EP0554760A1 - Multiplication de pression hydropneumatique - Google Patents

Multiplication de pression hydropneumatique Download PDF

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Publication number
EP0554760A1
EP0554760A1 EP93101144A EP93101144A EP0554760A1 EP 0554760 A1 EP0554760 A1 EP 0554760A1 EP 93101144 A EP93101144 A EP 93101144A EP 93101144 A EP93101144 A EP 93101144A EP 0554760 A1 EP0554760 A1 EP 0554760A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
pin
pressure intensifier
piston rod
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Withdrawn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
EP93101144A
Other languages
German (de)
English (en)
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 EP0554760A1 publication Critical patent/EP0554760A1/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Withdrawn legal-status Critical Current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
    • F15B11/02—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.
  • Pressure intensifiers of this type are pneumatic working systems with an energy-saving and fast-working pneumatic cylinder, into which a hydraulic system is integrated, with which a force stroke with a very high actuating force is applied from a desired forward stroke in the working direction. Although there are only pneumatic connections to the outside, forces are generated as with hydraulic cylinders.
  • the stepped piston is machined from one cylindrical block each manufactured in which the larger diameter of the stepped piston is turned down to the smaller diameter piston step or the diameter of the piston rod.
  • a part of great dimensional accuracy is obtained as a result, but at the expense of high manufacturing costs, since apart from the complex machining, considerable effort is involved in hardening, grinding and straightening the stepped piston.
  • such a stepped piston is not only an extremely highly stressed part, but must be manufactured and machined extremely precisely in order to meet its requirements.
  • the lateral surfaces of the stepped piston part of smaller diameter and the piston rod form sliding surfaces for radial seals that have to withstand high working pressures, particularly in the case of the stepped piston part, and this over an extraordinarily large number of working strokes.
  • the hydropneumatic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage that the individual piston parts to be connected to one another, namely disk pistons, working pistons and piston rods, can be produced from a different material according to the respective load, the parts also being separate, that is to say independent from each other, can be processed, for example during chip removal, hardening or when grinding. Another advantage is that these parts can be produced from bar material, which each has only the required maximum diameter, whereby material costs and machining costs can be reduced accordingly.
  • the working space in the hydropneumatic pressure intensifier is connected to a hydraulic storage space and this connection is blocked by a plunger after a pneumatically effected rapid traverse for hydraulic high-pressure generation, the plunger being drivable by a pneumatic piston and on the working piston on the
  • An auxiliary piston (second piston rod) projecting outward from the housing and radially sealed to the housing is arranged coaxially with the side facing away from the piston piston, thereby providing an annular surface remaining between the working piston and the auxiliary piston.
  • this auxiliary piston serves as a further part connected to the stepped piston.
  • such an auxiliary piston offers Advantages for the overall stroke limitation, on the other hand above all the possibility of obtaining high urgent and retraction forces, this auxiliary piston being used as a piston rod for the pulling mode of operation of the pressure intensifier.
  • a pin on the end face of one part and a corresponding blind hole in the end face of the other adjacent part, in which the pin can be fastened serves as the connection between the piston rod and the working piston or between the working piston and the auxiliary piston. Since these are turned parts, extremely precise axial alignment of the individual parts can be guaranteed.
  • a central bore is present in the disc piston, through which the pin of the working piston or the piston rod engages the blind bore of the piston rod or the working piston, so that the disc piston can be clamped between the working piston and the piston rod on this pin.
  • a thread can be present on the pin as a connecting means, which engages in a corresponding thread in the blind hole and / or a shrink connection and / or adhesive connection can be present between the pin and the blind hole or a welded connection ( Friction welding) must be present, in particular between the piston disc and the working piston on the one hand and the piston rod on the other.
  • a radial seal can be provided for further sealing between the pin and the blind bore (which is then penetrated by the longitudinal bore on the end face), in particular if it is only a screw or press connection in order to prevent oil from coming under high pressure from this oil supply hole between the pin and the blind hole into one of the pneumatic spaces.
  • FIGS. 1 and 2 have cylindrical outer dimensions.
  • Figure 1 as a cylinder
  • Figure 2 as two cylinders lying side by side, which are interconnected.
  • a working piston 2 is arranged axially displaceably 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 down and vice versa, as soon as an overpressure is generated in the pneumatic chamber 8, the working piston 2 is pushed up again into the starting position shown.
  • a storage space 9 hydraulically connected to working space 1 is shown in the drawing, in which a hydraulic accumulator pressure is generated by a storage piston 11 with storage spring 12, which is sufficient to fill working space 1 with hydraulic oil during the rapid stroke of working piston 2 hold.
  • the storage piston 11 is guided in a radially sealing and axially displaceable tube 13.
  • a drive piston 14 of a plunger 15 is mounted in this casing tube 13 and can be displaced in the direction of the working space 1 against the force of the storage spring 12.
  • the plunger 15 penetrates the storage piston 11 in a radially sealed manner and dips into the storage space 9.
  • the drive piston 14 with plunger 15 is driven by compressed air which is conducted into a working space 16 above the drive piston 14.
  • the pneumatic pressure in the working space 16 is reduced, so that the storage spring 12 pushes the drive piston 14 back into the starting position shown.
  • the pressure piston in the pneumatic chamber 7 and the pressure build-up in the pneumatic chamber 8 push the working piston 2 back through the disk piston 5 into the starting position shown, hydraulic fluid flowing back into the storage chamber 9 through the working piston 2.
  • the working space 1 is filled via a central bore 19 in the working piston 2 and the piston rod 4.
  • the working piston 2, disc piston 5 and piston rod 4 consist of three parts which are connected to one another.
  • a pin 22 is arranged on the end face 21 facing the working piston 2, the end portion of which is provided with a thread 23.
  • the disc piston 5, which has a central bore 25 for this purpose, is pushed on a cylindrical section 24 of this pin 22.
  • the working piston 2 has a threaded bore 27 on the end face 26 facing the disc piston 5, into which the pin 22 is screwed with its thread 23, the disc piston 5 being clamped between the end faces 21 and 26.
  • annular seal 28 is arranged in the threaded region 23, 27.
  • radial seals 29 of the working piston 2 are present between the pneumatic space 7 and the working space 1 for the bore in the housing 3 that receives it.
  • the second exemplary embodiment shown in FIG. 2 works in principle like the first, which is why the same reference numbers, but increased by one hundred, have been chosen for the corresponding parts.
  • the casing tube 113 which accommodates the storage piston 111, the drive piston 114 and the storage spring 112 is arranged parallel to the casing tube 106 and the housing 103, in which the disk piston 105, the piston rod 104 and the working piston 102 operate .
  • the two cylindrical parts are connected to one another via a housing block 31, in which runs a connecting channel 32 which connects the storage space 109 to the working space 101.
  • a section of this connecting channel 32 is the connecting bore 117 with the radial seal 118, into which the plunger 115 plunges after a certain stroke of the drive piston 114 has been covered.
  • This parallel arrangement enables an auxiliary piston 33 to be attached to the working piston 102 on the side facing away from the piston rod 104 and projecting outside the housing, in particular the housing block 31.
  • This auxiliary piston 33 is fastened to the working piston 102 by screwing it into a corresponding threaded bore 34. Radial seals 35 prevent oil from escaping under pressure from the working space 101 to the outside.
  • the auxiliary piston 33 works together with a threaded bolt 36 which can be screwed into a bush 37 connected to the housing block 31, as a result of which the respective starting position and thus the total stroke of the working piston 102 or the piston rod 104 can be adjusted.
  • connection between the piston rod 104 and the working piston 102 takes place, as in the first exemplary embodiment, by clamping the piston disk 105 via a threaded pin 122, which is engaged by a corresponding threaded hole 127 in the working piston 102.
  • a corresponding press or shrink connection instead of a pure threaded connection between the working piston 2, 102, the piston rod 4, 104 or the auxiliary piston 33, a corresponding press or shrink connection, adhesive connection or weld connection or a combination of several known connections of this type can also be used.
  • the decisive factor is that there is a pin which engages in a corresponding pocket opening of the other part, so it is also conceivable that the pin is arranged, for example, on the working piston and engages in corresponding pocket openings of the piston rod or auxiliary piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Damping Devices (AREA)
EP93101144A 1992-02-01 1993-01-26 Multiplication de pression hydropneumatique Withdrawn EP0554760A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4202893 1992-02-01
DE4202893 1992-02-01

Publications (1)

Publication Number Publication Date
EP0554760A1 true EP0554760A1 (fr) 1993-08-11

Family

ID=6450768

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93101144A Withdrawn EP0554760A1 (fr) 1992-02-01 1993-01-26 Multiplication de pression hydropneumatique

Country Status (3)

Country Link
EP (1) EP0554760A1 (fr)
JP (1) JPH07248001A (fr)
DE (1) DE4301983A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0972946A1 (fr) * 1998-07-14 2000-01-19 Fresmak, S.A. Multiplicateur de force pneumo-hydraulique
WO2015169693A1 (fr) * 2014-05-08 2015-11-12 Weber Schraubautomaten Gmbh Système de vissage

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0828942B1 (fr) * 1996-03-19 2000-08-09 TOX-PRESSOTECHNIK GmbH Machine-outil hydropneumatique
DE19907883A1 (de) * 1999-02-24 2000-08-31 Tox Pressotechnik Gmbh Hydropneumatischer Druckübersetzer
DE102006011637A1 (de) * 2006-03-14 2007-09-20 Festo Ag & Co. Pneumatischer Linearantrieb mit hydraulischer Kraftverstärkung
CN105003472B (zh) * 2015-06-05 2017-05-03 武汉工程大学 一种气‑液增压缸

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3260167A (en) * 1964-10-26 1966-07-12 Case Co J I Hydraulic cylinder with fast-acting means
FR2287605A1 (fr) * 1974-10-10 1976-05-07 Reuti Anstalt Cylindre operateur actionne par fluide, avec convertisseur d'efforts incorpore
EP0023030A1 (fr) * 1979-07-21 1981-01-28 RAPP, Eugen Transmission hydropneumatique avec amplificateur de pression

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3260167A (en) * 1964-10-26 1966-07-12 Case Co J I Hydraulic cylinder with fast-acting means
FR2287605A1 (fr) * 1974-10-10 1976-05-07 Reuti Anstalt Cylindre operateur actionne par fluide, avec convertisseur d'efforts incorpore
EP0023030A1 (fr) * 1979-07-21 1981-01-28 RAPP, Eugen Transmission hydropneumatique avec amplificateur de pression

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0972946A1 (fr) * 1998-07-14 2000-01-19 Fresmak, S.A. Multiplicateur de force pneumo-hydraulique
WO2015169693A1 (fr) * 2014-05-08 2015-11-12 Weber Schraubautomaten Gmbh Système de vissage

Also Published As

Publication number Publication date
JPH07248001A (ja) 1995-09-26
DE4301983A1 (fr) 1993-09-23

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