EP0023030A1 - Transmission hydropneumatique avec amplificateur de pression - Google Patents

Transmission hydropneumatique avec amplificateur de pression Download PDF

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Publication number
EP0023030A1
EP0023030A1 EP80104168A EP80104168A EP0023030A1 EP 0023030 A1 EP0023030 A1 EP 0023030A1 EP 80104168 A EP80104168 A EP 80104168A EP 80104168 A EP80104168 A EP 80104168A EP 0023030 A1 EP0023030 A1 EP 0023030A1
Authority
EP
European Patent Office
Prior art keywords
working
piston
cylinder housing
plunger
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.)
Withdrawn
Application number
EP80104168A
Other languages
German (de)
English (en)
Inventor
Eugen Rapp
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0023030A1 publication Critical patent/EP0023030A1/fr
Withdrawn legal-status Critical Current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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the two cylinder housing sections are arranged in one axis and the plunger moves in the same direction as the working piston during operation.
  • the new proposal amounts to arranging the cylinder housing sections for the plunger and for the working piston either side by side, i.e. in a structural unit with preferably parallel axes and opposite directions of movement of the plunger and working piston, or as completely separate cylinder housings in any orientation, the channel as pressure-resistant pipe or Hose line is executed.
  • the first variant enables the entire drive to be shortened to almost half its length.
  • the second variant opens up the possibility of a spatially further separated arrangement of the two cylinder housings, so that only the working cylinder housing that needs such a drive needs to be installed in the machine in question.
  • the stroke of the working piston can be infinitely limited.
  • this can be achieved in that the working piston has a second piston rod, which is led out of the rear of the working cylinder housing and carries a stop member which is adjustable in the longitudinal direction.
  • it is not infrequently desirable to be able to control the changeover from rapid traverse to power stroke in a stepless selection, even with drives that switch inherently depending on the force, ie as soon as the working piston opens an obstacle is encountered, i.e. a certain force is opposed to it.
  • a path-dependent changeover is achieved by a longitudinally displaceable stop sleeve surrounding the piston rod, which is supported on the working cylinder housing by a compression spring and on which the abovementioned stop member comes to a stop. If this stop sleeve also has a stop member which is adjustable in the longitudinal direction and which interacts with the stop member of the piston rod, both the switchover point and the total stroke of the working cylinder can be set separately.
  • the working piston is a pot piston, which is guided with its inner wall sealed on a trunk-shaped extension of the working cylinder housing, then, due to the separation of the working cylinder, there is the advantageous possibility of connecting the pressure-resistant channel arriving from the push-in chamber to the end annular space, which is the trunk-shaped Approach surrounds. Hydraulic oil is applied to the working piston on its end-face annular surface, while known pot pistons are acted upon by air on this annular surface for driving in rapid traverse. In the interest of expanding the applicability of a particular working cylinder housing, the air and hydraulic oil connections acting in the same direction can therefore be interchanged.
  • the insertion space 13 is connected via a channel 14 to the front opening of the cylinder jacket 7.
  • a stepped working piston 15,. Moves in this cylinder jacket and in the cylinder jacket 6. the piston rod 16 transmitting the driving force protrudes downward through the end plate 3.
  • a piston rod 17 protrudes through the head piece.
  • a stop screw 18 is screwed onto its threaded end.
  • an easily displaceable stop sleeve 19 is provided on the piston rod 17 and has a collar 20.
  • a compression spring 21 is clamped between this collar and the head piece 4. It presses the stop sleeve with its collar 20 upwards against an annular hood 22 which is firmly connected to the head piece 4.
  • the upper end of the stop sleeve 19 also has a thread, and a stop screw 23 of approximately the same diameter as the stop screw 18 is screwed onto this.
  • the annular spaces above and below the largest diameter of the working piston are provided with compressed air connections B and C.
  • the connected spaces between the annular piston 11 and the working piston 15 are filled with hydraulic oil.
  • the operation of the drive unit according to FIG. 1 is as follows: If port B is pressurized with compressed air, the working piston 15 moves downward in rapid traverse, with its section of smaller diameter sucking hydraulic oil from the storage space above the annular piston 11. This is the rapid traverse. If port A is also pressurized with compressed air, the plunger 10 moves into the insertion space 13, so that the working piston is moved downward with great force in accordance with the hydraulic transmission ratio in the power stroke.
  • the switch from rapid traverse to power stroke ie the connection of the pneumatic connection A, is taken care of a pneumatic control device, not shown.
  • the switch position of the working piston 15, in which the counterforce of the compression spring 21 is effective can be set on the stop screws 18 and 23. As soon as the stop screw 18 touches the stop screw 23, the compression spring 21 is pressed together via the stop sleeve 19. As a result, the counterforce acting on the working piston 15 increases very quickly, which triggers the switchover to the power stroke.
  • the drive arrangement according to FIG. 2 comprises a transmission cylinder housing 24, which is designed as a separate structural unit and is of relatively large size, but corresponds in construction to the translation cylinder housing 1 according to FIG. 1.
  • a head piece 25 also contains an insertion space 26, from which, however, several channels 27 branch off. Three are drawn, including an axially leading channel. However, there could be any number by adding to a star-shaped arrangement.
  • 28 smaller working cylinder housings 29 are connected to the channels 27 via pressure hoses, two of which are only shown in a reduced size and schematically.
  • Each of these working cylinder housings 29 contains a cup-shaped working piston 30, into which a trunk-shaped extension 31, which is sealed at its front end, projects.
  • Each working cylinder housing has two compressed air connections B and C. Due to their mutual action, the working pistons carry out their rapid traverse and return stroke.
  • the K is done by hydraulic rafthub B eaufschla- supply via the channels 27 and the pressure tubes 28 when the common for all working cylinder housing 29 plunger is acted upon in the booster cylinder housing 24 at the terminal A with compressed air.
  • a further advantage of the working cylinder housing 29 according to FIG. 2 is that the compressed air connection for the rapid traverse and the hydraulic connection can be interchanged.
  • the working cylinder 30 is pressurized with compressed air on its central inner surface and with hydraulic oil on its front annular surface.
  • the feed force in rapid traverse is thereby lower, but the hydraulic feed force in the power stroke is considerably greater. This means that two very different applications can be mastered with the same working cylinder housing.
  • FIG. 3 shows yet another embodiment of a working cylinder housing, which could also be used together with the translator cylinder housing 24 according to FIG. 2.
  • a stroke limitation and a path-dependent changeover from rapid traverse to power stroke could be applied.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Press Drives And Press Lines (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
EP80104168A 1979-07-21 1980-07-17 Transmission hydropneumatique avec amplificateur de pression Withdrawn EP0023030A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792929616 DE2929616A1 (de) 1979-07-21 1979-07-21 Druckuebersetzter hydropneumatischer antrieb
DE2929616 1979-07-21

Publications (1)

Publication Number Publication Date
EP0023030A1 true EP0023030A1 (fr) 1981-01-28

Family

ID=6076395

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80104168A Withdrawn EP0023030A1 (fr) 1979-07-21 1980-07-17 Transmission hydropneumatique avec amplificateur de pression

Country Status (6)

Country Link
EP (1) EP0023030A1 (fr)
DE (1) DE2929616A1 (fr)
ES (1) ES8103812A1 (fr)
IT (1) IT1131712B (fr)
PL (1) PL225771A1 (fr)
WO (1) WO1981000289A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3710178A1 (de) * 1987-04-01 1988-10-20 Antriebs Steuerungstech Ges Steuereinrichtung fuer einen pneumo-hydraulischen kraftantrieb
FR2652861A1 (fr) * 1989-09-18 1991-04-12 Savair Inc Appareil d'amplification d'une force appliquee a un outil.
EP0501384A2 (fr) * 1991-02-28 1992-09-02 Carlo Brasca Presse pneumatique-hydraulique à course réglable
EP0507070A2 (fr) * 1991-02-28 1992-10-07 Carlo Brasca Tête de presse, pneumatique-hydraulique combinée à actionnement rapide
EP0554760A1 (fr) * 1992-02-01 1993-08-11 TOX-PRESSOTECHNIK GmbH Multiplication de pression hydropneumatique
WO1997035114A1 (fr) * 1996-03-19 1997-09-25 Tox Pressotechnik Gmbh Machine-outil hydropneumatique
DE19630882C1 (de) * 1996-07-31 1998-03-05 Erwin Dimter Pneumatisch-hydraulische Vorschubeinheit mit automatischer Entlüftung und automatischem Leckölausgleich
DE19720252A1 (de) * 1997-05-15 1998-11-19 Kraemer & Grebe Kg Hydropneumatischer Druckübersetzer als Stanzenantrieb in Verpackungsmaschinen
DE102006045258A1 (de) * 2006-09-24 2008-04-10 Farger & Joosten Maschinenbau Gmbh Hydropneumatischer Druckübersetzer mit Hub- und Kraftbegrenzung

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2383402B1 (es) * 2010-02-02 2013-04-26 Tenias S.A. Sistema de accionamiento para palas cargadoras

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3426530A (en) * 1966-10-26 1969-02-11 Etablis L Faiveley Oleopneumatic jack with staged structure
GB1144373A (en) * 1966-01-21 1969-03-05 Jergen Tool Specialty Co Pressure multiplying means
DE1908058A1 (de) * 1969-02-18 1970-09-03 Erwin Dimter Vorrichtung zum Verstaerken des Drucks eines Hydraulikzylinders mittels Druckluft
DE2001387A1 (de) * 1970-01-14 1971-08-26 Volkswagenwerk Ag Zylinderanordnung zur Krafterzeugung mit einem Arbeits- und einem UEbersetzungszylinder
DE2258593A1 (de) * 1972-11-30 1974-06-12 Erhard Stueber Druckgasbetaetigter zylinder mit hydraulischer kraftverstaerkung
DE2651398A1 (de) * 1976-11-11 1978-05-18 Willi Horcher Stell- oder betaetigungsorgan fuer ein hin und her zu bewegendes funktionselement
FR2412732A1 (fr) * 1977-12-22 1979-07-20 Lezier Gerard Nouveau systeme oleo-pneumatique pour le remplissage rapide de verins hydrauliques a tres haute pression

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1144373A (en) * 1966-01-21 1969-03-05 Jergen Tool Specialty Co Pressure multiplying means
US3426530A (en) * 1966-10-26 1969-02-11 Etablis L Faiveley Oleopneumatic jack with staged structure
DE1908058A1 (de) * 1969-02-18 1970-09-03 Erwin Dimter Vorrichtung zum Verstaerken des Drucks eines Hydraulikzylinders mittels Druckluft
DE2001387A1 (de) * 1970-01-14 1971-08-26 Volkswagenwerk Ag Zylinderanordnung zur Krafterzeugung mit einem Arbeits- und einem UEbersetzungszylinder
DE2258593A1 (de) * 1972-11-30 1974-06-12 Erhard Stueber Druckgasbetaetigter zylinder mit hydraulischer kraftverstaerkung
DE2651398A1 (de) * 1976-11-11 1978-05-18 Willi Horcher Stell- oder betaetigungsorgan fuer ein hin und her zu bewegendes funktionselement
FR2412732A1 (fr) * 1977-12-22 1979-07-20 Lezier Gerard Nouveau systeme oleo-pneumatique pour le remplissage rapide de verins hydrauliques a tres haute pression

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3710178A1 (de) * 1987-04-01 1988-10-20 Antriebs Steuerungstech Ges Steuereinrichtung fuer einen pneumo-hydraulischen kraftantrieb
FR2652861A1 (fr) * 1989-09-18 1991-04-12 Savair Inc Appareil d'amplification d'une force appliquee a un outil.
US5247871A (en) * 1991-02-28 1993-09-28 Carlo Brasca Combined pneumatic-hydraulic press head with high actuation speed
EP0501384A2 (fr) * 1991-02-28 1992-09-02 Carlo Brasca Presse pneumatique-hydraulique à course réglable
EP0507070A2 (fr) * 1991-02-28 1992-10-07 Carlo Brasca Tête de presse, pneumatique-hydraulique combinée à actionnement rapide
EP0501384A3 (en) * 1991-02-28 1992-12-02 Carlo Brasca Combined pneumatic-hydraulic press with controlled stroke
EP0507070A3 (en) * 1991-02-28 1992-12-09 Carlo Brasca Combined pneumatic-hydraulic press head with high actuation speed
US5247870A (en) * 1991-02-28 1993-09-28 Carlo Brasca Combined pneumatic-hydraulic press with controlled stroke
EP0554760A1 (fr) * 1992-02-01 1993-08-11 TOX-PRESSOTECHNIK GmbH Multiplication de pression hydropneumatique
WO1997035114A1 (fr) * 1996-03-19 1997-09-25 Tox Pressotechnik Gmbh Machine-outil hydropneumatique
DE19630882C1 (de) * 1996-07-31 1998-03-05 Erwin Dimter Pneumatisch-hydraulische Vorschubeinheit mit automatischer Entlüftung und automatischem Leckölausgleich
DE19720252A1 (de) * 1997-05-15 1998-11-19 Kraemer & Grebe Kg Hydropneumatischer Druckübersetzer als Stanzenantrieb in Verpackungsmaschinen
DE102006045258A1 (de) * 2006-09-24 2008-04-10 Farger & Joosten Maschinenbau Gmbh Hydropneumatischer Druckübersetzer mit Hub- und Kraftbegrenzung
DE102006045258B4 (de) * 2006-09-24 2012-11-08 Farger & Joosten Maschinenbau Gmbh Hydropneumatischer Druckübersetzer mit Hub- und Kraftbegrenzung

Also Published As

Publication number Publication date
ES494330A0 (es) 1981-03-16
IT1131712B (it) 1986-06-25
DE2929616A1 (de) 1981-02-12
WO1981000289A1 (fr) 1981-02-05
PL225771A1 (fr) 1981-06-05
ES8103812A1 (es) 1981-03-16
IT8023520A0 (it) 1980-07-18

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Legal Events

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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AK Designated contracting states

Designated state(s): AT CH FR GB LU NL SE

STAA Information on the status of an ep patent application or granted ep patent

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18D Application deemed to be withdrawn

Effective date: 19820105

RIN1 Information on inventor provided before grant (corrected)

Inventor name: RAPP, EUGEN