EP1447571A1 - Cylindre à amortissement de fin de course réglable - Google Patents

Cylindre à amortissement de fin de course réglable Download PDF

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Publication number
EP1447571A1
EP1447571A1 EP04100496A EP04100496A EP1447571A1 EP 1447571 A1 EP1447571 A1 EP 1447571A1 EP 04100496 A EP04100496 A EP 04100496A EP 04100496 A EP04100496 A EP 04100496A EP 1447571 A1 EP1447571 A1 EP 1447571A1
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EP
European Patent Office
Prior art keywords
piston
end position
damping
pneumatic cylinder
stop element
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
EP04100496A
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German (de)
English (en)
Other versions
EP1447571B1 (fr
Inventor
Ernst-August Meyer
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.)
Aventics GmbH
Original Assignee
Rexroth Mecman 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
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Application filed by Rexroth Mecman GmbH filed Critical Rexroth Mecman GmbH
Publication of EP1447571A1 publication Critical patent/EP1447571A1/fr
Application granted granted Critical
Publication of EP1447571B1 publication Critical patent/EP1447571B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B15/223—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 completely seals the main fluid outlet as the piston approaches its end position

Definitions

  • the invention relates to a cushioned pneumatic cylinder, in the Cylinder housing axially movable a piston which can be acted on at least on one side is housed, with at least one of the two pressure chambers formed thereby with Means for adjustable cushioning of the end position is equipped.
  • End position-damped pneumatic cylinders with constant Damping length as well as with variable damping length.
  • this cannot be changed, i.e. the operating conditions to adjust.
  • the damping length for pneumatic cylinders is more variable The damping length can be changed to adjust the end position damping depending on the application of the piston.
  • Such a generic end position damped device is known from DE 44 10 103 C1 Pneumatic cylinder with variable damping length.
  • an electronic Control unit in the form of a counter pulse module via assigned discrete Prepositioning sensors a time-adjustable reversal of a powered first, one control valve assigned to the first end position on a previously non-energized second one second control valve associated end position.
  • the counter pulse duration can be varied, which is practically without power Approaching the end position at low speed allows. This Measures influence the effective damping length, which is flexible about the electronic control unit is variable.
  • DE 196 45 701 A1 describes another generic end position damped device Pneumatic cylinder with variable damping length.
  • the damping is here by means of generated a control valve assembly through which the flowing compressed air at least is throttled at times.
  • the control valve assembly has compressed air connections and Control connections that are connected to an electronic control unit.
  • the control valve arrangement has throttling of the compressed air flow in addition to a first one Passage cross section a second, smaller passage cross section and a Switch valve for switching between the two passage cross sections. By the Switching to the smaller passage cross-section temporarily throttles the Compressed air supply in the pressure medium cylinder for end position damping.
  • the invention includes the technical teaching that as a means for an adjustable End position damping is spaced on the end face of the piston via compression spring means attached, at least partially iron-metallic stop element is provided, which in a basic position G near the piston due to the magnetic force of at least one Permanent magnet is fixed to the piston, and which is in a working position remote from the piston A protrudes into the adjacent pressure chamber for end position damping, one outside adjustable along the cylinder housing to determine the damping length Magnetic element for generating a magnetic field opposite the permanent magnet essentially inverted magnetic field is provided to a change in position of the To achieve stop element from the basic position G to the working position A if the Piston passes the magnetic element shortly before the end position is reached.
  • the advantage of the solution according to the invention is in particular that with a Adjustment of the magnetic element attached to the outside of the cylinder housing Damping length can be flexibly adapted to any application. This adjustment takes place in manually in a simple manner without the need for control engineering.
  • the damping strength can also be adjusted manually using an adjustable throttle in conventional Way to be adjusted.
  • the mechanical solution according to the invention for End position damping requires only a small additional component expenditure, which Compactness of the pneumatic cylinder is not affected. So above all the length of the Pneumatic cylinder is not enlarged by this.
  • a particularly reliable hold of the ferrous metal stop element in the Basic position G near the piston results when the permanent magnet is hollow-cylindrical is designed, adapted to a preferably ring-like configuration of the stop element, wherein the compression spring means carrying the stop element from the hollow cylindrical Permanent magnet is at least partially enclosed.
  • This relative arrangement of the said components to each other also ensures their compact Housing within the limited space in the piston.
  • the compression spring means is preferably in the manner of a spiral compression spring or in the manner of a Formed elastomer bellows, which is attached to the piston on the one hand and on the other hand the stop element carries. It is conceivable that the pressure spring means itself through its Spring effect contributes to cushioning.
  • the compression spring means preferably has however, only a low specific spring constant, which is dimensioned so that a Axial movement of the stop element from the basic position G near the piston rebounding into the working position A remote from the piston is ensured.
  • the end position damping is preferably such that the stop element in the Working position A remote from the piston when the piston approaches the end position from when it is reached one defined by the axial spacing of the stop element from the piston Damping distancecs X a corresponding arranged in the associated cylinder cover The opening closes, so that only the exhaust air escaping from the pressure chamber the residual flow cross-section made available through a second bypass opening remains.
  • the stop element advantageously consists of different ones Materials, namely on the side facing the piston made of iron and on the opposite side facing the cylinder cover made of an elastomer material.
  • the stop element can thus be produced in a simple manner as a rubber-metal part become.
  • the preferably annular stop element corresponds to that in the Cylinder cover provided opening, which for example as an annular gap or as an in a circular row of holes can be formed.
  • an electrical solenoid which is opposite to that in the piston integrated permanent magnet is aligned so that when it is energized magnetic field essentially inverted with respect to the magnetic field of the permanent magnet results, which interferes with the magnetic field of the permanent magnet by this partially will be annulled.
  • the solenoid can be energized via an electronic Control unit take place, which is an optional connection or disconnection of the End position damping enables.
  • the control of the solenoid can be done together with the control of a solenoid valve acting on the pneumatic cylinder, so that a separate control device is not required.
  • Length-adjustable magnetic element attached to the outside of the cylinder housing as one to design permanent magnets, the positioning of which is also appropriate provides inverted magnetic field.
  • the permanent magnet Damping device does not trigger on the return stroke of the piston.
  • suitable technical means for feeding and removing the permanent magnet or to provide the like are suitable technical means for feeding and removing the permanent magnet or to provide the like.
  • the figure shows a longitudinal section through a pneumatic cylinder with end position damping variable damping length.
  • the pneumatic cylinder essentially consists of a cylinder housing 1, in which a piston 2 is axially displaceable.
  • the piston 2 is with two annular Provide sealing elements 3a and 3b, which on the inner wall of the cylinder housing 1st come into contact via appropriate sealing lip sections.
  • the piston 2 divides the Interior of the cylinder housing 1 in two pressure chambers 4a and 4b.
  • the pressure chambers 4a and 4b are further limited by sealingly attached to the end of the cylinder housing 1 Cylinder covers 5a and 5b.
  • a piston rod 6 runs from the piston 2.
  • the piston rod 6 penetrates the cylinder cover 5b in a sealed manner.
  • For sealing the cylinder cover 5b opposite the piston rod 6 is an annular sealing element 7 in the cylinder cover 5b arranged. Axially adjacent to the sealing element 7, the cylinder cover 5b also has one Guide bushing 8, which serves for exact axial guidance of the piston rod 6.
  • two pressure medium connections 9a and 9b are provided in the cylinder covers 5a and 5b.
  • the pressure medium connection 9a is connected to the pressure chamber 4a, whereas the Pressure medium connection 9b serves to act on the pressure chamber 4b.
  • axles are axially arranged on both sides spaced annular stop elements 10a and 10b are provided.
  • the axial spaced attachment of the stop elements 10a and 10b on the piston 2 takes place via a Compression spring means 11a and 11b, which in connection with the present invention perform the main functions, the stop elements 10a and 10b axially in the unloaded state spaced from the piston 2 and easy to move.
  • they provide evidence here kind of a spiral compression spring made of spring steel captivating compression spring means 11a and 11b only low spring constant.
  • the coaxially mounted relative to the piston 2 annular stop elements 10a, 10b correspond to the execution of the End position damping with associated openings 12a and 12b, which here is in the form of a Have annular gap, the shape of the stop element acting as a closure element 10a or 10b is adapted.
  • the stop element is used to improve the sealing effect 10a, 10b to the side of the opening 12a or 12b made of an elastomer material, whereas the opposite side is made of iron.
  • the end position damping is used when the damping distance X is reached Flow cross-section reduced accordingly for the escape of the pressure medium. to insufficient adjustment of the degree of damping is still a throttle screw 14a and 14b, which cooperates with the bypass opening 13a and 13b.
  • Adjustable end position damping is achieved in that the stop element 10a, 10b both a basic position G close to the piston and a working position A remote from the piston can take. (In the figure both positions are shown, which are equally for both damping sides apply.) In the basic position G near the piston, this is ferrous metal Stop element 10b by the magnetic force of a hollow cylindrical permanent magnet 15a, 15b fixed on the piston 2. In the other working position A, which is remote from the piston, this protrudes Stop element 10a - in the manner described above - in the adjacent Pressure chamber 4a into it. On the outside of the cylinder housing 1 there is a magnetic element 16a, 16b manually adjustable along the cylinder housing 1 and releasably attached thereto arranged.
  • the magnetic elements 16a, 16b are designed here as electrical magnetic coils, which can be energized via an electronic control unit (not shown further). When the magnetic elements 16a and 16b are energized, they develop a magnetic field, which in its polarization with respect to the magnetic field generated by the permanent magnet 15a, 15b is inverted. This disturbing weakening of the magnetic field of the permanent magnet 15a or 15b is released due to the compressive force of the compression spring means 11a and 11b Stop element 10a or 10b from its near the piston held by magnetic force Basic position G and reaches its working position A. Now the stop element 10a and 10b ready to carry out a damping function in the sense explained above.
  • the positioning of the magnetic elements 16a or 16b on the outside of the cylinder housing 1 can this triggering moment can be determined so that the damping length can be varied is.
  • the stop element 10a and 10b in again pressed the basic position G, where this is due to the permanent magnet 15a or 15b applied magnetic force is fixed again.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP20040100496 2003-02-12 2004-02-10 Cylindre à amortissement de fin de course réglable Expired - Lifetime EP1447571B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10305954 2003-02-12
DE2003105954 DE10305954B3 (de) 2003-02-12 2003-02-12 Endlagengedämpfter Pneumatikzylinder mit verstellbarer Endlagendämpfung

Publications (2)

Publication Number Publication Date
EP1447571A1 true EP1447571A1 (fr) 2004-08-18
EP1447571B1 EP1447571B1 (fr) 2005-09-07

Family

ID=32404441

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040100496 Expired - Lifetime EP1447571B1 (fr) 2003-02-12 2004-02-10 Cylindre à amortissement de fin de course réglable

Country Status (2)

Country Link
EP (1) EP1447571B1 (fr)
DE (2) DE10305954B3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1729015A1 (fr) 2005-06-03 2006-12-06 FESTO AG & Co Dispositif entraîné par un fluide
EP1918592A1 (fr) 2006-11-03 2008-05-07 Carl Freudenberg KG Joint d'étanchéité avec amortisseur de fin de course, fond avec joint d'étanchéité et vérin pneumatique avec fond et joint d'étanchéité
DE102009034790A1 (de) 2009-07-25 2011-01-27 Robert Bosch Gmbh Zylinder mit Endlagendämpfung
CN105422542A (zh) * 2015-12-22 2016-03-23 扬州捷迈锻压机械有限公司 一种双层退料气缸
CN109530652A (zh) * 2018-11-08 2019-03-29 贵州华昌汽车电器有限公司 一种压铸模具用的接插式不锈钢感应油缸

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2107256A1 (fr) 2008-03-31 2009-10-07 Carl Freudenberg KG Vérin pneumatique à fin de course amortie
EP2107255B1 (fr) 2008-03-31 2011-09-21 Carl Freudenberg KG Vérin pneumatique à fin de course amortie
CN101504019B (zh) * 2008-12-17 2012-05-02 国营第三八八厂 一种永磁缓冲液压缸
DE102010015081A1 (de) 2010-04-15 2011-10-20 Robert Bosch Gmbh Endlagengedämpfter Druckmittelzylinder
DE102017117000A1 (de) * 2017-07-27 2019-01-31 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Verfahren zum Steuern eines Aktuators sowie Aktuator

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63297804A (ja) * 1987-05-29 1988-12-05 Ckd Corp 流体圧シリンダ
DE4322255A1 (de) * 1993-07-05 1995-01-19 Festo Kg Dämpfungsvorrichtung
US5953976A (en) * 1997-04-10 1999-09-21 Buemach Engineering International B.V. Working cylinder with dampened ends

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4410103C1 (de) * 1994-03-21 1995-08-31 Mannesmann Ag Antrieb der fluidischen oder elektrischen Bauart mit einer Steuerung
DE19645701A1 (de) * 1996-11-06 1998-05-07 Wabco Gmbh Ventileinrichtung für eine durch ein Druckmittel betätigbare Türanlage

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63297804A (ja) * 1987-05-29 1988-12-05 Ckd Corp 流体圧シリンダ
DE4322255A1 (de) * 1993-07-05 1995-01-19 Festo Kg Dämpfungsvorrichtung
US5953976A (en) * 1997-04-10 1999-09-21 Buemach Engineering International B.V. Working cylinder with dampened ends

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 013, no. 130 (M - 808) 30 March 1989 (1989-03-30) *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1729015A1 (fr) 2005-06-03 2006-12-06 FESTO AG & Co Dispositif entraîné par un fluide
EP1918592A1 (fr) 2006-11-03 2008-05-07 Carl Freudenberg KG Joint d'étanchéité avec amortisseur de fin de course, fond avec joint d'étanchéité et vérin pneumatique avec fond et joint d'étanchéité
US7866252B2 (en) 2006-11-03 2011-01-11 Carl Freudenberg Kg Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
US8234970B2 (en) 2006-11-03 2012-08-07 Carl Freudenberg Kg Gasket, cover with gasket, and pneumatic cylinder with cover and gasket
DE102009034790A1 (de) 2009-07-25 2011-01-27 Robert Bosch Gmbh Zylinder mit Endlagendämpfung
DE102009034790B4 (de) 2009-07-25 2024-02-01 Aventics Gmbh Zylinder mit Endlagendämpfung
CN105422542A (zh) * 2015-12-22 2016-03-23 扬州捷迈锻压机械有限公司 一种双层退料气缸
CN109530652A (zh) * 2018-11-08 2019-03-29 贵州华昌汽车电器有限公司 一种压铸模具用的接插式不锈钢感应油缸

Also Published As

Publication number Publication date
DE10305954B3 (de) 2004-07-01
EP1447571B1 (fr) 2005-09-07
DE502004000056D1 (de) 2005-10-13

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