EP0577955B1 - Hydropneumatischer Druckübersetzer - Google Patents

Hydropneumatischer Druckübersetzer Download PDF

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Publication number
EP0577955B1
EP0577955B1 EP93107954A EP93107954A EP0577955B1 EP 0577955 B1 EP0577955 B1 EP 0577955B1 EP 93107954 A EP93107954 A EP 93107954A EP 93107954 A EP93107954 A EP 93107954A EP 0577955 B1 EP0577955 B1 EP 0577955B1
Authority
EP
European Patent Office
Prior art keywords
working
piston
room
storage
plunger
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.)
Expired - Lifetime
Application number
EP93107954A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0577955A1 (de
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
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 Tox Pressotechnik GmbH and Co KG filed Critical Tox Pressotechnik GmbH and Co KG
Publication of EP0577955A1 publication Critical patent/EP0577955A1/de
Application granted granted Critical
Publication of EP0577955B1 publication Critical patent/EP0577955B1/de
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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • 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 hydraulic pressure intensifier according to the preamble of the main claim.
  • a hydraulic pressure intensifier of the generic type DE-A-2 810 894 and DE PS 28 18 332
  • the plunger is held in its initial position via a return spring, this spring simultaneously acting on a storage piston, whereby the low pressure is generated in the storage space .
  • the hydraulic fluid flows from the storage space into the enlarging working space under this low pressure.
  • the plunger is then driven and, above all, plunges into the bore in a radially sealing manner, the high pressure is generated in the working space when the plunger is moved further into the hydraulic fluid there, which further drives the working piston.
  • the hydraulic pressure booster according to the invention with the characterizing features of the main claim has the advantage over the fact that extreme precision is achieved in the repetition of the individual operations and with relatively little effort. If the plunger dips into the bore and the high-pressure seal there too early and hydraulic fluid can no longer flow from the storage space into the working space via this channel, then hydraulic fluid flows from the storage space into the working space via the second connecting channel and thus prevents a negative pressure in the Working space is created, which can lead to the release of air bound in the hydraulic fluid, up to the foaming of the oil. Then when the plunger succeeding piston, the working space is completely filled with the hydraulic fluid that has flowed through the connecting channel in the meantime, so that the power stroke starts precisely at the same time as the plunger is moved.
  • the return stroke of the working piston then takes place as described in detail.
  • additional power strokes can be carried out as required and different control sequences can also take place.
  • a second rapid stroke instead of a second rapid stroke, only a stopping in the working position after the first power stroke can take place, in which time the plunger returns, after which the second power stroke starts immediately with respect to the stroke after the first power stroke of the working piston.
  • the plunger moves back a little in an interim period, during which hydraulic fluid can flow from the storage space into the working space.
  • the stroke of the plunger required in several stages can be divided into several sections with a corresponding return stroke, so that the cross-sectional ratio of plunger to working piston can be chosen to be extremely different, with the advantage of an extraordinarily high pressure ratio.
  • a check valve that opens in the direction of the working space and closes in the direction of the storage space is arranged in the connecting channel.
  • This check valve can be equipped with or without a closing spring, it can be designed as a slide valve, ball valve or other check valve, such as a flap valve. Decisive for the opening of the check valve is the difference between the pressures in the work space and the storage space and of course the area acted on the movable valve part, as well as the force of the closing spring.
  • the check valve can be designed so that even very low pressures are sufficient to open it.
  • the connecting channel and check valve are arranged in the housing of the hydraulic pressure booster.
  • the two spaces are connected to one another via a line running outside the housing and in which the check valve is arranged.
  • the application of the invention is particularly advantageous in the case of a hydraulic pressure intensifier in the form of a hydropneutical pressure intensifier which has the features of claim 6.
  • a hydropneumatic pressure intensifier is known per se (DE PS 28 18 337) and, above all, has the problem that, due to the additional independent pneumatic actuation of the working piston, it leads the plunger or lags on the return stroke.
  • the invention can of course also be applied to such hydropneumatic pressure intensifiers in which the storage space on the one hand and the working space on the other hand are accommodated in two cylinders which are independent and in particular arranged in parallel, as are known per se and have also been supplied for a long time.
  • the decisive factor is that whatever the course, this additional connection channel is present between the storage space and the work space.
  • a working piston 2 is axially displaceably arranged in a working space 1 filled with hydraulic oil and is guided in a bore in a housing 3.
  • a piston rod 4 projecting outside the housing is arranged on the working piston 2 for power transmission.
  • a disc piston 5 is attached to the working piston 2 and piston rod 4. This disc piston 5 is radially sealed to a casing tube 6 and thereby separates two spaces 7 and 8, which are alternately supplied with compressed air for the rapid traverse of the working piston 2.
  • the working piston 2 is pushed downwards.
  • the working piston 2 is moved up again into the starting position shown.
  • a storage space 9 hydraulically connected to the working space 1 above the working space 1, in which a lower one by a storage piston 11 with a storage spring 12 Hydraulic accumulator pressure is generated, which is sufficient to keep the working space 1 filled with hydraulic oil from the storage space 9 during the rapid stroke of the working piston 2.
  • the storage piston 11 is guided in a radially sealing and axially displaceable tube 13.
  • a drive piston 14 of a plunger 15 which is displaceable in the direction of the working space 1 against the force of the storage spring 12.
  • the plunger 15 penetrates, radially sealed, the storage piston 11 and dips into the storage space 9.
  • the drive piston 14 with plunger 15 is driven by compressed air, which is conducted into a control chamber 16 above the drive piston 14. This control of compressed air occurs when the working piston 2 has ended its rapid traverse and before the actual pressure stroke of the working piston 2 is to begin. If the drive piston 14 is displaced by the compressed air, after a forward stroke the plunger 15 plunges into a connecting bore 17 leading from the storage space 9 to the work space 1, after which this connection is interrupted by the cooperation of a radial seal 18, so that the plunger 15 is submerged further Hydraulic fluid is displaced into the working space 1 there, with a corresponding action on the working piston 2.
  • the pneumatic pressure in the control chamber 16 is reduced, so that the storage spring 12 pushes the drive piston 14 back into the starting position shown.
  • pressure reduction in the pneumatic chamber 7 or pressure build-up in the pneumatic chamber 8 pushes the working piston 2 back into the starting position shown, through the disk piston 5, hydraulic fluid being displaced back into the storage chamber 9 by the working piston 2 and the storage piston 11 countering the force there the storage spring 12 is moved back to the starting position shown.
  • a connecting channel 19 is provided, in which a check valve blocking the storage space 9 is arranged, with a movable valve member 21 and a spring 22 then hydraulic fluid still flows from the storage space 9 into the working space 1 when the connecting bore 17 is blocked by the plunger 15 or the radial seal 18.
  • connection channel between the storage space 9 and the working space 1 is a line 23 running outside the housing 3, in which a correspondingly arranged check valve with a movable valve member 24 and a spring 25 is arranged, this check valve 24, 25 also locks towards storage space 9.

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-Damping Devices (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Housings And Mounting Of Transformers (AREA)
  • Actuator (AREA)
  • Colloid Chemistry (AREA)
  • Glass Compositions (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)
  • Safety Valves (AREA)
EP93107954A 1992-07-02 1993-05-15 Hydropneumatischer Druckübersetzer Expired - Lifetime EP0577955B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4221638 1992-07-02
DE4221638A DE4221638B4 (de) 1992-07-02 1992-07-02 Verfahren für einen hydraulischen Druckübersetzer

Publications (2)

Publication Number Publication Date
EP0577955A1 EP0577955A1 (de) 1994-01-12
EP0577955B1 true EP0577955B1 (de) 1997-04-09

Family

ID=6462267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93107954A Expired - Lifetime EP0577955B1 (de) 1992-07-02 1993-05-15 Hydropneumatischer Druckübersetzer

Country Status (9)

Country Link
US (1) US5381661A (es)
EP (1) EP0577955B1 (es)
JP (1) JPH06213202A (es)
KR (1) KR100292553B1 (es)
AT (1) ATE151504T1 (es)
CA (1) CA2099469C (es)
DE (2) DE4221638B4 (es)
DK (1) DK0577955T3 (es)
ES (1) ES2101160T3 (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10026616A1 (de) * 2000-05-29 2001-12-13 Schunk Gmbh & Co Kg Druckübersetzer, insbesondere hydropneumatischer Druckübersetzer

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2102762A1 (en) * 1993-11-09 1995-05-10 Viljo K. Valavaara Two-stage pressure cylinder
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
DE59702132D1 (de) * 1996-03-19 2000-09-14 Tox Pressotechnik Gmbh Hydropneumatische werkzeugmaschine
US6113608A (en) * 1998-11-20 2000-09-05 Scimed Life Systems, Inc. Stent delivery device
DE19907883A1 (de) * 1999-02-24 2000-08-31 Tox Pressotechnik Gmbh Hydropneumatischer Druckübersetzer
KR100380121B1 (ko) * 2000-03-15 2003-04-14 주재석 유압식 증압실린더
DE102004062695B4 (de) * 2004-12-21 2006-11-02 Karl-Heinz Jung Hydraulikpumpe
DE102004062696B4 (de) * 2004-12-21 2006-10-05 Karl-Heinz Jung Hydraulikpumpe
MX2009000844A (es) * 2006-07-31 2009-02-04 Norgren Gmbh Accionador neumatico.
US7775040B2 (en) * 2006-11-08 2010-08-17 Caterpillar Inc Bidirectional hydraulic transformer
US8301307B2 (en) 2007-04-13 2012-10-30 Norgren Gmbh Pneumatic actuator system and method
JP6084972B2 (ja) 2011-08-12 2017-02-22 イートン コーポレーションＥａｔｏｎ Ｃｏｒｐｏｒａｔｉｏｎ エネルギを回収し、油圧システムにかかる負荷を平準化するためのシステム及び方法
CN103717808A (zh) 2011-08-12 2014-04-09 伊顿公司 用于回收惯性能量的方法和装置
KR101331764B1 (ko) * 2011-10-21 2013-11-20 주다영 유압식 증압실린더
DE102012008902A1 (de) 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatische Vorrichtung zur Druckübersetzung und Nietvorrichtung
US8978493B2 (en) * 2012-07-27 2015-03-17 Westinghouse Electric Company Llc Conduit length adjustment apparatus and method
KR102126360B1 (ko) 2012-12-19 2020-06-24 이턴 코포레이션 유압 시스템용 제어 시스템 및 에너지를 회수하고 유압 시스템 부하를 평준화하는 방법
LU92618B1 (en) * 2014-12-16 2016-06-17 Luxembourg Patent Co Valve actuating device with opening reduced speed
US10456824B2 (en) 2016-06-10 2019-10-29 Btm Company Llc Safety power assist for manual press
KR102148632B1 (ko) * 2020-05-08 2020-08-26 박승일 체적가변 피스톤을 이용한 유압 배력(油壓 培力) 장치
CN113351768B (zh) * 2021-05-28 2022-08-30 苏州托克斯冲压设备有限公司 汽车转向内拉杆封口压铆装置

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
US2827766A (en) * 1954-12-09 1958-03-25 Lionel E Weiss Hydro-pneumatic press apparatus
US2915878A (en) * 1956-07-06 1959-12-08 Hramoff Olga Self-contained booster cylinder
US3200596A (en) * 1962-04-30 1965-08-17 Power Control Products Inc Cylinder and piston arrangement
FR1573184A (es) * 1968-04-12 1969-07-04
US3631676A (en) * 1970-09-18 1972-01-04 Borg Warner Dual-ratio master cylinder
CH616992A5 (en) * 1977-03-24 1980-04-30 Schenker Emil Storen Und Masch Pneumatic-hydraulic piston/cylinder unit, in particular for the actuation of tools
DE2818337C2 (de) * 1978-04-26 1980-07-17 Haug, Paul, 7307 Aichwald Druckübersetzter hydropneumatischer
DE2848591A1 (de) * 1978-11-09 1980-05-22 Haug Paul Zylinderanordnung mit pneumohydraulischer druckuebersetzung und eilgang
DE3125081A1 (de) * 1981-06-26 1983-01-13 Kolben-Seeger GmbH & Co KG, 6236 Eschborn Hydropneumatischer druckzylinder
HU185642B (en) * 1981-08-04 1985-03-28 Bela Zimber Penumatically controlled pressure converter for operating hydraulic work devices
DE3828699A1 (de) * 1988-08-24 1990-03-01 Eugen Rapp Verfahren zur oelauffuellung eines hydro-pneumatischen druckuebersetzers und einrichtung zur durchfuehrung des verfahrens
JP3062889B2 (ja) * 1990-05-11 2000-07-12 株式会社コスメック ブースタ駆動式油圧シリンダ装置
DE4122204A1 (de) * 1991-07-04 1993-01-07 Weiss Maschf Johann Pneumatisch-hydrostatischer druckuebersetzer

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10026616A1 (de) * 2000-05-29 2001-12-13 Schunk Gmbh & Co Kg Druckübersetzer, insbesondere hydropneumatischer Druckübersetzer
DE10026616B4 (de) * 2000-05-29 2006-01-26 Schunk Gmbh & Co. Kg Fabrik Für Spann- Und Greifwerkzeuge Druckübersetzer, insbesondere hydropneumatischer Druckübersetzer

Also Published As

Publication number Publication date
CA2099469A1 (en) 1994-01-03
DE4221638B4 (de) 2005-11-03
CA2099469C (en) 1999-09-21
DE59306086D1 (de) 1997-05-15
KR940002509A (ko) 1994-02-17
ATE151504T1 (de) 1997-04-15
US5381661A (en) 1995-01-17
KR100292553B1 (ko) 2001-06-01
JPH06213202A (ja) 1994-08-02
EP0577955A1 (de) 1994-01-12
DE4221638A1 (de) 1994-03-03
ES2101160T3 (es) 1997-07-01
DK0577955T3 (da) 1997-10-20

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