EP0579037A1 - Multiplicateur de pression hydropneumatique - Google Patents

Multiplicateur de pression hydropneumatique Download PDF

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Publication number
EP0579037A1
EP0579037A1 EP93110428A EP93110428A EP0579037A1 EP 0579037 A1 EP0579037 A1 EP 0579037A1 EP 93110428 A EP93110428 A EP 93110428A EP 93110428 A EP93110428 A EP 93110428A EP 0579037 A1 EP0579037 A1 EP 0579037A1
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EP
European Patent Office
Prior art keywords
piston
pressure
working
plunger
space
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
EP93110428A
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German (de)
English (en)
Other versions
EP0579037B1 (fr
EP0579037B2 (fr
Inventor
Viktor Dipl.-Ing. Malina
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.)
Tox Pressotechnik GmbH and Co KG
Original Assignee
Tox Pressotechnik GmbH and Co KG
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Filing date
Publication date
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Application filed by Tox Pressotechnik GmbH and Co KG filed Critical Tox Pressotechnik GmbH and Co KG
Publication of EP0579037A1 publication Critical patent/EP0579037A1/fr
Publication of EP0579037B1 publication Critical patent/EP0579037B1/fr
Application granted granted Critical
Publication of EP0579037B2 publication Critical patent/EP0579037B2/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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters

Definitions

  • the invention is based on a hydropneumatic pressure intensifier according to the preamble of the main claim.
  • a main problem with such hydropneumatic pressure boosters is the sealing between the storage space and the control space, since the hydraulic pressures in the storage space and the pneumatic pressures in the control space change continuously during a work cycle, and do not necessarily change synchronously, with the risk that oil will leak out the storage space enters the control room and this causes leakage losses, which can affect the working capacity of the hydropneumatic pressure intensifier, or there is a risk that air from the control room gets into the storage space, where it is absorbed by the oil with the disadvantage that it enters the Workspace arrives and there tends to be more compressible during the high pressure phase of the pressure stroke with all the resulting disadvantages for the ability of the unit to work.
  • the hydropneumatic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage over the fact that there is a low pressure in the ventilation ring grooves, for example atmospheric pressure, so that any air volume passing to the control chamber can be derived. Should oil quantities get into the ventilation ring grooves from the storage space, this is not disadvantageous, at least for the respective work process, but it is only necessary to add oil to the storage space if there is a considerable loss of oil.
  • a bore in the working cylinder is used for ventilation, which is always in overlap with the circumferential surface groove regardless of the working stroke of the storage piston. Both in the starting position and in the end position - possibly with only a small amount remaining in the storage space - is completely relieved, whereby the vent hole can lead directly to the atmosphere.
  • the relief ring groove in the bore wall is connected to that on the lateral surface by at least one radial bore of the storage piston.
  • a radial bore can be carried out in a simple manner as a transverse bore, the beginning and end of this radial bore each ending in the annular groove surface and thus having no frictional contact with the working cylinder or the plunger.
  • a working piston 2 is arranged axially displaceably and radially sealingly in a housing 1 and delimits a working space 3 filled with hydraulic oil with it.
  • a piston rod 4 projecting outside the housing is arranged on the working piston 2.
  • the working piston 2 as a collar has an auxiliary piston 5, which is radially sealed off from a casing tube 6 and thereby separates two pneumatic spaces 7 and 8, which are alternately supplied with pneumatic pressure for the rapid traverse of the working piston 2.
  • the working piston 2 As soon as there is sufficient working pressure in the pneumatic space 7, the working piston 2 is pushed down and vice versa, with a correspondingly high pressure in the pneumatic space 8 and a reduced pressure in the pneumatic space 7, the working piston 2 is moved back into the starting position shown.
  • a storage space 9 for hydraulic oil for hydraulic oil, the storage pressure of which is generated by a storage piston and the pneumatic pressure in a control space 12.
  • the accumulator piston 11 is guided in a jacket tube 13, which delimits the accumulator chamber 9 and the control chamber 12, in a radially sealing and axially displaceable manner, in the manner of a free piston.
  • the casing tube 13 is closed on the one hand by a housing part 14 of the housing 1 and on the other hand by a partition wall 15, with corresponding twists on the housing part 14 and partition wall 15 for pushing on the casing tube 13, with additional static seals 16.
  • the partition 15 serves to delimit a pneumatic space 17 which is surrounded by a casing tube 18 and in which the drive piston 19 of a plunger 21 is mounted, which can be displaced in the working space 3 against the hydraulic pressure.
  • the plunger 21 penetrates the partition 15 and the storage piston 11 in a radially sealed manner and dips with its free end into the storage space 9.
  • the drive piston 19 with the plunger 21 is driven by compressed air which is conducted into a drive space 22 above the drive piston 21, as a result of which the high-pressure operation is initiated.
  • the plunger 21, after covering a certain stroke dips into a connecting bore 23 leading from the storage space 9 to the working space 3, this connection being interrupted with the participation of a radial seal 24.
  • hydraulic fluid With a further stroke of the plunger 21 and a correspondingly deeper immersion in the working space 3, hydraulic fluid is displaced there, so that a high working pressure is generated in the working space 3 due to the relatively small plunger diameter.
  • This pressure corresponds to the transmission ratio of the working surfaces of the drive piston 19 to the plunger 21, starting from the pneumatic pressure acting on the drive piston 19.
  • the resulting high hydraulic pressure acts directly on the working piston 2 and causes the desired high force on the piston rod 4.
  • the pneumatic pressure in the drive chamber 22 is reduced and a corresponding pneumatic pressure is built up in the pneumatic chamber 17, so that the drive piston 19 with the plunger 21 is pushed back into the starting position shown, after which from the working chamber 3, through the working piston 2 displaced, hydraulic fluid flows into the storage space 9 and the working piston 2, driven by the auxiliary piston 5 and compressed air in the pneumatic space 8, is displaced into the starting position also shown.
  • the various pneumatic spaces are leading to the outside of the hydropneumatic pressure intensifier Connection channels equipped, namely the pneumatic room 7 through the channel 25, the pneumatic room 8 through the channel 26, the control room 12 through the channel 27, the pneumatic room 17 through the channel 28 and the drive chamber 22 through the channel 29.
  • control Connection channels 26 and 28 for the pneumatic spaces 8 and 17 are connected to one another via a pneumatic control line 31, so that when the pneumatic control pressure is supplied via them, the auxiliary piston 5 and the drive piston 19 are pushed into the starting position shown.
  • the pressure in the pneumatic control line 31 is reduced and passed into a pneumatic control line 32 which connects the connecting channels 25, 27 and 29 to one another, the connecting channel 29 being connected upstream of a pressure-controlled valve 33.
  • the supplied pneumatic pressure is thus first supplied to the connecting channels 25 and 27 and thus to the pneumatic chamber 7 and the control chamber 12, after which the auxiliary piston 5 with the working piston 2 is pushed down in rapid traverse and the accumulator piston 11 corresponding to the one overflowing from the storage chamber 9 into the working chamber 3 Hydraulic amount is replenished.
  • the hydraulic volume in the work space 3 and the storage space 9 is constant overall, apart from leak quantities that have to be refilled every now and then.
  • the accumulator piston 11 is arranged between the oil-filled storage chamber 9 and the control chamber 12 filled with air of different pressure according to the above-mentioned control, the main aim being to prevent oil air from the storage space 9 into the control space 12 and vice versa into the storage space 9.
  • an absolute air-oil separation on the storage piston 11 is used for this purpose, in which it has annular grooves 34 and 35 with radial seals 36 and 37 on the one hand both towards the casing tube 13 and towards the plunger 21.
  • the radial seals 37 to the plunger 21 are shown once as a round cord seal and once as a sleeve seal.
  • annular groove 38 is arranged on the outer surface of the accumulator piston 11 and is vented to the outside of the unit via a ventilation hole 39 arranged in the outer casing 13.
  • the vent hole 39 is arranged in relation to the annular groove 38, or the maximum possible stroke of the accumulator piston 11, so that it always remains in register with the annular groove 38.
  • annular groove 42 is provided in the central bore 41 of the storage piston 11, which is penetrated by the plunger 21, and is connected by a continuous radial bore 43 to the always vented annular groove 38 on the outer surface of the storage piston 11.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Damping Devices (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
EP93110428A 1992-07-02 1993-06-30 Multiplicateur de pression hydropneumatique Expired - Lifetime EP0579037B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4223411A DE4223411A1 (de) 1992-07-02 1992-07-02 Hydropneumatischer Druckübersetzer
DE4223411 1992-07-02

Publications (3)

Publication Number Publication Date
EP0579037A1 true EP0579037A1 (fr) 1994-01-19
EP0579037B1 EP0579037B1 (fr) 1997-09-24
EP0579037B2 EP0579037B2 (fr) 2003-01-22

Family

ID=6463352

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93110428A Expired - Lifetime EP0579037B2 (fr) 1992-07-02 1993-06-30 Multiplicateur de pression hydropneumatique

Country Status (5)

Country Link
US (1) US5377488A (fr)
EP (1) EP0579037B2 (fr)
JP (1) JPH06159303A (fr)
AT (1) ATE158642T1 (fr)
DE (2) DE4223411A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995013478A1 (fr) * 1993-11-09 1995-05-18 Valavaara Viljo K Cylindre de compression a deux etages
DE19720252A1 (de) * 1997-05-15 1998-11-19 Kraemer & Grebe Kg Hydropneumatischer Druckübersetzer als Stanzenantrieb in Verpackungsmaschinen
WO2000039466A1 (fr) * 1998-12-23 2000-07-06 Tox Pressotechnik Gmbh & Co. Kg Joint pour demultiplicateur de pression hydropneumatique

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4445011A1 (de) * 1994-12-16 1996-06-20 Tox Pressotechnik Gmbh Hydraulischer Druckübersetzer
US5526644A (en) * 1995-06-07 1996-06-18 Brieschke; Todd M. Oil intensifier cylinder
DE19780220D2 (de) * 1996-03-19 1998-03-19 Tox Pressotechnik Gmbh Hydropneumatische Werkzeugmaschine
US5865029A (en) * 1997-07-11 1999-02-02 Aries Engineering Company, Inc. Air/oil intensifier having multiple sensors
KR100380121B1 (ko) * 2000-03-15 2003-04-14 주재석 유압식 증압실린더
US20040028543A1 (en) 2000-03-27 2004-02-12 Eugen Rapp Hydraulic pressure intensifier
DE10255230A1 (de) * 2002-11-26 2004-06-09 Uhde High Pressure Technologies Gmbh Hochdruckvorrichtung und -verfahren zum hydraulisch-pneumatischen Krafthub für Reinraumanwendungen
DE102004010438B3 (de) * 2004-03-01 2005-06-30 Farger & Joosten Maschinenbau Gmbh Hydropneumatischer Druckübersetzer mit Axial- und Radialdichtungen
JP5154553B2 (ja) * 2006-07-31 2013-02-27 ノルグレン・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 空気圧式アクチュエータ
WO2008125132A1 (fr) * 2007-04-13 2008-10-23 Norgren Gmbh Système d'actionneur pneumatique et procédé
DE102007036844B4 (de) * 2007-08-06 2021-05-06 Tox Pressotechnik Gmbh & Co. Kg Verfahren zum Betrieb einer hydropneumatischen Vorrichtung zur Druckübersetzung
KR100917070B1 (ko) * 2007-09-03 2009-09-15 윤택수 부스터가 구비된 증압장치
DE102007044907A1 (de) * 2007-09-19 2009-04-02 Tox Pressotechnik Gmbh & Co. Kg Verfahren zum Betrieb einer hydropneumatischen Vorrichtung sowie Hydraulikflüssigkeitspumpe für die Wartung einer hydropneumatischen Vorrichtung
DE102012008902A1 (de) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatische Vorrichtung zur Druckübersetzung und Nietvorrichtung
US9394928B2 (en) 2012-07-31 2016-07-19 Caterpillar Inc. Dynamic seal wear mitigation system
US9651067B2 (en) * 2012-07-31 2017-05-16 Caterpillar Inc. Hydraulic system with a dynamic seal
CN102913509A (zh) * 2012-11-23 2013-02-06 湖北汽车工业学院 电液增压缸及安装有电液增压缸的压机设备
CN104279194A (zh) * 2013-07-09 2015-01-14 北京精密机电控制设备研究所 一种燃气挤压式油箱
CN107288942B (zh) * 2016-03-31 2019-01-08 中核新能核工业工程有限责任公司 以压缩空气为动力的小流量uf6气体增压装置
JP6999439B2 (ja) * 2017-03-15 2022-01-18 セイコーインスツル株式会社 シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法
US10941790B2 (en) * 2017-03-15 2021-03-09 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
US10982690B2 (en) * 2017-03-15 2021-04-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2765625A (en) * 1952-06-12 1956-10-09 Charles H Hart Air-hydraulic booster
DE2230492A1 (de) * 1972-06-22 1974-01-10 Stommel & Voos Stahlstempelfab Pneumatisch-hydraulischer druckumsetzer
DE1777423A1 (de) * 1967-06-08 1974-11-21 Josef Nemetz Hydropneumatischer spannzylinder
DE2810894A1 (de) * 1977-03-24 1978-10-05 Schenker Storen Maschf Pneumatisch hydraulischer zylinder

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1504765A (fr) * 1966-10-26 1967-12-08 Faiveley Sa Vérin oléopneumatique à structure étagée
DE2304752A1 (de) * 1973-02-01 1974-08-15 Schaal Kg Werkzeug U Vorrichtu Vorrichtung zur pneumatisch - hydraulischen uebertragung von kraeften
DE2818337C2 (de) * 1978-04-26 1980-07-17 Haug, Paul, 7307 Aichwald Druckübersetzter hydropneumatischer
DE3125081A1 (de) * 1981-06-26 1983-01-13 Kolben-Seeger GmbH & Co KG, 6236 Eschborn Hydropneumatischer druckzylinder
DE3828699A1 (de) * 1988-08-24 1990-03-01 Eugen Rapp Verfahren zur oelauffuellung eines hydro-pneumatischen druckuebersetzers und einrichtung zur durchfuehrung des verfahrens
MX167118B (es) † 1989-09-18 1993-03-04 Savair Inc Cilindro intensificador oleoneumatico y metodo para aplicar una fuerza intensificada a una pieza de trabajo
US5107681A (en) † 1990-08-10 1992-04-28 Savair Inc. Oleopneumatic intensifier cylinder
US5265423A (en) * 1992-12-04 1993-11-30 Power Products Ltd. Air-oil pressure intensifier with isolation system for prohibiting leakage between and intermixing of the air and oil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2765625A (en) * 1952-06-12 1956-10-09 Charles H Hart Air-hydraulic booster
DE1777423A1 (de) * 1967-06-08 1974-11-21 Josef Nemetz Hydropneumatischer spannzylinder
DE2230492A1 (de) * 1972-06-22 1974-01-10 Stommel & Voos Stahlstempelfab Pneumatisch-hydraulischer druckumsetzer
DE2810894A1 (de) * 1977-03-24 1978-10-05 Schenker Storen Maschf Pneumatisch hydraulischer zylinder

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995013478A1 (fr) * 1993-11-09 1995-05-18 Valavaara Viljo K Cylindre de compression a deux etages
DE19720252A1 (de) * 1997-05-15 1998-11-19 Kraemer & Grebe Kg Hydropneumatischer Druckübersetzer als Stanzenantrieb in Verpackungsmaschinen
WO2000039466A1 (fr) * 1998-12-23 2000-07-06 Tox Pressotechnik Gmbh & Co. Kg Joint pour demultiplicateur de pression hydropneumatique
US6502395B1 (en) 1998-12-23 2003-01-07 Tox Pressotechnik Gmbh & Co., Kg Seal for hydropneumatic pressure intensifier

Also Published As

Publication number Publication date
ATE158642T1 (de) 1997-10-15
EP0579037B1 (fr) 1997-09-24
EP0579037B2 (fr) 2003-01-22
JPH06159303A (ja) 1994-06-07
DE59307411D1 (de) 1997-10-30
DE4223411A1 (de) 1994-01-05
US5377488A (en) 1995-01-03

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