EP0085080B1 - Steuerschaltung für einen pneumatisch-hydraulischen druckwandler - Google Patents

Steuerschaltung für einen pneumatisch-hydraulischen druckwandler Download PDF

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Publication number
EP0085080B1
EP0085080B1 EP82902371A EP82902371A EP0085080B1 EP 0085080 B1 EP0085080 B1 EP 0085080B1 EP 82902371 A EP82902371 A EP 82902371A EP 82902371 A EP82902371 A EP 82902371A EP 0085080 B1 EP0085080 B1 EP 0085080B1
Authority
EP
European Patent Office
Prior art keywords
valve
hydraulic
control valve
pressure
cylinder
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
Application number
EP82902371A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0085080A4 (de
EP0085080A1 (de
Inventor
Béla ZIMBER
Imre Molnar
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.)
KOEZPONTI VALTO-ES HITELBANK RT INNOVACIOS ALAP
Original Assignee
KOZPONTI VALTO-ES HITELBANK RT INNOVACIOS ALAP
Kozponti Valto-Es Hitelbank Rt Innovacios Alap
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 KOZPONTI VALTO-ES HITELBANK RT INNOVACIOS ALAP, Kozponti Valto-Es Hitelbank Rt Innovacios Alap filed Critical KOZPONTI VALTO-ES HITELBANK RT INNOVACIOS ALAP
Priority to AT82902371T priority Critical patent/ATE19292T1/de
Publication of EP0085080A1 publication Critical patent/EP0085080A1/de
Publication of EP0085080A4 publication Critical patent/EP0085080A4/de
Application granted granted Critical
Publication of EP0085080B1 publication Critical patent/EP0085080B1/de
Expired 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
    • 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
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check valve
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve

Definitions

  • the invention relates to a control circuit for a pneumatic-hydraulic pressure intensifier for actuating hydraulic working devices, which has a double-acting pneumatic drive piston and a displacement piston which can be immersed in a hydraulic pressure chamber to which the hydraulic working device is connected.
  • the object of the invention is to provide a control circuit for a pneumatic-hydraulic pressure intensifier with a double-acting pneumatic drive piston and a displacement piston which can be immersed in a hydraulic pressure chamber, and to design it in such a way that different hydraulic working devices can be actuated via the pressure intensifier in a specific mode of operation to be performed that can be easily adapted to the respective work device.
  • control circuits such as quick exhaust valves, timers, throttle check valves and the like. Like., are generally known. It is also known per se (DE-B-15 50 716) for a pneumatic-hydraulic pressure intensifier whose pneumatic drive piston is only single-acting to use a pneumatically actuated hydraulic container as the hydraulic pressure source.
  • the pressure intensifier with a control circuit can be used to actuate hydraulic working devices for riveting, pressing, cutting, for sheet metal forming, for lifting, tensioning, driving in screws, removing hubs, etc.
  • the mode of operation corresponding to the respective requirement can be set.
  • the different ways of working can be varied as desired.
  • the pneumatically controlled pressure intensifier 1 has a double working cylinder, on one side of which a working cylinder receiving the pneumatically operated double-acting drive piston 1a, and on the other side of which a hydraulic pressure chamber is arranged, in which the displacement piston 1 b, which is assembled with the drive piston 1 a, can be immersed.
  • the two-position control valve 9 is connected to the primary space of the pneumatic working cylinder in front of the drive piston 1 a of the pressure intensifier 1 via the control line 21.
  • the control valve 9 is connected to a compressed air source via an air conditioner.
  • the control valve 9 is connected to the pilot valve 11 via the control line 22 and the valve 10.
  • the other side of the pilot valve 11 is connected via line 24 to line 21, which in turn connects the control valve 9 to the primary space of the pneumatic working cylinder.
  • Another connection of the control valve 9 is connected to the directional control valve 8 via the throttle check valve 7.
  • a buffer tank 25 is connected to the line between the throttle check valve 7 and the directional valve 8.
  • the pressure line 27 branches off from the additional line 26 between the control valve 9 and the directional control valve 8, which is connected via the directional control valve 8 to the secondary space formed behind the drive piston 1a of the pneumatic working cylinder, which leads via the quick-release valve 3 to the hydraulic reservoir 2.
  • the line between the directional control valve 8 and the secondary space is connected via the control line 28 to the signal input of the valve 10, on the one hand, and on the other hand it is connected to the control valve 9 via the throttle check valve 6.
  • the buffer tank 30 is connected between the throttle check valve 6 and the control valve 9.
  • the hydraulic tank 2 is connected via the throttle check valve 4 to the hydraulic pressure chamber of the pressure booster 1 in such a way that this connection can be shut off by the displacement piston 1.
  • this is achieved in that the hydraulic cylinder is formed in two parts and a sealed passage for the displacer 1 is formed between the two parts.
  • different hydraulic working devices see FIGS. 3a to 3j
  • the hydraulic reservoir 2 is connected via the throttle check valve 4 and the directional control valve 12 to the line 29 connecting the directional control valve 12 to the hydraulic pressure chamber.
  • the directional control valve 12 is a valve which determines the mode of operation, i. H. it ensures either a single cycle or a repetitive function depending on the actuation of the pilot valve.
  • the compressed air holds the pneumatic drive piston 1a in its basic position with a pressure of 6 bar via the control valve 9.
  • the control valve 9 receives the control pressure denoted by X via the valve 10 and the control line 22.
  • the control valve 9 switches over, whereby the primary space of the pneumatic working cylinder is connected to the atmosphere and the compressed air reaches the hydraulic tank 2 via the quick exhaust valve 3.
  • the compressed air supplies a control pressure Z for the directional control valve 8 via the throttle check valve 7.
  • the directional control valve 8 switches over, as a result of which the compressed air reaches the secondary space of the pneumatic working cylinder and displaces the drive piston 1a to the front.
  • the compressed air in the hydraulic tank 2 presses oil under a pressure of 6 bar via the throttle check valve 4 into the hydraulic pressure chamber or through it into the connected working device.
  • the working device makes an impact movement, ie it moves forward as long as the pressure can maintain the movement. This phase can be seen as the delivery of the working device.
  • the displacer 1 b first blocks the path of the liquid flowing out of the hydraulic container 2 and subsequently introduces oil into the working device under a pressure of approximately 150 bar; as a result, it performs the work cycle (cutting, pressing, etc.).
  • the displacer 1b continues until the working device reaches a closed state or until the control valve 9 receives the control pressure Y via the throttle check valve 6.
  • the buffer tank 30 is connected to the line between the throttle check valve 6 and the control valve 9, as a result of which the system functions as a time valve. Now the control valve 9 switches back.
  • the time t 1 elapsed between the pressing of the start button and the appearance of the control pressure Y (FIG. 2) can be regulated by means of the throttle check valve 6.
  • the time t 2 of the rapid advancement of the working device or the movement to the infeed is determined by the appearance of the control pressure Z, which can be set with the throttle check valve 7.
  • the feed speed of the displacer 1 is set with the throttle valve 5; the rapid feed rate t 2 is determined with the help of the throttle check valve 4.
  • the quantity valves 4, 5 determine the speed, while the time is determined by the quantity valves 6, 7, in place of which a time valve of any type can be used.
  • the quantity valves 4, 5, 6, 7 mentioned a wide variety of operating modes are possible. Some examples of these variations are shown in Fig. 2 represented by path-time diagrams.
  • the pistons return to their basic position after the end of a movement phase.
  • the return of the pistons is not connected to the automatic return of the working device to the starting position, since the return check is prevented by the check valve present in the directional control valve 12.
  • This operation can e.g. B. may be required when lifting, tensioning or pulling off a hub.
  • the control signal Y appears on the control valve 9, this switches back to its starting position; as a result, the control system is vented and the drive piston 1a of the pressure intensifier 1 returns to its basic position under the action of the air entering the primary space of the pneumatic cylinder.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP82902371A 1981-08-04 1982-08-04 Steuerschaltung für einen pneumatisch-hydraulischen druckwandler Expired EP0085080B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82902371T ATE19292T1 (de) 1981-08-04 1982-08-04 Steuerschaltung fuer einen pneumatischhydraulischen druckwandler.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU812257A HU185642B (en) 1981-08-04 1981-08-04 Penumatically controlled pressure converter for operating hydraulic work devices
HU225781 1981-08-04

Publications (3)

Publication Number Publication Date
EP0085080A1 EP0085080A1 (de) 1983-08-10
EP0085080A4 EP0085080A4 (de) 1984-01-20
EP0085080B1 true EP0085080B1 (de) 1986-04-16

Family

ID=10958536

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82902371A Expired EP0085080B1 (de) 1981-08-04 1982-08-04 Steuerschaltung für einen pneumatisch-hydraulischen druckwandler

Country Status (7)

Country Link
US (1) US4509330A (fi)
EP (1) EP0085080B1 (fi)
JP (1) JPS58501333A (fi)
DE (1) DE3270622D1 (fi)
FI (1) FI75214C (fi)
HU (1) HU185642B (fi)
WO (1) WO1983000540A1 (fi)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4729224A (en) * 1984-06-04 1988-03-08 Mcateer James D Installation, apparatus and method for actuating doors, gates and the like under extreme environmental conditions
IT207878Z2 (it) * 1986-03-06 1988-02-22 Iveco Fiat Convertitore pneumo idraulico per pinze di freni a disco
DE3611438A1 (de) * 1986-04-05 1987-10-08 Medical Res & Dev Ag Pneumatisch-hydraulischer wandler
US4879875A (en) * 1988-03-22 1989-11-14 The Boeing Company Fastener driving tool
DK171121B1 (da) * 1989-08-15 1996-06-17 Johannes Vagn Baatrup Hydraulisk trykforstærker
DE4221638B4 (de) * 1992-07-02 2005-11-03 Tox Pressotechnik Gmbh & Co. Kg Verfahren für einen hydraulischen Druckübersetzer
AT406984B (de) * 1998-12-22 2000-11-27 Joerg Thurner Vorrichtung zur umwandlung von in druckluft gespeicherter energie in mechanischer arbeit
US20110225961A1 (en) * 2008-12-10 2011-09-22 Numatics, Incorporated Pressurized Air-Spring Return Cylinder and Pneumatic Intensifier System
ITMO20100044A1 (it) * 2010-02-26 2011-08-27 De Hieronymis Carlo Maria Rozzi Intensificatore di forza idraulica a riarmo con mantenimento della posizione raggiunta e della forza di spinta ottenuta durante ogni fase di riarmo
TWM396335U (en) * 2010-07-23 2011-01-11 Chanto Air Hydraulics Co Ltd Pressure-boosting cylinder capable of storing oil
CN103586995A (zh) * 2013-11-12 2014-02-19 乐山市新联机械制造有限责任公司 密炼机卸料门的气液增压装置
WO2020178832A1 (en) * 2019-03-05 2020-09-10 Dan Davidian System and method for hydraulic-pneumatic drive with energy storage for elevators

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2229876A1 (fi) * 1973-05-14 1974-12-13 Beneteau Donald

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
US1940304A (en) * 1932-02-23 1933-12-19 Bergue S Patents Ltd De Machine for riveting, punching, pressing, stamping, and like operations
US2169423A (en) * 1936-08-04 1939-08-15 Midland Steel Prod Co Riveter
US3407601A (en) * 1965-07-26 1968-10-29 Martin Tool Works Inc Air-hydraulic system and apparatus
US3638532A (en) * 1969-06-30 1972-02-01 Fastener Corp Fastener driving tool
US3748860A (en) * 1971-02-05 1973-07-31 Altec Mfg Co Inc Hydraulic booster
CA983348A (en) * 1973-05-29 1976-02-10 Endre A. Mayer Dual single action ram intensifier
SU767410A1 (ru) * 1978-07-03 1980-09-30 Центральное проектно-конструкторское технологическое бюро "Автоспецоборудование" Пневмопривод возвратно-поступательного действи с автоматическим реверсированием
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
SU907319A1 (ru) * 1980-06-30 1982-02-23 Московский автомобильный завод им.И.А.Лихачева Пневмогидропривод возвратно-поступательного действи
DE3032430A1 (de) * 1980-08-28 1982-03-04 F.E. Schulte Strathaus Kg, 4750 Unna Vorrichtung zur erhoehung des druckes eines an einer druckmittelleitung anstehenden fluids fuer einen verbraucher

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2229876A1 (fi) * 1973-05-14 1974-12-13 Beneteau Donald

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
DESIGN ENGINEERING, Band 39, Dezember 1974 LONDEN (GB) "Applications of dashpot cylinders and check-units in hydro-pneumatic techniques", Seiten 29,31-35. *
ENGINEERS DIGEST, Band 34, nr. 8, August 1973 LONDON (GB) "Low-Cost Pneumatic Time-Delay Systems", Seiten 29-31. *
ÖLHYDRAULIK UND PNEUMATIK, Band 15, Nr. 1, Januar 1971 MAINZ (DE) K.-H. MUTH: "Pneumatisch verzögerte Steuerung von Druckluft-Wegeventilen", Seiten 36,37 *
PRODUCT ENGINEERING, Band 40, Nr. 12, 16. Juni 1969 NEW YORK (US) "Intensifier powered by shop air delivers 200,000-psi oil pressure", Seiten 115,116 *

Also Published As

Publication number Publication date
DE3270622D1 (en) 1986-05-22
FI831086L (fi) 1983-03-30
JPS58501333A (ja) 1983-08-11
EP0085080A4 (de) 1984-01-20
EP0085080A1 (de) 1983-08-10
US4509330A (en) 1985-04-09
FI75214B (fi) 1988-01-29
FI75214C (fi) 1988-05-09
FI831086A0 (fi) 1983-03-30
WO1983000540A1 (en) 1983-02-17
HU185642B (en) 1985-03-28

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