EP1042615A1 - Dispositif de travail actionne par un fluide - Google Patents

Dispositif de travail actionne par un fluide

Info

Publication number
EP1042615A1
EP1042615A1 EP99953807A EP99953807A EP1042615A1 EP 1042615 A1 EP1042615 A1 EP 1042615A1 EP 99953807 A EP99953807 A EP 99953807A EP 99953807 A EP99953807 A EP 99953807A EP 1042615 A1 EP1042615 A1 EP 1042615A1
Authority
EP
European Patent Office
Prior art keywords
piston rod
fluid
working
spaces
housing
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
EP99953807A
Other languages
German (de)
English (en)
Other versions
EP1042615B1 (fr
Inventor
Dieter Waldmann
Ernst HÄGELE
Gerald Müller
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.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
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 Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP1042615A1 publication Critical patent/EP1042615A1/fr
Application granted granted Critical
Publication of EP1042615B1 publication Critical patent/EP1042615B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
    • F04B9/135—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting elastic-fluid motors, each acting in one direction
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7055—Linear output members having more than two chambers

Definitions

  • the invention relates to a fluid-operated working device, with a housing, with a piston rod which can be displaced relative to the housing by fluid force, and with at least one control valve which can be actuated as a function of the position of the piston rod and which, by interacting with a sealing region arranged fixed to the housing, provides the fluid connection between two fluid spaces controlling control element contains.
  • Such a fluid-operated working device known to the applicant is designed as a pressure increasing device with which the pressure of a fluid can be increased.
  • a housing that contains two piston chambers in which pistons are located, which are connected to a working unit via a piston rod.
  • the piston chambers are divided into two working spaces by the pistons, with a valve device controlling the external working spaces to produce a reciprocating stroke movement of the working unit.
  • the fluid displaced from the working chambers on the piston rod side during the stroke movement is fed to a high-pressure chamber, in which an increased pressure is thereby built up.
  • control valves integrated into the housing can be provided, the control elements of which protrude into the adjacent piston rod-side working space and are mechanically actuated at the end of the stroke by the bulging piston.
  • a disadvantage of the design described is the failure and lock-prone actuation of the control valves. It has therefore already been proposed to switch the valve device by means of electrical signals, which are generated by sensors which are actuated by the pistons in a contactless manner.
  • electrical signals which are generated by sensors which are actuated by the pistons in a contactless manner.
  • it is a relatively expensive construction and an electrical auxiliary and working energy must be supplied.
  • control member of the control valve is formed directly by the piston rod correspondingly contoured on the outer circumference.
  • control element for the control valve in question, which would have to be actuated by mechanical coupling with wear.
  • the control element is formed directly by the piston rod, which, in cooperation with the sealing area, controls the fluid connection between two fluid spaces by appropriately contouring its outer circumference. In order to completely shut off the fluid connection, all that is required is an outer contour that is in fluid-tight contact with the sealing area. If the fluid connection is to be released, all that is required is an appropriately reduced cross section.
  • a stroke-dependent actuation of the control valve and, accordingly, a valve device that may be actuated by it can be achieved.
  • a pressure booster device which can also be referred to as a pressure booster
  • the valve device can be assembled inexpensively from one or more series valves that can be attached to the outside of the housing. It would also be possible for the valve device to be built in a space-saving manner, which in this case can expediently be designed as a multi-way pulse valve.
  • expensive sensors with associated actuating elements for example permanent magnets
  • additional control measures can be dispensed with.
  • the two fluid spaces adjoin axially on both sides to a sealing area coaxially surrounding the piston rod, the piston rod being connected via at least one length section serving to shut off the fluid connection (as a shut-off section has) which is contoured in such a way that when it takes a position covering the sealing area, that is to say generally axially at the same level as the sealing area, it bears with sealing contact on the sealing area and thereby causes a shut-off position.
  • the piston rod expediently has at least one length section (referred to as release section) which serves to release the fluid connection and which is contoured in such a way that when it takes up a position covering the sealing area, it is at least essentially at the same axial height as the sealing area causes an overflow gap connecting the two fluid spaces, which enables the fluidic pressure medium to flow through.
  • release section at least one length section which serves to release the fluid connection and which is contoured in such a way that when it takes up a position covering the sealing area, it is at least essentially at the same axial height as the sealing area causes an overflow gap connecting the two fluid spaces, which enables the fluidic pressure medium to flow through.
  • release section is formed by a circumferential groove-like depression of the piston rod. It should also be noted that any number of release sections can be provided axially spaced on the piston rod according to the desired control task.
  • the piston rod is preferably connected to at least one piston which divides two working spaces from one another in the housing, a first of the fluid spaces to be controlled with regard to their connection being connected to or being formed by the working space on the piston rod side.
  • the fluid-operated working device is designed as a pressure increasing device, it has Expediently via a valve device which can be actuated fluidically by the at least one control valve.
  • the stroke direction of the piston rod can be specified via the valve device. There is therefore the possibility, for example, of reversing the stroke direction as a function of certain axial positions of the piston rod.
  • the sealing area of the control valve is expediently located in a wall of the housing which is penetrated by the piston rod and is in particular defined by an annular seal which is expediently designed as a lip seal or a so-called grooved ring.
  • the intermediate wall lying between the piston chambers can contain a logical control, if required, which involves switching the valve which specifies the stroke direction - Direction causes if there is either no pressure at the same time or a certain actuation pressure (primary pressure) is present at the channels leading from the valve device to the outer working spaces of the piston chambers.
  • Figure 1 shows an exemplary design of the fluid-operated working device in a preferred embodiment as a pressure increasing device. in a longitudinal section along section line II from FIG. 2, and
  • FIG. 2 shows the arrangement from FIG. 1 in cross section according to section line II-II from FIG. 1.
  • the working device 1 contains a housing 2 in which two piston chambers 4, 4 ′ are arranged axially one after the other and separated from one another by an intermediate wall 3.
  • each piston chamber there is an axially displaceable piston 5, 5 ', which lies sealingly against the cylindrical inner surface of the piston chamber 4, 4' concerned.
  • the two pistons 5, 5 ' are rigidly connected to one another by an axially extending piston rod 6 passing through the intermediate wall 3 to form a unit axially displaceable.
  • the intermediate wall 3 contains an axially continuous passage opening 8 through which the piston rod 6 is guided.
  • Each piston 5, 5 ' divides the associated piston chamber 4, 4' into a piston rod associated with the intermediate wall 3 term inner working space 12, 12 'and an axially opposite, not penetrated by the piston rod 6 outer working space 13, 13'.
  • a first primary channel arrangement 14, which runs at least partially in the wall of the housing 2, connects, with the interposition of a valve device 15 that can be actuated by fluid force, the two outer working spaces 13, 13 ′ to a feed opening 16 provided on the outer surface of the housing 2, via which a Primary pressure P x standing fluid pressure medium, in particular compressed air, is supplied.
  • a pressure setting device 17, which is indicated schematically in FIG. 2 and which is expediently designed as a pressure regulator, is also advantageously interposed. It is located upstream of the valve device 15 towards the feed opening 16 and enables the primary pressure actually present at the valve device 15 to be specified. If necessary, the pressure setting device 17 can also be omitted.
  • the valve device 15 of the exemplary embodiment is designed as a 5/2-way valve, which is a so-called pulse valve which can be switched over by brief fluidic pressurization and which maintains the switch position in question even after the actuation pressure has been removed.
  • the first primary channel arrangement 14 is inserted by the valve device 15 into one or more channel sections 18 leading to the feed opening 16 and at least two into the two outer working spaces 13, 13 'dividing opening on the piston chamber side channel sections 19. Furthermore, the valve device 15 communicates with two ventilation channels 20.
  • fluid is supplied to the respective outer working space 13 or 13 'under the primary pressure, while at the same time the other outer working space 13' or 13 is vented. This causes the working unit 7 to be displaced in one or the other axial direction.
  • actuating means 24 for example actuating pistons or actuating diaphragms, cooperating with the valve member 23 are acted upon by fluid under an actuating pressure.
  • an actuating means 24 is assigned to each of the two axial end regions of the valve member 23, the fluid application of which is effected via actuating channels 22.
  • it contains a common channel section 27 starting from the feed opening 16, which splits into two branch sections 28, 28 'in the interior of the housing wall, which branch out into the working chambers 12, 12' on the piston rod side and into each of which a first check valve 26, 26 'is switched on.
  • the alignment of the first check valves 26, 26 ' is such that a fluid flow in the direction of the working chambers 12, 12' on the piston rod side is possible and is prevented in the opposite direction.
  • a secondary channel arrangement 32 is provided which communicates on the one hand with the working chambers 12, 12 'on the piston rod side and on the other hand leads to an outlet opening 33 provided in the area of the outer surface of the housing 2, to which a volume, referred to here as the high pressure chamber 34, is connected.
  • a secondary pressure P 2 is to be generated in the high-pressure chamber 34, which is higher than the secondary pressure applied on the inlet side? 1st
  • the secondary duct arrangement 32 is also subdivided into a common duct section 35 starting from the outlet opening 33 and two branch sections 36, 36 'branching off from it and opening into the piston rod-side working spaces 12, 12'.
  • a second check valve 37, 37' is switched on, with the opposite direction of action than the first check valves 26, 26 ', so that a fluid flow from the piston rod-side working spaces 12, 12' to the high-pressure space 34 is possible and in the opposite direction is prevented.
  • the check valves 26, 26 '; 37, 37 ' are expediently arranged in the intermediate wall 3, but could in principle also be provided externally.
  • the outer working space 13 'on the right outside is acted upon by fluid under the primary pressure P x , while at the same time the opposite outer working space 13 is vented.
  • the working unit 7 therefore moves to the left, the piston 5 'approaching the intermediate wall 3 and lying on the right in FIG.
  • valve device 15 is switched over so that the direction of movement of the working unit 7 is reversed, with the working chamber 12 on the piston rod side now the piston chamber 4 on the left in FIG. 1, under the pressure prevailing there, is displaced via the secondary channel arrangement 32 to the high-pressure chamber 34.
  • a secondary pressure P 2 which is at a higher pressure than the primary pressure P x , gradually builds up in the high-pressure chamber 34.
  • the pressure regulator 17 By returning the pressure in the high-pressure chamber 34 to the pressure regulator 17 as a control pressure (indicated by dash-dotted lines), an operating mode is possible in which the pressure regulator 17 interrupts the fluid supply to the valve device 15 when a desired preset secondary pressure P 2 has been reached.
  • the described operating mode of the working device 1 requires the valve device 15 to be actuated as a function of the axial position of the working unit 7 relative to the housing 2.
  • this is done using two control valves 38, 38 'upstream of the actuating means 24 of the valve device 15. which are actuated as a function of the position of the piston rod 6 and accordingly actuate or switch the valve device 15.
  • the latter happens in that the control valves control the supply of an actuating fluid to the actuating means 24 of the valve device 15.
  • piston rod 6 itself is a component of the two control valves in that it forms their control members and by cooperation with a housing-fixed assigned to a respective control valve 38, 38 ' Sealing area 43, 43 'controls the fluid supply "of the actuating fluid to the actuating means 24.
  • the sealing areas 43, 43 ' are located in the intermediate wall 3 of the housing 2 penetrated by the piston rod 6 and are each defined in the exemplary embodiment by at least one ring-shaped seal 44 which is fixed in an axially immovable manner in a circumferential groove of the passage opening 8.
  • the seals 44 are expediently lip seals which are also referred to as grooved rings.
  • the piston rod 6 is coaxially surrounded by the sealing areas 43, 43 '.
  • the sealing regions 43, 43 ' are expediently placed with only a small axial distance from the end face 45, 45' of the intermediate wall 3 delimiting the associated piston chamber 4, 4 '.
  • Each sealing area 43, 43 ' is located axially between a first fluid space 46 and a second fluid space 47.
  • the first fluid space 46 communicates with the respective adjacent piston rod-side working space 12, 12', in the exemplary embodiment via an axially relatively short annular gap between the Passage opening 8 and the outer surface of the piston rod 6. It would also be conceivable that the first fluid space 46 is formed directly by the adjacent working space on the piston rod side.
  • the second fluid spaces 47 are formed by annular interspaces, which axially follow the respective sealing region 43, 43 'between the outer circumference. catch the piston rod 6 and the inner circumference of the passage opening 8 are provided. In order to prevent the two second fluid spaces 47 from communicating with one another via the passage opening 8, they are sealed off from one another on the side axially opposite the assigned sealing area 43, 43 ′ in the interior of the intermediate wall 3. In the exemplary embodiment, this is done in that every second fluid space 47 is flanked on the axial side opposite the sealing area 43, 43 'by a further sealing area 48 which is in constant sealing contact with the outer surface of the piston rod 6 and expediently also in the form of an annular seal a lip seal or a groove ring is formed.
  • a leakage discharge channel 49 which on the one hand opens into the longitudinal section of the passage opening 8 between the two further sealing areas 48 and on the other hand leads to the outer surface of the housing 2, so that any leakage that may occur can be derived.
  • the fluid control function of the piston rod 6 is now realized in that the piston rod 6 has an outer periphery contoured to the desired control function over its length. Because this outer circumference varies over the length of the piston rod 6, a stroke-dependent interaction of the piston rod 6 with the sealing regions 43, 43 'can be brought about, in order to thereby control the fluid connection between the two fluid spaces 46, 47.
  • An actuation of the valve device 15 can be brought about, in which the actuating fluid and thus the fluidic actuation signal is received from the piston rod-side working spaces 12, 12 '.
  • the piston rod 6 of the exemplary embodiment has a greater length than the intermediate wall 3, which serves to shut off the fluid connection between the two fluid spaces 46, 47 of the two control valves 38, 38 'and is therefore referred to below as shut-off section 52. It is contoured in such a way that when it assumes a position covering one of the sealing areas 43, 43 'with sealing contact, it bears against this sealing area 43, 43' so that it assumes a shut-off position in this regard, the fluid connection between the two adjacent first and second fluid spaces 46 , 47 is separated. In the / shut-off position, the shut-off section 52 thus lies axially at the same height as the associated sealing area 43, 43 'and is sealingly enclosed by this or the associated seal 44.
  • the piston rod 6 has two axially spaced-apart length sections which adjoin the shut-off section 52 axially on both sides and which serve for the stroke-dependent release of the fluid connection between the two pairs of fluid spaces 46, 47 and are therefore referred to as release sections 53, 53 '.
  • the release sections 53, 53 ' are contoured such that when they assume a position covering the assigned sealing area 43, 43', they form at least one overflow gap 54 connecting the fluid spaces 46, 47 are at least partially radially spaced from the relevant sealing area 43, 43 '.
  • the position in question is referred to as the release position since the overflow gap 54 releases the connection between the two fluid spaces 46, 47, which enables the fluid to flow through while passing through the assigned sealing area 43, 43 '.
  • the relevant release section 53, 53 ' as shown as a circumferential groove-like depression introduced into the piston rod 6, so that the overflow gap 54 is an annular gap.
  • one or more local depressions distributed over the circumference of the piston rod could also be provided on the release section 53, 53 '. It is essential that the piston rod 6 on the release section 53, 53 'has a smaller cross-section along a sufficiently long length than the shut-off section 52 or the associated sealing area 43, 43'.
  • the piston rod 6 is now designed overall so that the shut-off section 52 is always effective until a piston 5, 5 'comes into the vicinity of the associated end face 45, 45' of the intermediate wall 3 or comes to bear against it.
  • the release sections 53, 53 'in the exemplary embodiment are arranged axially at only a small distance from each of the two pistons 5, 5'.
  • the control valves 38, 38 ' are thus closed by the shut-off section 52, which cooperates with both sealing areas 43, 43' at the same time.
  • the release section 53, 53' assigned to it assumes the release position, so that fluid under high pressure from the assigned piston rod-side working space 12, 12 'through the then exposed overflow gap 54 and the subsequent actuating channel 22 can reach the valve device 15 as actuating fluid.
  • Suitable venting means 55 are assigned to each actuating channel 22 so that the pressure built up in the actuating channels 22 can rapidly decrease again after the associated control valve 38, 38 ′ has been closed.
  • they are each formed by a nozzle or throttle connecting the relevant actuation channel 22 to the atmosphere, which nozzle does not adversely affect the pressure build-up required for switching, but can subsequently bring about pressure compensation with the atmosphere.
  • a logic control not shown in detail and preferably integrated in the intermediate wall, is expediently provided, which causes the valve device 15 to be switched over when a primary pressure is present or not at the same time in the two piston chamber-side channel sections of the first primary channel arrangement 14.
  • the valve device 15 is attached to the outside of the housing, in particular by means of an intermediate plate.
  • it can also be integrated at least partially or completely into the housing and in particular into the intermediate wall 3.
  • the associated circuit diagram is shown symbolically in FIG. 1 to clarify the valve function of the valve device 15.
  • piston rod can also be used as a control element for one or more control valves in working devices of a different design, in particular also in designs with the construction of conventional working cylinders which have only one piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Actuator (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Braking Systems And Boosters (AREA)

Abstract

L'invention concerne un dispositif de travail actionné par un fluide qui comporte une enveloppe (2) et une tige de piston (6) pouvant être déplacée par une force fluidique par rapport à laditenveloppe (2). Au moins une soupape de commande (38, 38') actionnée en fonction de la position de la tige de piston (6) contient un organe de commande qui commande, en coopérant avec une zone d'étanchéité (43, 43') solidaire du boîtier, la liaison fluidique entre les deux chambres à fluide (46, 47). Cet organe de commande est formé directement par la tige de piston (6), dont le contour correspond à la périphérie extérieure.
EP99953807A 1998-10-21 1999-10-13 Dispositif de travail actionne par un fluide Expired - Lifetime EP1042615B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE29818762U 1998-10-21
DE29818762U DE29818762U1 (de) 1998-10-21 1998-10-21 Fluidbetätigte Arbeitsvorrichtung
PCT/EP1999/007694 WO2000023716A1 (fr) 1998-10-21 1999-10-13 Dispositif de travail actionne par un fluide

Publications (2)

Publication Number Publication Date
EP1042615A1 true EP1042615A1 (fr) 2000-10-11
EP1042615B1 EP1042615B1 (fr) 2004-08-04

Family

ID=8064190

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99953807A Expired - Lifetime EP1042615B1 (fr) 1998-10-21 1999-10-13 Dispositif de travail actionne par un fluide

Country Status (5)

Country Link
EP (1) EP1042615B1 (fr)
JP (1) JP2002527296A (fr)
KR (1) KR20010033338A (fr)
DE (2) DE29818762U1 (fr)
WO (1) WO2000023716A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1818547A2 (fr) 2006-02-10 2007-08-15 FESTO AG & Co Dispositif d'entretien d'air comprimé
EP3546762A4 (fr) * 2016-11-22 2020-07-29 SMC Corporation Multiplicateur de pression

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9670921B2 (en) * 2015-09-17 2017-06-06 Monkey Pumps, LLC Reciprocating drive mechanism with a spool vent
WO2017087146A1 (fr) * 2015-11-19 2017-05-26 Monkey Pumps, LLC Mécanisme d'entraînement alternatif présentant un évent de bobine
CN114060329A (zh) * 2020-08-04 2022-02-18 费斯托（中国）自动化制造有限公司 气动增压器
IT202100014633A1 (it) * 2021-06-04 2022-12-04 Camozzi Automation S P A Moltiplicatore di pressione

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Publication number Priority date Publication date Assignee Title
US2864313A (en) * 1957-04-24 1958-12-16 Dawson Edward Hydraulic intensifier
CH512674A (fr) * 1964-04-14 1971-09-15 Francis Daumas Jacques Groupe motopompe à liquide, à commande pneumatique
DE1528583A1 (de) * 1965-05-20 1970-01-29 Stahl U Appbau Hans Leffer Gmb Hydraulisch oder pneumatisch kontinuierlich betaetigter Kolbenantrieb mit hin- und hergehender Bewegung,insbesondere doppeltwirkender Druckuebersetzer
DE4438621A1 (de) * 1994-10-28 1996-05-02 Wagner Hermann Wasserhydraulikschweißsystem sowie ein Ventil und ein Druckübersetzer für ein solches
DE29516960U1 (de) * 1995-10-26 1996-01-04 Bar Pneumatische Steuerungssys Druckerhöher
DE19633258C1 (de) * 1996-08-17 1997-08-28 Iversen Hydraulics Aps Druckverstärker für Fluide, insbesondere für Hydraulikflüssigkeiten

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0023716A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1818547A2 (fr) 2006-02-10 2007-08-15 FESTO AG & Co Dispositif d'entretien d'air comprimé
EP3546762A4 (fr) * 2016-11-22 2020-07-29 SMC Corporation Multiplicateur de pression

Also Published As

Publication number Publication date
DE29818762U1 (de) 1998-12-24
DE59910134D1 (de) 2004-09-09
EP1042615B1 (fr) 2004-08-04
KR20010033338A (ko) 2001-04-25
WO2000023716A1 (fr) 2000-04-27
JP2002527296A (ja) 2002-08-27

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