitting with a compressed air source not shown or a vent, in each case via corresponding, also not shown valves, can be connected and opens on its other side in each case in a cylindrical, cup-shaped receiving opening 15, which opens on the piston 4 side facing the respective end portion 2 and 3 to the cylinder chamber 6 and 7 out.
  • the coaxial to the piston rod receiving opening 15 is closed in both end portions 2, 3 on the side facing away from the piston 4, which is achieved at the end part 2 by the piston rod seal 9, while the receiving opening 15 in the other end part 3 by a molded-bottom part 16th is completed.
  • Each of the two receiving openings 15 includes an inserted into an annular groove 18 in the vicinity of its mouth, around running elastic sealing element in the form of an O-ring 20th
  • the axial depth of the two receiving openings 15 is usually the same and dimensioned so that there is a maximum depth 21 without lengthening the installation length of the working cylinder.
  • the receiving opening 15 in each of the two end portions 2, 3 each forms a damping element of a device for cushioning the piston 4. It cooperates for this purpose with a second damping element, which is provided on the piston 4 and each having a telescopic damping pin which at the approach of the piston at its respective end position in the respective receiving opening 15 is sealingly inserted to limit a damping chamber, the pressure medium includes, which causes a throttling of the piston movement in the throttled outflow from the receiving opening a pneumatic damping.
  • the cooperating with the receiving opening 15 second damping element has a cylindrical sleeve 19 which is mounted on the end part 2 facing the side of the piston 4 on the piston rod 8 and on the other end part 3 facing the piston side on the cylindrical sleeve 11 each axially limited longitudinally displaceable.
  • the sleeve 19 is chamfered on its side facing the respective end part 2, 3 at 22 outside and at its opposite end with an annular flange 23 which carries a respective end portion 2, 3 facing stop surface 24.
  • the annular flange 23 of each of the two sleeves 19 is assigned in each case an annular groove 25 in the piston end face facing it, which can receive the annular flange 24 completely, as will be explained in detail yet.
  • each sleeve 19 is formed in the region of its inner wall with an annular shoulder 26, with a corresponding annular shoulder 27 near the free end of the tube 11 on the one piston side and an annular shoulder 28 on the Piston rod 8 cooperates on the other side of the piston.
  • annular shoulders 27, 28 are spaced so far from the adjacent piston end face and matched to the length of the sleeve 19, that in the illustrated in Figure 1 first piston remote end position in which the annular shoulders 26, 27 and 26, 28 abut each other, the two sleeves 19 are with their annular flange 23 in the same axial distance from the adjacent piston end face and that in a second piston near end position of the flange 24 is respectively completely received in the annular groove 25, as shown in Figure 6 for the end part 3 associated sleeve 19 is.
  • the two sleeves 19 are releasably locked.
  • the associated latching device has an in an annular groove 29 and 30 of the piston rod 8 and the sleeve 11 inserted latching element in the form of an O-ring 31 which cooperates with a locking recess 32 on the inner wall of the sleeve 19 elastically yielding.
  • the end portion 3 adjacent sleeve 19 protrudes axially over a large part of its length over the sleeve 11, while the other sleeve 19 rests on a larger diameter portion of the piston rod 8 over most of its length.
  • locking can alternatively occur a frictional locking of the sleeves.
  • an all-round annular bead 32 is formed, which can cooperate with the respective O-ring 20 in the end part 2 and 3 and together with this inhibiting means for each of the respective End portion directed away axial movement of the sleeve 19 in the manner described below.
  • the two receiving openings 15 in the end parts 2, 3 are each provided with a device for throttled discharge of pressure medium enclosed in the damping space enclosed by the piston 4, the cylinder space or 7 and the end part 2 and 3, respectively.
  • this device includes a throttle valve 33, which is illustrated in detail "Y" of Figure 2.
  • the throttle valve 33 is inserted into a corresponding bore 34 of the respective end part 2 or 3, which via a coaxial channel 35 with the receiving opening 15 and a laterally outgoing channel 36th is in communication with the cylinder chamber 6 and 7, respectively.
  • the throttle valve 33 has a valve body 37 which is pressed by a valve spring 38 elastically against a valve seat 39, wherein the valve spring 39 is axially supported against a screwed into the bore 34 plug 40.
  • the valve body 37 is formed in the manner of a differential piston. If the same medium pressure prevails in the two channels 35, 36, the valve spring 38 can hold the valve body 37 on the valve seat 39 and thus the throttle valve closed (FIG. 2). If the pressure in the damping chamber, and thus in the channel 35, increases by a preset value, the valve body 37 is lifted off the seat 39 accordingly.
  • a throttle channel 40 of small cross-section is formed, through which air can flow out of the damping chamber into the adjacent pressureless cylinder chamber 6 or 7 when the valve is closed.
  • the throttle channel 40 acts as a bypass channel.
  • the path of the piston 4 from the stroke position, in which the damping chamber is formed in the cylinder chamber 7 straight to the end position in Fig. 6, is referred to as the damping stroke 41. If, as is the case in principle in the prior art, only one uniform damping pin is connected to the piston 4, the damping stroke would only be the one indicated by 42 in FIG. 4 (small path), which is essentially defined by the stop surface 24 calculated from calculated axial length of the sleeve 19 is determined. Since the sleeve 19 is mounted longitudinally displaceably on the sleeve 11, there is a telescopic effect, by which the damping stroke 41 is increased in comparison to the mentioned damping stroke 42 to almost twice.
  • Rodless cylinders are known in various embodiments. Examples are in the EP 0 260 344 B1 and the US-A 4,373,427 described. In such working cylinders, the peg-shaped damping element is often firmly connected to the end parts of the cylinder, wherein the damping element during the movement of the piston against the end position enters into this. There are, as the US patent shows, reverse constructions have been proposed, but then leads to correspondingly thick end parts. If the damping element is arranged at the respective end part, the space already present in these working cylinders in the piston is advantageously utilized for the pneumatic damping and the end parts can be kept relatively short and independent of the damping length. The invention makes it possible to achieve substantially longer damping paths without lengthening the installation length of the cylinder even in these cases, as can be seen conspicuously from FIG. 8:
  • the tubular cylinder body 51 is closed at the ends by two end parts 52, 53 and encloses a cylinder space in which a piston 54 is guided longitudinally displaceable.
  • the cylinder body 51 is provided with a longitudinal slot through which a web connected to the piston 54 leads outwardly to a power transmission element 55.
  • the longitudinal slot is closed by an elastic sealing band 56 which is in two parts and which Cylinder or pressure chamber 57, 58 seals on both sides of the piston 54 to the outside.
  • Each of the two end portions 52 carries a projecting into the respective cylinder chamber 57 and 58, tubular bearing part 59, which is aligned coaxially with the piston 54.
  • a sleeve 19 is mounted longitudinally displaceably according to the figures 1 to 7, which is associated with a coaxial cylindrical receiving opening 15 in the opposite end face of the piston 54.
  • the sleeve 19 is as shown in particular in Figure 3, designed and stored. The same parts are provided with the same reference numerals and not explained again.
  • the tubular bearing parts 59 each open into a channel 60 which leads to a throttle valve 33, similar to FIG. 2. Structure and effect of this valve are, as already explained with reference to Figure 2, so that even here a further explanation is unnecessary.
  • Figure 8 shows the rodless cylinder in a stroke position in which the damping element forming a left sleeve 19 in the extended end position, that is shown away from the end portion 52. Again, holds a detent or possibly just a frictional engagement between the bearing part 59 and the sliding sleeve 19 formed by this, displaceable damping element in the extended position.
  • Upon movement of the piston in the direction of the left end position to the sleeve 19 is first inserted into the receiving opening 15, whereupon the sleeve itself on the bearing part 59 until it rests against the end part 52 is pushed telescopically.
  • a detent or a simple frictional engagement between the sleeve 19 and the inhibiting means forming O-ring 20 ensures that the displaceable damping element forming sleeve 19 is brought back in a piston movement away from the end portion 52 in the extended end position shown in Figure 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
  • Vibration Dampers (AREA)
EP06012469A 2005-07-14 2006-06-17 Vérin avec amortissement de fin de course Not-in-force EP1744062B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005032853A DE102005032853B3 (de) 2005-07-14 2005-07-14 Arbeitszylinder mit Endlagendämpfung

Publications (3)

Publication Number Publication Date
EP1744062A2 true EP1744062A2 (fr) 2007-01-17
EP1744062A3 EP1744062A3 (fr) 2009-07-22
EP1744062B1 EP1744062B1 (fr) 2011-11-23

Family

ID=37076268

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06012469A Not-in-force EP1744062B1 (fr) 2005-07-14 2006-06-17 Vérin avec amortissement de fin de course

Country Status (7)

Country Link
US (1) US7581485B2 (fr)
EP (1) EP1744062B1 (fr)
CN (1) CN1896552A (fr)
AT (1) ATE534825T1 (fr)
DE (1) DE102005032853B3 (fr)
DK (1) DK1744062T3 (fr)
ES (1) ES2378077T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102155457A (zh) * 2010-07-23 2011-08-17 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
CN102155458A (zh) * 2010-07-23 2011-08-17 三一重工股份有限公司 一种液压油缸及其相关装置、及液压缓冲系统、挖掘机和混凝土泵车

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JP2008133920A (ja) * 2006-11-29 2008-06-12 Smc Corp 流体圧シリンダ
US8863645B2 (en) * 2007-03-28 2014-10-21 Norgren Gmbh Piston support portion for a piston assembly of a rodless cylinder
DE102009016198B4 (de) 2009-04-03 2013-01-17 Festo Ag & Co. Kg Fluidbetätigter Linearantrieb mit Endlagendämpfung
JP5360564B2 (ja) 2009-06-03 2013-12-04 Ｓｍｃ株式会社 空気圧シリンダのエアクッション機構
DE102009056496A1 (de) 2009-12-01 2011-08-04 FESTO AG & Co. KG, 73734 Drosselventil
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
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
WO2012041786A1 (fr) * 2010-09-28 2012-04-05 Norgren Gmbh Vérin à amortissement
KR20130128394A (ko) * 2010-11-15 2013-11-26 볼보 컨스트럭션 이큅먼트 에이비 가변 쿠션 오리피스를 구비한 유압실린더
CN102705299A (zh) * 2012-05-17 2012-10-03 太仓奥科机械设备有限公司 气缸缓冲装置
US9103357B2 (en) 2012-09-29 2015-08-11 Shenzhen China Star Optoelectronics Technology Co., Ltd Cylinder
CN102852895B (zh) * 2012-09-29 2015-07-15 深圳市华星光电技术有限公司 一种气缸
CN106545547A (zh) * 2015-09-19 2017-03-29 嘉兴大道锻造技术咨询有限公司 一种缓冲气缸
CN106593989B (zh) * 2017-02-04 2018-08-31 三一汽车制造有限公司 一种液压油缸、液压系统及工程机械
IT201900001511A1 (it) * 2019-02-01 2020-08-01 Cnh Ind Italia Spa Cilindro idraulico migliorato per veicolo da lavoro
JP7447689B2 (ja) * 2020-06-10 2024-03-12 Smc株式会社 ガスシリンダ
JP7323103B2 (ja) * 2020-07-22 2023-08-08 Smc株式会社 流体圧シリンダ
WO2022074284A1 (fr) * 2020-10-08 2022-04-14 Pimatic Oy Agencement dans un vérin pneumatique
CN113931961B (zh) * 2021-09-09 2023-03-28 神龙汽车有限公司 一种新型液压自适应阻尼调节减震器

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US3999463A (en) 1975-02-27 1976-12-28 Componetrol, Inc. Fluid motor construction
DE3818833A1 (de) 1988-06-03 1989-02-02 Dimter Erwin Kolben fuer druckluftzylinder, insbesondere fuer kolbenstangenlose zylinder
DE29706364U1 (de) 1997-04-10 1997-06-19 Buemach Engineering Internatio Endlagengedämpfter Arbeitszylinder
JPH11132203A (ja) 1997-10-28 1999-05-18 Hitachi Constr Mach Co Ltd 油圧シリンダのクッション装置
US6758127B2 (en) 2000-12-20 2004-07-06 Imi Norgren Gmbh Pressurized medium activated working cylinder

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US2786452A (en) * 1954-11-29 1957-03-26 Hannifin Corp Fluid actuated cylinder having fluid cushion means
US3067726A (en) * 1961-02-27 1962-12-11 Int Basic Economy Corp Cushioning structure for fluid power cylinders
US3196753A (en) * 1963-05-21 1965-07-27 Tomkins Johnson Co Cushion control and surge relief
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US4301714A (en) * 1979-05-24 1981-11-24 Ab Mecman Damping device in pressurized fluid cylinders
DE3631514A1 (de) * 1986-09-17 1988-03-24 Proma Prod & Marketing Gmbh Druckmittelzylinder
SE467424B (sv) * 1990-11-09 1992-07-13 Mecman Ab Anordning foer aendlaegesdaempning och hastighetsreglering av roerelsen hos en kolv i en tryckmediecylinder
GB9421002D0 (en) * 1994-10-18 1994-12-07 Norgren Martonair Gmbh Fluid powered cylinder

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Publication number Priority date Publication date Assignee Title
US3999463A (en) 1975-02-27 1976-12-28 Componetrol, Inc. Fluid motor construction
DE3818833A1 (de) 1988-06-03 1989-02-02 Dimter Erwin Kolben fuer druckluftzylinder, insbesondere fuer kolbenstangenlose zylinder
DE29706364U1 (de) 1997-04-10 1997-06-19 Buemach Engineering Internatio Endlagengedämpfter Arbeitszylinder
JPH11132203A (ja) 1997-10-28 1999-05-18 Hitachi Constr Mach Co Ltd 油圧シリンダのクッション装置
US6758127B2 (en) 2000-12-20 2004-07-06 Imi Norgren Gmbh Pressurized medium activated working cylinder

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102155457A (zh) * 2010-07-23 2011-08-17 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
CN102155458A (zh) * 2010-07-23 2011-08-17 三一重工股份有限公司 一种液压油缸及其相关装置、及液压缓冲系统、挖掘机和混凝土泵车
CN102155458B (zh) * 2010-07-23 2012-07-04 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
CN102155457B (zh) * 2010-07-23 2012-07-18 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

Also Published As

Publication number Publication date
CN1896552A (zh) 2007-01-17
ES2378077T3 (es) 2012-04-04
DE102005032853B3 (de) 2007-02-08
US20070012532A1 (en) 2007-01-18
DK1744062T3 (da) 2011-12-19
ATE534825T1 (de) 2011-12-15
EP1744062B1 (fr) 2011-11-23
US7581485B2 (en) 2009-09-01
EP1744062A3 (fr) 2009-07-22

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