EP0579037B2 - Hydropneumatic pressure intensifier - Google Patents

Hydropneumatic pressure intensifier Download PDF

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Publication number
EP0579037B2
EP0579037B2 EP93110428A EP93110428A EP0579037B2 EP 0579037 B2 EP0579037 B2 EP 0579037B2 EP 93110428 A EP93110428 A EP 93110428A EP 93110428 A EP93110428 A EP 93110428A EP 0579037 B2 EP0579037 B2 EP 0579037B2
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EP
European Patent Office
Prior art keywords
piston
operating
pressure
chamber
storage
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EP93110428A
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German (de)
French (fr)
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EP0579037A1 (en
EP0579037B1 (en
Inventor
Viktor Dipl.-Ing. Malina
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Tox Pressotechnik GmbH and Co KG
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Tox Pressotechnik GmbH and Co KG
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    • 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
    • F15B2211/21—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 translator according to the type of the main claim.
  • On Main problem with such hydropneumatic pressure intensifiers consists in the sealing between the storage room and the control room, because the hydraulic pressures in the storage space and the pneumatic ones Press continuously in the control room during a work cycle change, and not necessarily change synchronously, whereby on the one hand there is a risk that oil from the storage space in the Control room arrives and this causes leakage losses that the Working capacity of the hydropneumatic pressure intensifier can affect, or there is a risk that air from the Control room enters the storage room where it is absorbed by the oil with the disadvantage that it gets into the work area and there the high pressure phase of the pressure stroke to an intensified Compressibility tends with all of the resulting disadvantages for the working ability of the unit.
  • pressure translators (DE-OS 2810 894) are both to the wall of the working cylinder, as well as to the outer surface of the Plunger two radial seals provided with the purpose one to achieve optimal air-oil separation. Is problematic here in particular, that the inclination of the air from the control room in the Storage space does not come about in the low pressure phase is present, but rather in the high pressure phase, whereby also small amounts of air as wall laminates during the axial movement of the Storage piston are "pumped past" the radial seals.
  • the hydropneumatic pressure intensifier according to the invention with the characteristic features of the main claim points to compared to the advantage that in the ventilation ring grooves
  • the lowest pressure prevails, for example atmospheric pressure, so that the radial seal towards the control room passing air volumes can be derived.
  • A is used for ventilation Bore in the working cylinder, which is independent of the working stroke of the Accumulator piston with the lateral surface ring groove always in overlap stands. Both in the starting position and in the end position - possibly with only small remaining amounts in the storage space - is for a complete relief is provided, the vent hole can lead directly to the atmosphere.
  • a radial bore can in be carried out simply as a cross hole, beginning and end of this radial bore in each case in the annular groove lateral surfaces ends and therefore no frictional contact with the working cylinder or the plunger.
  • a Auxiliary piston connected to the working piston for rapid traverse alternately can be acted upon pneumatically on both sides.
  • Pressure intensifier is a working piston 2 axially in a housing 1 slidably and radially sealed and limited with it a hydraulic oil-filled working space 3.
  • a piston rod 4 projecting outside the housing arranged.
  • the working piston 2 has a collar Auxiliary piston 5, which is radially sealed to a casing tube 6 and thereby separates two pneumatic spaces 7 and 8 from each other for the rapid traverse of working piston 2 alternating with pneumatic Pressure are supplied.
  • a storage space 9 for hydraulic oil Above the work area 3 and hydraulically connected to it is a storage space 9 for hydraulic oil, the storage pressure by a storage piston and pneumatic pressure in one Control room 12 is generated.
  • the storage piston 11 is in one Storage space 9 and the control room 12, delimiting Jacket tube 13 guided radially sealing and axially displaceable, in Art a free piston.
  • the casing tube 13 is on the one hand by a Housing part 14 of the housing 1 and on the other hand by a Partition 15 closed, being on housing part 14 and partition 15 corresponding twists for pushing on the casing tube 13 are present, with additional static seals 16.
  • the partition 15 is used for the side facing away from the control chamber 12 Limitation of a pneumatic space 17, which is by a casing tube 18th is surrounded and in which the drive piston 19 of a plunger 21st is stored, which counter to the hydraulic pressure in the Work space 3 is movable.
  • the plunger 21 penetrates the partition 15 in a radially sealed manner and the storage piston 11 and dips with its free end in the Storage space 9.
  • the drive piston 19 with plunger 21 is driven by compressed air, which in a drive room 22 above of the drive piston 21 is passed, whereby the High pressure operation is initiated.
  • the plunger dives 21, after a certain stroke in one of Storage space 9 connecting bore 23 leading to work space 3, this connection with the participation of a radial seal 24 is interrupted.
  • This pressure corresponds to that Transmission ratio of the working surfaces of drive pistons 19 to Plunger piston 21, starting from the drive piston 19 pressurized pneumatic pressure.
  • the resulting high hydraulic pressure acts directly on the working piston 2 and causes the desired high force on the piston rod 4.
  • the various pneumatic rooms are through to the outside of the Hydropneumatic pressure intensifier leading connection channels equipped, namely the pneumatic room 7 through the channel 25, the Pneumatic room 8 through the channel 26, the control room 12 through the Channel 27, the pneumatic room 17 through the channel 28 and the Drive space 22 through the channel 29.
  • the working stroke is in the pneumatic control line 31 Pressure reduced and passed into a pneumatic control line 32, which connects the connecting channels 25, 27 and 29 to each other, wherein the connection channel 29 is a pressure-controlled valve 33 is connected upstream.
  • the supplied pneumatic pressure is the first the connecting channels 25 and 27 and thus the pneumatic space 7 and supplied to the control chamber 12, after which the auxiliary piston 5 with Piston 2 is pushed down in rapid and the Accumulator piston 11 corresponding to that from the storage space 9 in the Working space 3 overflowing hydraulic quantity is replenished.
  • the hydraulic volume in work space 3 and storage space 9 is overall constant, except for leakage amounts that occur every now and then need to be refilled.
  • Control line 32 and the pressure-controlled valve 33 gives the Inflow to the connecting duct 29 and thus to the drive chamber 22 free, so that the drive piston 19 with plunger 21 down is moved with the effect described above.
  • the accumulator piston 11 is between the one filled with oil Storage space 9 and, according to the control mentioned above, with air different pressure-filled control chamber 12, wherein especially to prevent oil from the storage space 9 in the control room 12 and vice versa air into the storage room 9 arrives.
  • an absolute air-oil separation is used for this on the storage piston 11, in which it is on the one hand both to the casing tube 13 as well as plunger 21 with annular grooves 34 and 35 Has radial seals 36 and 37.
  • the radial seals 37 for Plunger 21 is once as a round cord seal and once as Cuff seal shown shown shown.
  • annular groove 38 which is arranged in a Casing tube 13 arranged vent hole 39 to the outside the unit is vented.
  • the vent hole 39 is related on the annular groove 38, or the maximum possible stroke of the Storage piston 11 arranged so that they are always in overlap with the annular groove 38 remains.
  • annular groove 42 is provided by a continuous Radial bore 43 with the always vented annular groove 38 on the Shell surface of the storage piston 11 is connected.

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  • 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-Pressure Circuits (AREA)
  • Fluid-Damping Devices (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)

Abstract

Hydropneumatic pressure intensifier with a storage piston (11) which is secured in position between storage oil and compressed air and through which in addition a plunger piston (21) passes centrally, annular relief grooves (38 and 42) being provided for the oil/air separation on the circumferential surface as well as in the wall of the central bore (41). The annular relief grooves (38 and 42) are connected to one another and are pressure-relieved via a vent bore (39) leading to the outside. <IMAGE>

Description

Die Erfindung geht aus von einem hydropneumatischen Druckübersetzer nach der Gattung des Hauptanspruchs. Ein Hauptproblem bei derartigen hydropneumatischen Druckübersetzern besteht in der Abdichtung zwischen Speicherraum und Steuerraum, da die hydraulischen Drücke im Speicherraum und die pneumatischen Drücke im Steuerraum während eines Arbeitszyklus sich laufend verändern, und zwar nicht unbedingt synchron verändern, wobei einerseits die Gefahr besteht, daß Öl aus dem Speicherraum in den Steuerraum gelangt und dadurch Leckverluste entstehen, die das Arbeitsvermögen des hydropneumatischen Druckübersetzer beeinträchtigen können, oder es besteht die Gefahr, daß Luft aus dem Steuerraum in den Speicherraum gelangt, wo es vom Öl aufgenommen wird mit dem Nachteil, daß es in den Arbeitsraum gelangt und dort bei der Hochdruckphase des Druckhubs zu einer verstärkten Kompressibilität neigt mit all den sich daraus ergebenden Nachteilen für die Arbeitsfähigkeit des Aggregats.The invention is based on a hydropneumatic Pressure translator according to the type of the main claim. On Main problem with such hydropneumatic pressure intensifiers consists in the sealing between the storage room and the control room, because the hydraulic pressures in the storage space and the pneumatic ones Press continuously in the control room during a work cycle change, and not necessarily change synchronously, whereby on the one hand there is a risk that oil from the storage space in the Control room arrives and this causes leakage losses that the Working capacity of the hydropneumatic pressure intensifier can affect, or there is a risk that air from the Control room enters the storage room where it is absorbed by the oil with the disadvantage that it gets into the work area and there the high pressure phase of the pressure stroke to an intensified Compressibility tends with all of the resulting disadvantages for the working ability of the unit.

Bei einem bekannten gattungsgemäßen hydropneumatischen Druckübersetzer (DE-OS 2810 894) sind aus diesem Grunde sowohl zur Wand des Arbeitszylinders hin, als auch zur Mantelfläche des Tauchkolbens zwei Radialdichtungen vorgesehen mit dem Zweck eine optimale Luft-Öl-Trennung zu erzielen. Problematisch ist hier insbesondere, daß die Neigung der Luft vom Steuerraum in den Speicherraum zu gelangen nicht etwa in der Niederdruckphase vorhanden ist, sondern vielmehr in der Hochdruckphase, wobei auch geringe Luftmengen als Wandlaminate bei der axialen Bewegung des Speicherkolbens an den Radialdichtungen "vorbeigepumpt" werden. In a known generic hydropneumatic For this reason, pressure translators (DE-OS 2810 894) are both to the wall of the working cylinder, as well as to the outer surface of the Plunger two radial seals provided with the purpose one to achieve optimal air-oil separation. Is problematic here in particular, that the inclination of the air from the control room in the Storage space does not come about in the low pressure phase is present, but rather in the high pressure phase, whereby also small amounts of air as wall laminates during the axial movement of the Storage piston are "pumped past" the radial seals.

Der erfindungsgemäße hydropneumatische Druckübersetzer mit den kennzeichnenden Merkmalen des Hauptanspruchs weist dem gegenüber den Vorteil auf, daß in den Entlüftungsringnuten Niederstdruck herrscht, beispielsweise atmosphärischer Druck, so daß sich jegliche die zum Steuerraum hin vorhandene Radialdichtung passierende Luftmengen abgeleitet werden können. Sollten in die Entlüftungsringnuten Ölmengen vom Speicherraum her gelangen, so ist dieses zumindest für den jeweiligen Arbeitsvorgang nicht nachteilig, sondern es muß lediglich bei erheblichem Ölverlust Öl in den Speicherraum nachgefüllt werden. Dabei dient zur Entlüftung eine Bohrung im Arbeitszylinder, die unabhängig vom Arbeitshub des Speicherkolbens mit der Mantelflächenringnut stets in Überdeckung steht. Sowohl in der Ausgangslage als auch in der Endlage - möglicherweise bei nur geringen Restmengen im Speicherraum - ist für eine vollständige Entlastung gesorgt, wobei die Entlüftungsbohrung direkt zur Atmosphäre hin führen kann.The hydropneumatic pressure intensifier according to the invention with the characteristic features of the main claim points to compared to the advantage that in the ventilation ring grooves The lowest pressure prevails, for example atmospheric pressure, so that the radial seal towards the control room passing air volumes can be derived. Should in the Vent ring grooves get oil quantities from the storage space, see above is this not disadvantageous at least for the respective work process, it only needs oil in the case of significant oil loss Storage space can be refilled. A is used for ventilation Bore in the working cylinder, which is independent of the working stroke of the Accumulator piston with the lateral surface ring groove always in overlap stands. Both in the starting position and in the end position - possibly with only small remaining amounts in the storage space - is for a complete relief is provided, the vent hole can lead directly to the atmosphere.

Nach einer vorteilhaften Ausgestaltung der Erfindung ist die in der Bohrungswand vorhandene Entlastungsringnut mit jener auf der Mantelfläche durch mindestens eine Radialbohrung des Speicherkolbens verbunden. Eine solche Radialbohrung kann in einfacher Weise als Querbohrung durchgeführt werden, wobei Anfang und Ende dieser Radialbohrung jeweils in den Ringnutmantelflächen endet und damit keine Reibberührung mit dem Arbeitszylinder bzw. dem Tauchkolben aufweist.According to an advantageous embodiment of the invention Bore wall existing relief ring groove with that on the Lateral surface through at least one radial bore of the Accumulator piston connected. Such a radial bore can in be carried out simply as a cross hole, beginning and end of this radial bore in each case in the annular groove lateral surfaces ends and therefore no frictional contact with the working cylinder or the plunger.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung sind beiderseits der Entlüftungsringnuten zusätzlich an sich bekannte Dichtungsringnuten zur Aufnahme von Radialdichtungen vorhanden.According to a further advantageous embodiment of the invention known on both sides of the ventilation ring grooves Sealing ring grooves are available to accommodate radial seals.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung sind in der Trennwand radial nach außen führende Anschlusskanäle für Druckluft vorhanden.According to a further advantageous embodiment of the invention, in the dividing wall radially leading connection channels for Compressed air available.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist der auf dem Steuerraum abgewandten Seite der Trennwand vorhandene Raum luftdruckgesteuert, für die Rückstellung eines mit dem Tauchkolben verbundenen Antriebskolbens.According to a further advantageous embodiment of the invention existing on the side of the partition facing away from the control room Room controlled by air pressure, for resetting one with the Plunger connected drive piston.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist ein Hilfskolben mit dem Arbeitskolben verbunden, der für einen Eilgang beiderseits abwechselnd pneumatisch beaufschlagbar ist.According to a further advantageous embodiment of the invention, a Auxiliary piston connected to the working piston for rapid traverse alternately can be acted upon pneumatically on both sides.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention are the following description, the drawing and the claims removable.

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und wird im Folgenden näher beschrieben.An embodiment of the object of the invention is in the Drawing shown and is described in more detail below.

Es zeigen:

Fig. 1
einen hydropneumatischen Druckübersetzer im Längsschnitt und
Fig. 2
einen Ausschnitt aus Fig. 1 im vergrößerten Maßstab.
Show it:
Fig. 1
a hydropneumatic pressure intensifier in longitudinal section and
Fig. 2
a section of Fig. 1 on an enlarged scale.

Bei dem in den Figuren 1 und 2 dargestellten hydropneumatischen Druckübersetzer ist in einem Gehäuse 1 ein Arbeitskolben 2 axial verschiebbar und radial dichtend angeordnet und begrenzt mit ihm einen hydraulikölgefüllten Arbeitsraum 3. An dem Arbeitskolben 2 ist eine nach außerhalb des Gehäuses ragende Kolbenstange 4 angeordnet. Außerdem weist der Arbeitskolben 2 als Bund einen Hilfskolben 5 auf, der zu einem Mantelrohr 6 hin radial abgedichtet ist und dadurch zwei Pneumatikräume 7 und 8 voneinander trennt, die für den Eilgang des Arbeitskolbens 2 abwechselnd mit pneumatischem Druck versorgt werden. Sobald ein ausreichender Arbeitsdruck im Pneumatikraum 7 herrscht, wird der Arbeitskolben 2 nach unten geschoben und umgekehrt, bei entsprechend hohem Druck im Pneumatikraum 8 und abgebautem Druck im Pneumatikraum 7, wird der Arbeitskolben 2 wieder in die dargestellte Ausgangslage verschoben.In the hydropneumatic shown in Figures 1 and 2 Pressure intensifier is a working piston 2 axially in a housing 1 slidably and radially sealed and limited with it a hydraulic oil-filled working space 3. On the working piston 2 a piston rod 4 projecting outside the housing arranged. In addition, the working piston 2 has a collar Auxiliary piston 5, which is radially sealed to a casing tube 6 and thereby separates two pneumatic spaces 7 and 8 from each other for the rapid traverse of working piston 2 alternating with pneumatic Pressure are supplied. As soon as there is sufficient working pressure in the Pneumatic chamber 7 prevails, the working piston 2 is down pushed and vice versa, at a correspondingly high pressure in the Pneumatic space 8 and pressure in the pneumatic space 7, is the working piston 2 back to the starting position shown postponed.

Oberhalb des Arbeitsraums 3 und mit diesem hydraulisch verbunden ist ein Speicherraum 9 für Hydrauliköl, dessen Speicherdruck durch einen Speicherkolben und den pneumatischen Druck in einem Steuerraum 12 erzeugt wird. Der Speicherkolben 11 ist in einem, den Speicherraum 9 als auch den Steuerraum 12, begrenzenden Mantelrohr 13 radial dichtend und axial verschiebbar geführt, in Art eines Freikolbens. Das Mantelrohr 13 ist einerseits durch einen Gehäuseteil 14 des Gehäuses 1 und andererseits durch eine Trennwand 15 verschlossen, wobei auf Gehäuseteil 14 und Trennwand 15 entsprechende Abdrehungen zur Aufschiebung des Mantelrohres 13 vorhanden sind, mit zusätzlichen statischen Dichtungen 16. Auf der dem Steuerraum 12 abgewandten Seite dient die Trennwand 15 zur Begrenzung eines Pneumatikraums 17, der durch ein Mantelrohr 18 umgeben ist und in dem der Antriebskolben 19 eines Tauchkolbens 21 gelagert ist, welcher entgegen dem hydraulischen Druck im Arbeitsraum 3 verschiebbar ist.Above the work area 3 and hydraulically connected to it is a storage space 9 for hydraulic oil, the storage pressure by a storage piston and pneumatic pressure in one Control room 12 is generated. The storage piston 11 is in one Storage space 9 and the control room 12, delimiting Jacket tube 13 guided radially sealing and axially displaceable, in Art a free piston. The casing tube 13 is on the one hand by a Housing part 14 of the housing 1 and on the other hand by a Partition 15 closed, being on housing part 14 and partition 15 corresponding twists for pushing on the casing tube 13 are present, with additional static seals 16. On the The partition 15 is used for the side facing away from the control chamber 12 Limitation of a pneumatic space 17, which is by a casing tube 18th is surrounded and in which the drive piston 19 of a plunger 21st is stored, which counter to the hydraulic pressure in the Work space 3 is movable.

Der Tauchkolben 21 durchdringt radial abgedichtet die Trennwand 15 und den Speicherkolben 11 und taucht mit seinem freien Ende in den Speicherraum 9. Der Antriebskolben 19 mit Tauchkolben 21 wird durch Druckluft angetrieben, die in einen Antriebsraum 22 oberhalb des Antriebskolbens 21 geleitet wird, wodurch der Hochdruckarbeitsgang eingeleitet wird. Hierbei taucht der Tauchkolben 21, nach Zurücklegung eines bestimmten Hubes in eine vom Speicherraum 9 zum Arbeitsraum 3 führende Verbindungsbohrung 23, wobei diese Verbindung unter Mitwirkung einer Radialdichtung 24 unterbrochen wird. Bei weiterem Hub des Tauchkolbens 21 und entsprechend tieferem Eintauchen in den Arbeitsraum 3, wird dort dadurch Hydraulikflüssigkeit verdrängt, so daß aufgrund des relativ kleinen Tauchkolbendurchmessers ein hoher Arbeitsdruck im Arbeitsraum 3 erzeugt wird. Dieser Druck entspricht dem Übersetzungsverhältnis der Arbeitsflächen von Antriebskolben 19 zu Tauchkolben 21, ausgehend vom dem den Antriebskolben 19 beaufschlagenden pneumatischen Druck. Der dabei entstehende hohe hydraulische Druck wirkt unmittelbar auf den Arbeitskolben 2 und bewirkt die gewünschte hohe Kraft an der Kolbenstange 4.The plunger 21 penetrates the partition 15 in a radially sealed manner and the storage piston 11 and dips with its free end in the Storage space 9. The drive piston 19 with plunger 21 is driven by compressed air, which in a drive room 22 above of the drive piston 21 is passed, whereby the High pressure operation is initiated. Here the plunger dives 21, after a certain stroke in one of Storage space 9 connecting bore 23 leading to work space 3, this connection with the participation of a radial seal 24 is interrupted. With a further stroke of the plunger 21 and correspondingly deeper immersion in the work area 3, there thereby displacing hydraulic fluid, so that due to the relative small plunger diameter a high working pressure in Work space 3 is generated. This pressure corresponds to that Transmission ratio of the working surfaces of drive pistons 19 to Plunger piston 21, starting from the drive piston 19 pressurized pneumatic pressure. The resulting high hydraulic pressure acts directly on the working piston 2 and causes the desired high force on the piston rod 4.

Für den Rückhub des Tauchkolbens 21 wird der pneumatische Druck im Antriebsraum 22 abgebaut und ein entsprechender pneumatischer Druck im Pneumatikraum 17 aufgebaut, so daß der Antriebskolben 19 mit dem Tauchkolben 21 in die gezeigte Ausgangslage zurückgeschoben wird, wonach aus dem Arbeitsraum 3, durch den Arbeitskolben 2 verdrängt, Hydraulikflüssigkeit in den Speicherraum 9 strömt und wobei der Arbeitskolben 2, angetrieben durch den Hilfskolben 5 und Druckluft im Pneumatikraum 8 in die ebenfalls gezeigte Ausgangslage verschoben wird.For the return stroke of the plunger 21, the pneumatic pressure dismantled in the drive room 22 and a corresponding pneumatic Pressure built up in the pneumatic chamber 17 so that the drive piston 19th with the plunger 21 in the starting position shown is pushed back, after which from the work room 3, through the Piston 2 displaces hydraulic fluid into the storage space 9 flows and wherein the working piston 2, driven by the Auxiliary piston 5 and compressed air in the pneumatic chamber 8 in the likewise shown starting position is shifted.

Die verschiedenen Pneumatikräume sind durch, nach außerhalb des hydropneumatischen Druckübersetzers führende Anschlußkanäle ausgestattet, nämlich der Pneumatikraum 7 durch den Kanal 25, der Pneumatikraum 8 durch den Kanal 26, der Steuerraum 12 durch den Kanal 27, der Pneumatikraum 17 durch den Kanal 28 und der Antriebsraum 22 durch den Kanal 29. Nach einer beispielhaften Ansteuerungsart sind die Anschlußkanäle 26 und 28 für die Pneumatikräume 8 und 17 über eine pneumatische Steuerleitung 31 miteinander verbunden, so daß, wenn über diese der pneumatische Steuerdruck zugeleitet wird, der Hilfskolben 5 und der Antriebskolben 19 in die dargestellte Ausgangslage geschoben werden. Für den Arbeitshub hingegen wird in der pneumatischen Steuerleitung 31 der Druck abgebaut und in eine pneumatische Steuerleitung 32 geleitet, die die Anschlußkanäle 25, 27 und 29 miteinander verbindet, wobei dem Anschlußkanal 29 ein druckabhängig gesteuertes Ventil 33 vorgeschaltet ist. Der zugeführte Pneumatikdruck wird somit zuerst den Anschlußkanälen 25 und 27 und damit dem Pneumatikraum 7 und dem Steuerraum 12 zugeführt, wonach der Hilfskolben 5 mit Arbeitskolben 2 im Eilgang nach unten geschoben wird und der Speicherkolben 11 entsprechend dem aus dem Speicherraum 9 in den Arbeitsraum 3 überfließenden Hydraulikmenge nachgeschoben wird. Das Hydraulikvolumen in Arbeitsraum 3 und Speicherraum 9 ist insgesamt konstant, abgesehen von Leckmengen, die hin und wieder nachgefüllt werden müssen. Sobald die Kolbenstange 4 auf Widerstand stößt (Ende des Eilganges) erhöht sich der Druck in der pneumatischen Steuerleitung 32 und das druckabhängig gesteuerte Ventil 33 gibt den Zustrom zum Anschlußkanal 29 und damit zum Antriebsraum 22 frei, so daß der Antriebskolben 19 mit Tauchkolben 21 nach unten verschoben wird mit der weiter oben beschriebenen Wirkung.The various pneumatic rooms are through to the outside of the Hydropneumatic pressure intensifier leading connection channels equipped, namely the pneumatic room 7 through the channel 25, the Pneumatic room 8 through the channel 26, the control room 12 through the Channel 27, the pneumatic room 17 through the channel 28 and the Drive space 22 through the channel 29. According to an exemplary Type of control are the connecting channels 26 and 28 for the Pneumatic rooms 8 and 17 via a pneumatic control line 31 connected to each other so that when the pneumatic Control pressure is supplied, the auxiliary piston 5 and the drive piston 19 are pushed into the starting position shown. For the In contrast, the working stroke is in the pneumatic control line 31 Pressure reduced and passed into a pneumatic control line 32, which connects the connecting channels 25, 27 and 29 to each other, wherein the connection channel 29 is a pressure-controlled valve 33 is connected upstream. The supplied pneumatic pressure is the first the connecting channels 25 and 27 and thus the pneumatic space 7 and supplied to the control chamber 12, after which the auxiliary piston 5 with Piston 2 is pushed down in rapid and the Accumulator piston 11 corresponding to that from the storage space 9 in the Working space 3 overflowing hydraulic quantity is replenished. The hydraulic volume in work space 3 and storage space 9 is overall constant, except for leakage amounts that occur every now and then need to be refilled. As soon as the piston rod 4 is on resistance bumps (end of rapid traverse) the pressure in the pneumatic increases Control line 32 and the pressure-controlled valve 33 gives the Inflow to the connecting duct 29 and thus to the drive chamber 22 free, so that the drive piston 19 with plunger 21 down is moved with the effect described above.

Der Speicherkolben 11 ist, zwischen dem mit Öl gefüllten Speicherraum 9 und dem, gemäß oben genannter Steuerung, mit Luft unterschiedlichen Drucks gefülltem Steuerraum 12 angeordnet, wobei vor allem verhindert werden soll, daß Öl aus dem Speicherraum 9 in den Steuerraum 12 und umgekehrt Luft in den Speicherraum 9 gelangt. Erfindungsgemäß dient hierfür eine absolute Luft-Öl-Trennung am Speicherkolben 11, in dem er einerseits sowohl zum Mantelrohr 13, als auch zum Tauchkolben 21 hin Ringnuten 34 und 35 mit Radialdichtungen 36 und 37 aufweist. Die Radialdichtungen 37 zum Tauchkolben 21 hin ist einmal als Rundschnurdichtung und einmal als Manschettendichtung ausgebildet dargestellt. Um in dem Bereich zwischen den Radialdichtungen einen absoluten Druckabbau und dadurch die Luft-Öl-Trennung zu erhalten ist auf der Mantelfläche des Speicherkolbens 11 eine Ringnut 38 angeordnet, die über eine im Mantelrohr 13 angeordnete Entlüftungsbohrung 39 nach außerhalb des Aggregates entlüftet ist. Die Entlüftungsbohrung 39 ist in Bezug auf die Ringnut 38, bzw. den maximal möglichen Hub des Speicherkolbens 11 so angeordnet, daß sie stets in Überdeckung mit der Ringnut 38 bleibt. Als weiteres ist in der zentralen Bohrung 41 des Speicherkolbens 11, welche vom Tauchkolben 21 durchdrungen ist, eine Ringnut 42 vorgesehen, die durch eine durchgehende Radialbohrung 43 mit der stets entlüfteten Ringnut 38 auf der Mantelfläche des Speicherkolbens 11 verbunden ist.The accumulator piston 11 is between the one filled with oil Storage space 9 and, according to the control mentioned above, with air different pressure-filled control chamber 12, wherein especially to prevent oil from the storage space 9 in the control room 12 and vice versa air into the storage room 9 arrives. According to the invention, an absolute air-oil separation is used for this on the storage piston 11, in which it is on the one hand both to the casing tube 13 as well as plunger 21 with annular grooves 34 and 35 Has radial seals 36 and 37. The radial seals 37 for Plunger 21 is once as a round cord seal and once as Cuff seal shown shown. To in the area absolute pressure reduction between the radial seals and thereby maintaining the air-oil separation is on the lateral surface of the Storage piston 11 an annular groove 38 which is arranged in a Casing tube 13 arranged vent hole 39 to the outside the unit is vented. The vent hole 39 is related on the annular groove 38, or the maximum possible stroke of the Storage piston 11 arranged so that they are always in overlap with the annular groove 38 remains. Another is in the central bore 41 of the Accumulator piston 11, which is penetrated by plunger 21, an annular groove 42 is provided by a continuous Radial bore 43 with the always vented annular groove 38 on the Shell surface of the storage piston 11 is connected.

Alle in der Beschreibung, den nachfolgenden Ansprüchen und der Zeichnung dargestellten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein. All in the description, the following claims and the Features shown in the drawing can be used both individually and in any combination with each other be essential to the invention.

BezugszahlenlisteLIST OF REFERENCE NUMBERS

11
Gehäusecasing
22
Arbeitskolbenworking piston
33
Arbeitsraumworking space
44
Kolbenstangepiston rod
55
Hilfskolbenauxiliary piston
66
Mantelrohrcasing pipe
77
Pneumatikraumpneumatic space
88th
Pneumatikraumpneumatic space
99
Speicherraumstorage space
1010
--
1111
Speicherkolbenaccumulator piston
1212
Steuerraumcontrol room
1313
Mantelrohrcasing pipe
1414
Gehäuseteilhousing part
1515
Trennwandpartition wall
1616
Statische DichtungStatic seal
1717
Pneumatikraumpneumatic space
1818
Mantelrohrcasing pipe
1919
Antriebskolbendrive piston
2020
--
2121
Tauchkolbenplunger
2222
Antriebsraumdrive space
2323
Verbindungsbohrungconnecting bore
2424
Radialdichtungradial seal
2525
Anschlußkanalconnecting channel
2626
Anschlußkanalconnecting channel
2727
Anschlußkanalconnecting channel
2828
Anschlußkanalconnecting channel
2929
Anschlußkanalconnecting channel
3030
--
3131
Pneumatische
Steuerleitungpneumatic
control line
3232
Pneumatische
Steuerleitungpneumatic
control line
3333
Druckabhängig
gesteuertes
Ventilpressure dependent
controlled
Valve
3434
Ringnutring groove
3535
Ringnutring groove
3636
Radialdichtungradial seal
3737
Radialdichtungradial seal
3838
Ringnutring groove
3939
Entlüftungsbohrungvent hole
4040
--
4141
Zentrale BohrungCentral drilling
4242
Ringnutring groove
4343
Radialbohrungradial bore

Claims (6)

  1. Hydropneumatic pressure intensifier
    having an operating chamber (3) for varying pressures, namely a lower storage pressure and a high operating pressure, arranged in a subassembly housing,
    having an operating piston (2) limiting the operating chamber (3) on the front side and whose operating stroke can be actuated by means of the operating pressure in the subassembly housing (1) and which is led to the exterior by a piston rod (4),
    having an accumulator chamber (9) arranged in a tubular jacket (13) and hydraulically combinable with the operating chamber (3) and from which hydraulic oil under storage pressure flows into the operating chamber (3) during a fast motion of the operating stroke and flows back again on the return stroke,
    having a plunger piston (21) which can be actuated pneumatically or hydraulically as a high-pressure generator and which plunges into the operating chamber (3) after the rapid motion of the operating piston (2),
    having a storage piston (11) limiting the accumulator chamber (9) and axially movable in the tubular jacket (13) and which is penetrated by the plunger piston (21),
    with in each case two seals (36, 37) existing in the stroke direction at a distance from the storage piston and acting on both the plunger piston (21) and the tubular jacket (13), namely radial seals (36) arranged in two ring grooves (34) on the jacket surface of the storage piston (11) and acting on the tubular jacket (13) and two radial seals (36) acting on the plunger piston (21) and arranged in two ring grooves (35) in the wall of the inner bore (41) penetrated by the plunger piston,
    having a control chamber (12) existing on the side of the plunger piston (11) facing away from the accumulator chamber (9) and which may be charged with air of differing pressures, and
    having a partition (15) limited the control chamber (12) and firmly joined to the tubular jacket (13) and penetrated by the plunger piston (21),
    having an outer ring groove (38) on the jacket surface of the storage piston (11) in the stroke direction between the seals (36) and open to the tubular jacket (13), and
    having an inner ring groove (42) in the wall of the inner bore (41) of the plunger piston (11) and likewise arranged between the seals (37),
    characterised in that
    a vent bore (39) which always overlaps the outer ring groove (38) is arranged in the tubular jacket (13) to relieve the pressure of the outer ring groove (38), and
    the vent bore (39) leads to the atmosphere.
  2. Hydropneumatic pressure intensifier according to claim 1, characterised in that the outer ring groove (38) is connected to the inner ring groove (42) by means of a radial bore (43) in the storage piston (11).
  3. Hydropneumatic pressure intensifier according to one of the previous claims 1 or 2, characterised in that separate sealing ring grooves (34, 35) are provided on both sides of the outer ring groove (38) and inner ring groove (42) for the accommodation of radial seals (36, 37).
  4. Hydropneumatic pressure intensifier according to one of the previous claims, characterised in that connecting ducts (27, 28) for compressed air radially leading to the exterior are provided in the partition (15).
  5. Hydropneumatic pressure intensifier according to one of the previous claims, characterised in that the chamber (17) existing on the side of the partition (15) facing away from the control chamber (12) is controlled by compressed air for the return of a drive piston (19) connected to the plunger piston (21).
  6. Hydropneumatic pressure intensifier according to one of the previous claims, characterised in that an auxiliary piston (5) is connected to the operating piston (2) which can be pneumatically charged alternately on both sides for a fast motion.
EP93110428A 1992-07-02 1993-06-30 Hydropneumatic pressure intensifier Expired - Lifetime EP0579037B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4223411 1992-07-02
DE4223411A DE4223411A1 (en) 1992-07-02 1992-07-02 Hydropneumatic pressure intensifier

Publications (3)

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EP0579037A1 EP0579037A1 (en) 1994-01-19
EP0579037B1 EP0579037B1 (en) 1997-09-24
EP0579037B2 true EP0579037B2 (en) 2003-01-22

Family

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EP93110428A Expired - Lifetime EP0579037B2 (en) 1992-07-02 1993-06-30 Hydropneumatic pressure intensifier

Country Status (5)

Country Link
US (1) US5377488A (en)
EP (1) EP0579037B2 (en)
JP (1) JPH06159303A (en)
AT (1) ATE158642T1 (en)
DE (2) DE4223411A1 (en)

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KR100380121B1 (en) * 2000-03-15 2003-04-14 주재석 Hydraulic Pressure Booster Cylinder
JP2004503702A (en) 2000-03-27 2004-02-05 トックス・プレッソテヒニック・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング・ウント・コンパニー・コマンディトゲゼルシャフト Hydraulic intensifier
DE10255230A1 (en) * 2002-11-26 2004-06-09 Uhde High Pressure Technologies Gmbh High-pressure device and method for hydraulic-pneumatic power stroke for clean room applications
US8261547B2 (en) * 2006-07-31 2012-09-11 Norgren Gmbh Pneumatic actuator
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DE102007036844B4 (en) * 2007-08-06 2021-05-06 Tox Pressotechnik Gmbh & Co. Kg Method for operating a hydropneumatic device for pressure intensification
KR100917070B1 (en) * 2007-09-03 2009-09-15 윤택수 The intensifying device with booster
DE102007044907A1 (en) * 2007-09-19 2009-04-02 Tox Pressotechnik Gmbh & Co. Kg Method for operating hydro-pneumatic device for pressure transmission, involves displacing hydraulic fluid from storage chamber, and draining hydraulic fluid volume in storage chamber below ventilation opening into storage chamber
DE102012008902A1 (en) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatic device for pressure transmission and riveting device
US9394928B2 (en) 2012-07-31 2016-07-19 Caterpillar Inc. Dynamic seal wear mitigation system
US9651067B2 (en) * 2012-07-31 2017-05-16 Caterpillar Inc. Hydraulic system with a dynamic seal
CN102913509A (en) * 2012-11-23 2013-02-06 湖北汽车工业学院 Electrohydraulic pressurizing cylinder and pressing machine equipment with same
CN104279194A (en) * 2013-07-09 2015-01-14 北京精密机电控制设备研究所 Fuel gas extrusion type oil tank
CN107288942B (en) * 2016-03-31 2019-01-08 中核新能核工业工程有限责任公司 Using compressed air as the small flow UF6 gas pressurized device of power
US10982690B2 (en) * 2017-03-15 2021-04-20 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
US10941790B2 (en) * 2017-03-15 2021-03-09 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece
JP6999439B2 (en) * 2017-03-15 2022-01-18 セイコーインスツル株式会社 Cylinder device, press device, work clamp device, cylinder device operation method, work clamping method, and work press method

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Also Published As

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EP0579037A1 (en) 1994-01-19
DE59307411D1 (en) 1997-10-30
JPH06159303A (en) 1994-06-07
ATE158642T1 (en) 1997-10-15
US5377488A (en) 1995-01-03
EP0579037B1 (en) 1997-09-24
DE4223411A1 (en) 1994-01-05

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