[go: up one dir, main page]

WO1996041957A1 - Unite hydraulique multiplicatrice de pression, notamment pour une presse fonctionnant selon le procede d'extrusion a haute pression interieure - Google Patents

Unite hydraulique multiplicatrice de pression, notamment pour une presse fonctionnant selon le procede d'extrusion a haute pression interieure Download PDF

Info

Publication number
WO1996041957A1
WO1996041957A1 PCT/EP1996/002490 EP9602490W WO9641957A1 WO 1996041957 A1 WO1996041957 A1 WO 1996041957A1 EP 9602490 W EP9602490 W EP 9602490W WO 9641957 A1 WO9641957 A1 WO 9641957A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
piston rod
pressure
cylinder
chamber
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.)
Ceased
Application number
PCT/EP1996/002490
Other languages
German (de)
English (en)
Inventor
Manfred Breckner
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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 Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of WO1996041957A1 publication Critical patent/WO1996041957A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D26/00—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces
    • B21D26/02—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces by applying fluid pressure
    • B21D26/021—Deforming sheet bodies
    • B21D26/027—Means for controlling fluid parameters, e.g. pressure or temperature
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D26/00—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces
    • B21D26/02—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces by applying fluid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D26/00—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces
    • B21D26/02—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces by applying fluid pressure
    • B21D26/021—Deforming sheet bodies
    • B21D26/029—Closing or sealing means

Definitions

  • Hydraulic pressure intensifier unit in particular for a press working according to the internal high pressure molding process
  • the invention is based on a hydraulic pressure intensifier unit, which is used in particular on a press working according to the internal high pressure forming method and which has the features from the preamble of claim 1.
  • Such a hydraulic pressure intensifier unit is known from DE 43 12 589 AI.
  • the primary piston of the pressure intensifier is axially displaceable in a first cylinder space, while the secondary piston, which is located on a first side of the primary piston, is immersed in a high pressure space.
  • a piston rod extends from the second side of the primary piston opposite the secondary piston, which passes through a housing head that closes the first cylinder chamber, a second cylinder chamber that is separate from the first cylinder chamber, and a cover that closes the second cylinder chamber and projects above the second cylinder chamber
  • the cylinder chamber can be supplied with hydraulic fluid through an axial channel running centrally through the piston rod, the primary piston and the secondary piston of the pressure intensifier, in order to fill the blank to be deformed.
  • the axial channel and the second cylinder chamber are connected to one another via a transverse bore in the piston rod. So that this transverse bore does not get into the area of seals between the first and the second cylinder space, the length of the second cylinder space is greater than the maximum stroke of the piston rod.
  • the primary piston, secondary piston and piston rod of the pressure converter can also be moved in rapid traverse.
  • a completely separate rapid traverse cylinder with a rapid traverse piston and with a rapid traverse piston rod is provided, which with that from the second Cylinder chamber protruding piston rod of the pressure intensifier is connected.
  • the piston rod of the pressure intensifier itself forms the housing of the rapid traverse cylinder, which is displaceable relative to a stationary rapid traverse piston.
  • the known hydraulic pressure intensifier units with rapid traverse cylinders are relatively long axially.
  • the aim of the invention is to further develop a hydraulic pressure intensifier unit with the features from the preamble of claim 1 in such a way that smaller axial dimensions are possible.
  • the rapid-motion piston is located in the second cylinder space and divides it into a piston rod-side subspace un into a piston rod-side subspace that in the piston rod-side compartment a first pressure medium channel un opens into the piston rod-side compartment a second pressure medium channel and that the axial channel is open to the piston rod-side compartment.
  • the matched to the maximum stroke of the pressure intensifier length of the second cylinder space is also used for the stroke of the rapid traverse piston, s that compared to the known hydraulic pressure intensifier units, the axial length can be significantly reduced without the supply of pressure medium through the axial channel in front of the face of the secondary piston would be more difficult. It is also advantageous that the piston rod of the pressure intensifier does not have to be guided outward from the second cylinder space, which would lead to additional sealing problems.
  • a hydraulic pressure booster unit of the type according to the invention
  • a hydraulic oil is used as the pressure medium with which the primary piston of the pressure booster is applied.
  • a water-based hydraulic fluid a so-called HFA fluid
  • HFA fluid is used as the pressure medium in which the internal high pressure required to deform a blank is generated.
  • the two partial spaces on the two sides of the rapid traverse piston can now be acted upon with the same pressure fluid. If an HFA liquid is the pressure medium with which a blank is deformed, the rapid traverse piston is also pressurized with this HFA liquid on the side facing away from the piston rod. No HFA liquid can get into the hydraulic oil and no hydraulic oil can get into the HFA liquid via the rapid traverse piston.
  • the maximum pressure is set to a value which has proven to be favorable for filling the blank to be formed. This maximum pressure is in the range between 30 and 70 bar.
  • the piston rod-side subspace can preferably be subjected to a higher pressure than the piston rod-side pressure chamber in order to be able to move the primary piston and the secondary piston of the pressure intensifier in rapid traverse.
  • the hydraulic pressure booster unit is advantageously developed in accordance with claim 5.
  • the displacement sensor is then arranged so that it does not enlarge the axial dimensions of the pressure intensifier unit.
  • the hydraulic pressure intensifier unit shown comprises a docking cylinder 10, a pressure intensifier 11 and a rapid traverse cylinder 12 for the pressure intensifier 11.
  • the parts named with regard to their function cannot be clearly separated from one another locally, but are integrated into one another to form a compact unit.
  • the housing 13 of the unit includes a docking cylinder 10 and the pressure intensifier 11 common, a one-piece housing middle part 14, which has a third cylinder wall 15 and a first cylinder space 16.
  • the two cylinder spaces 15 and 16 are open on opposite sides and separated from one another by a bottom 17 of the housing middle part 14, from which the cylinder jackets 18 and 19 extend in opposite directions in the cylinder spaces.
  • the third cylinder space 15 is provided with a housing head 20 and de first cylinder chamber 16 closed with a housing head 21.
  • the third cylinder chamber 15 belongs to the docking cylinder 10.
  • a docking piston 25 is axially displaceable in it and has a piston rod attached to it only on one side. This passes al docking piston rod 26 through the housing head 20 to the outside. A its free end is screwed on a flange 27, with which egg-shaped tubular blank 37 can be closed.
  • a central bore 28 extends axially through the Andoc piston 25 and through the docking piston rod 26, this bore weaving a section 29 with a smaller diameter and has a section 30 with a larger diameter, the latter extends from the end face of the docking piston rod 26 facing the flange 27 to a radial shoulder 3 which has an axial distance from the housing head 20 even when the docking piston rod 26 is retracted to the maximum.
  • Docking piston rod 26 and housing head 20 are sealed off from one another with the aid of two axially spaced seals 32 and 33, between which a leak line 34 extends.
  • hydraulic oil can flow into or out of the two partial spaces 15a and 15b of the cylinder space 15 separated from one another by the docking piston 25.
  • the step 31 in the bore 28 is not overrun by the free end of the docking piston rod 26 in any phase of a working cycle of the pressure booster unit.
  • the free end of the secondary piston 41 is therefore always axially outside the housing head 20.
  • a piston rod 42 which is opposite to the secondary piston 41 is fastened and passes through a bore 43 in the housing head 21 into a second cylinder formed with the aid of this housing head and a housing pot 22 the space 44 occurs and there is firmly connected to a rapid-motion piston 45.
  • the rapid-motion piston 45 divides the cylinder space 44 into two partial spaces 44a and 44b, each of which can be supplied with a pressure fluid via a channel 47 or 48 in the housing pot 22.
  • a water-based hydraulic fluid (HFA fluid) is intended for this.
  • a channel 49 leads centrally through the piston rod 42, the primary piston 40 and the secondary piston 41 of the pressure intensifier 11 and is supplied through a transverse bore 50 with the pressure fluid via the channel 48.
  • th partial chamber 44a of the cylinder chamber 44 is connected and at the mouth of which in the section 30 of the bore 28 there is a check valve 51 blocking the channel 48.
  • the primary piston 40 of the pressure booster 11 can be alternately pressurized on both sides via the channels 52 and 53 passing through the cylinder jacket 19. Hydraulic oil is used as the pressure medium.
  • a number of seals are provided to separate the various pressure chambers and the various hydraulic fluids from one another.
  • three axially spaced seals 60, 61 and 62 are arranged between the housing head 21 and the piston rod 42. Between the seals 60 and 61 there is a leakage line 63, in which water-based hydraulic fluid leaking from the part space 44a of the cylinder space 44 is discharged via the seal 60. Between the seals 61 and 62 there is a leakage line 64, via which the hydraulic oil leaks out of the partial space 16a of the cylinder space 16 via the seal 62.
  • two seals 65 and 66 are arranged at an axial distance from one another, between which a leak line 67 comes off, which is connected to the tank as is usual with a leak and which a mutual influence of the pressures in the two sub-spaces 15a and 16b of the cylinder spaces 1 and 16, which are separated from one another by the base 17, is prevented.
  • the seal 68 is located immediately behind the piston-side start of the bore 28 in the docking piston 25.
  • the other two seals 69 and 70 are located just before the step 31 in radial planes, which also extend in front of the housing head 20 when the docking piston rod is retracted completely.
  • the seals recognizable in FIG. 1 can each be composed of a plurality of sealing rings, which are also axially spaced apart.
  • a leakage line 71 for the hydraulic fluid which leaks from section 30 of the bore 28 via seal 70, leads through the docking piston rod 26 to the outside.
  • Another leakage line 72 is also still in each position of the docking piston rod 26 in front of the housing head 20, passes transversely through the docking piston rod 26 and opens into the section 29 of the bore 28 between the two seals 68 and 69 Hydraulic oil discharged that leaks through the seal 68.
  • the HFA liquid is fed to the two channels 47 and 48 via a control block 80, which has a pump connection 81 connected to a pump 79 and a tank connection 82 and to which various valves are attached.
  • One of these valves is a 4/2-way valve 83 which is connected to the tank connection 82 with a valve connection A and to the pump connection 81 of the control block 80 with a valve connection B.
  • a channel 85 leads from a valve connection P of the directional control valve 83 to an output 86 of the control block 80, to which the channel 47 is connected.
  • Another port T of the directional valve 83 is connected to a port A of a 3/2-way seat valve 87. In the switching position of the directional control valve 83 shown in the drawing, its connections A and P as well as B and T are connected to one another. In the other switching position there is a connection between the connections A and T and the connections B and P.
  • connection A In the position shown, the 3/2-way seat valve 87 switches through the connection A to a connection T, which connects directly to the tank connection 82 of the control block 80 and, via a check valve 88 opening towards it, to the leak line 63 is.
  • connection A In the other switching position of the 3/2-way seat valve 87, the connection A is connected to a connection P, which is located at an output 89 of the control block 80, to which the channel 48 is connected.
  • the maximum pressure at port P of the 3/2-way seat valve 87 is determined by a pressure relief valve 90, which may be set to a value of approximately 50 to 60.
  • the maximum pressure at the port P of the 4/2-way valve 83 is determined by a pressure limiting valve 91 which is set to a higher maximum pressure than the pressure limiting valve 90, for example 110 bar. Hydraulic fluid can be sucked in from the tank connection 82 of the control block into the two partial spaces of the cylinder space 44 via suction valves 92.
  • the HFA liquid is circulated by the pump 79 via the pump connection 81 of the control block 80, the 4/2-way valve 83, the 3/2-way seat valve 87 and the tank connection 82 of the control block 80 promoted in circulation.
  • the docking piston 25 first pushes the flange 27 close to the blank 37 to be deformed.
  • the 3/2-way seat valve is switched so that HFA liquid from the pump connection 81 of the control block 80, via the directional valve 83, the 3/2-way valve 87, the channel 48, the partial area 44a of the cylinder space 44, the transverse bore 50, the longitudinal bore 49, the check valve 51, the section 30 of the bore 28 and a bore 75 in the flange 27 are conveyed into the blank, where the air escapes from the blank through a gap between the flange and the blank together with HFA liquid.
  • the pressure in the blank increases.
  • the blank is considered filled and is closed by the docking cylinder. Now the two way valves 83 and 87 are switched.
  • the docking piston 25 can be moved further in order to axially feed material of the blank.
  • the liquid in the formed blank is first decompressed by partially withdrawing the primary piston 40 and the secondary piston 41 of the pressure intensifier 11 together with the rapid-motion piston 45, and then the docking piston 25 is brought back into the starting position shown in the drawing.
  • a displacement sensor 95 which is arranged decentrally in the area of housing pot 22 and housing head 21 without increasing the axial dimensions of the pressure booster unit.
  • the displacement sensor is rod-shaped and has a first part 96, which is fixed in place on the housing pot 22, and a rod 97, which is fastened to the primary piston 40 and is tightly guided through the housing head 21 as a second part.
  • the rod carries at its free end an annular permanent magnet, not shown, which is displaced along a rod 98 of the first part 96 when the primary piston 40 moves.
  • the displacement sensor 95 emits a different signal.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Abstract

Une unité hydraulique multiplicatrice de pression connue comprend un multiplicateur de pression (11) pourvu d'un piston primaire (40) qui se déplace axialement dans une première chambre de cylindre (16), un piston secondaire (41) situé d'un côté du piston primaire (40) et qui plonge dans une chambre sous haute pression (28), et une tige de piston (42) qui part du deuxième côté du piston primaire (40) et qui s'étend jusqu'à une deuxième chambre de cylindre (44) séparée de la première chambre de cylindre (16). Un liquide hydraulique peut être amené depuis un raccordement extérieur jusqu'à la chambre sous haute pression par l'intermédiaire de la deuxième chambre de cylindre (44) et un canal axial (49) qui traverse longitudinalement la tige de piston (42), le piston primaire (40) et le piston secondaire (41). Outre le multiplicateur de pression (11), l'unité comprend un cylindre à déplacement rapide (12) dont le piston à déplacement rapide (45) est relié à la tige de piston (42) du multiplicateur de pression (11). Afin d'obtenir une unité hydraulique multiplicatrice de pression d'une longueur réduite, le piston à déplacement rapide (45) se situe dans la deuxième chambre de cylindre (44) et celle-ci se divise en une chambre partielle (44a) située du côté de la tige du piston et en une chambre partielle (44b) située du côté opposé à la tige de piston. Un canal à fluide hydraulique (48) débouche dans la chambre partielle (44a) située du côté de la tige de piston et un deuxième canal à fluide hydraulique (47) débouche dans la chambre partielle (44b) située du côté opposé à la tige du piston. Le canal axial est ouvert sur la chambre partielle (44a) située du côté de la tige du piston.
PCT/EP1996/002490 1995-06-09 1996-06-07 Unite hydraulique multiplicatrice de pression, notamment pour une presse fonctionnant selon le procede d'extrusion a haute pression interieure Ceased WO1996041957A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1995121102 DE19521102A1 (de) 1995-06-09 1995-06-09 Hydraulische Druckübersetzereinheit, insbesondere für eine nach dem Innenhochdruckumformverfahren arbeitende Presse
DE19521102.2 1995-06-09

Publications (1)

Publication Number Publication Date
WO1996041957A1 true WO1996041957A1 (fr) 1996-12-27

Family

ID=7764033

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1996/002490 Ceased WO1996041957A1 (fr) 1995-06-09 1996-06-07 Unite hydraulique multiplicatrice de pression, notamment pour une presse fonctionnant selon le procede d'extrusion a haute pression interieure

Country Status (2)

Country Link
DE (1) DE19521102A1 (fr)
WO (1) WO1996041957A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6499295B1 (en) 1998-08-06 2002-12-31 Mannesmann Rexroth Ag Hydro-transformer
DE19844648A1 (de) * 1998-08-06 2000-02-10 Mannesmann Rexroth Ag Hydro-Transformator

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3910087A (en) * 1974-12-18 1975-10-07 Boeing Co Hydraulic-forming machine
DD135694A1 (de) * 1977-04-05 1979-05-23 Vyzk Ustav Tvarecich Stroju Vorrichtung zum hydromechanischen ziehen
DE4312589A1 (de) * 1992-10-27 1994-04-28 Rexroth Mannesmann Gmbh Hydraulisches System für eine Umformpresse

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3907944A1 (de) * 1989-03-11 1990-09-13 Bochumer Eisen Heintzmann Stellvorrichtung mit einem zylinder und einem in dem zylinder gefuehrten kolben
DE4334220A1 (de) * 1993-10-07 1995-04-13 Rexroth Mannesmann Gmbh Verfahren zur Herstellung eines rohrartigen Hohlkörpers und Presse zur Durchführung eines solchen Verfahrens

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3910087A (en) * 1974-12-18 1975-10-07 Boeing Co Hydraulic-forming machine
DD135694A1 (de) * 1977-04-05 1979-05-23 Vyzk Ustav Tvarecich Stroju Vorrichtung zum hydromechanischen ziehen
DE4312589A1 (de) * 1992-10-27 1994-04-28 Rexroth Mannesmann Gmbh Hydraulisches System für eine Umformpresse

Also Published As

Publication number Publication date
DE19521102A1 (de) 1996-12-12

Similar Documents

Publication Publication Date Title
EP0579037B1 (fr) Multiplicateur de pression hydropneumatique
DE102009036663B4 (de) Innenhochdruckumformwerkzeug und ein Verfahren zum Betreiben dessen
DE102008063241A1 (de) Hauptzylinder
DE202009007668U1 (de) Lasthalteventil mit Druckbegrenzungsfunktion
DE3128798C2 (de) Steuervorrichtung für eine hydraulische blockiergeschützte Fahrzeugbremse
DE19631803B4 (de) Hydraulische Steuervorrichtung
DE4208980A1 (de) Hydraulische antriebsvorrichtung mit einem zylinder
DE4312589C2 (de) Hydraulisches System für eine Umformpresse
WO1996041957A1 (fr) Unite hydraulique multiplicatrice de pression, notamment pour une presse fonctionnant selon le procede d'extrusion a haute pression interieure
DE2522977A1 (de) Fluiddruckverstaerker
EP0254867B1 (fr) Dispositif pour changer avec peu de perte le débit d'une pompe à débit constant
EP0830221B1 (fr) Unite hydraulique multiplicatrice de pression, notamment pour une presse fonctionnant selon le procede d'extrusion a haute pression interieure
DE3448016C2 (fr)
DE4435848A1 (de) Servomotor
WO2004018120A1 (fr) Cylindre principal ou cylindre de compression d'une extrudeuse
DE4217121C2 (de) Freikolben-Zylinder-Vorrichtung mit zwei verschiedenen Druckflüssigkeiten
DE4345339C2 (de) Hydraulisches System für eine Umformpresse
DE69805376T2 (de) Hydraulische Druckübersetzer
DE10051042C2 (de) Antriebszylinder für Stanzen, Prägemaschinen, Pressen und dergleichen
EP0384157B1 (fr) Soupape à deux voies à commande pilotée hydrauliquement en manière à siège
DE2318915C2 (de) Folgesteuereinrichtung für eine einseitig verstellbare hydrostatische Verdrängermaschine
DE102005047823A1 (de) Eilgangzylindereinheit
DE60013324T2 (de) Verfahren und vorrichtung zur hydraulischen druckerzeugung
DE3819921C2 (fr)
EP0071655B1 (fr) Pompe hydraulique à actionnement pneumatique

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): CA CZ JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: CA