EP0579037A1 - Hydropneumatic pressure intensifier - Google Patents

Hydropneumatic pressure intensifier Download PDF

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Publication number
EP0579037A1
EP0579037A1 EP93110428A EP93110428A EP0579037A1 EP 0579037 A1 EP0579037 A1 EP 0579037A1 EP 93110428 A EP93110428 A EP 93110428A EP 93110428 A EP93110428 A EP 93110428A EP 0579037 A1 EP0579037 A1 EP 0579037A1
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EP
European Patent Office
Prior art keywords
piston
pressure
working
plunger
space
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EP93110428A
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German (de)
French (fr)
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EP0579037B1 (en
EP0579037B2 (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 intensifier according to the preamble of the main claim.
  • a main problem with such hydropneumatic pressure boosters is the sealing between the storage space and the control space, since the hydraulic pressures in the storage space and the pneumatic pressures in the control space change continuously during a work cycle, and do not necessarily change synchronously, with the risk that oil will leak out the storage space enters the control room and this causes leakage losses, which can affect the working capacity of the hydropneumatic pressure intensifier, or there is a risk that air from the control room gets into the storage space, where it is absorbed by the oil with the disadvantage that it enters the Workspace arrives and there tends to be more compressible during the high pressure phase of the pressure stroke with all the resulting disadvantages for the ability of the unit to work.
  • the hydropneumatic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage over the fact that there is a low pressure in the ventilation ring grooves, for example atmospheric pressure, so that any air volume passing to the control chamber can be derived. Should oil quantities get into the ventilation ring grooves from the storage space, this is not disadvantageous, at least for the respective work process, but it is only necessary to add oil to the storage space if there is a considerable loss of oil.
  • a bore in the working cylinder is used for ventilation, which is always in overlap with the circumferential surface groove regardless of the working stroke of the storage piston. Both in the starting position and in the end position - possibly with only a small amount remaining in the storage space - is completely relieved, whereby the vent hole can lead directly to the atmosphere.
  • the relief ring groove in the bore wall is connected to that on the lateral surface by at least one radial bore of the storage piston.
  • a radial bore can be carried out in a simple manner as a transverse bore, the beginning and end of this radial bore each ending in the annular groove surface and thus having no frictional contact with the working cylinder or the plunger.
  • a working piston 2 is arranged axially displaceably and radially sealingly in a housing 1 and delimits a working space 3 filled with hydraulic oil with it.
  • a piston rod 4 projecting outside the housing is arranged on the working piston 2.
  • the working piston 2 as a collar has an auxiliary piston 5, which is radially sealed off from a casing tube 6 and thereby separates two pneumatic spaces 7 and 8, which are alternately supplied with pneumatic pressure for the rapid traverse of the working piston 2.
  • the working piston 2 As soon as there is sufficient working pressure in the pneumatic space 7, the working piston 2 is pushed down and vice versa, with a correspondingly high pressure in the pneumatic space 8 and a reduced pressure in the pneumatic space 7, the working piston 2 is moved back into the starting position shown.
  • a storage space 9 for hydraulic oil for hydraulic oil, the storage pressure of which is generated by a storage piston and the pneumatic pressure in a control space 12.
  • the accumulator piston 11 is guided in a jacket tube 13, which delimits the accumulator chamber 9 and the control chamber 12, in a radially sealing and axially displaceable manner, in the manner of a free piston.
  • the casing tube 13 is closed on the one hand by a housing part 14 of the housing 1 and on the other hand by a partition wall 15, with corresponding twists on the housing part 14 and partition wall 15 for pushing on the casing tube 13, with additional static seals 16.
  • the partition 15 serves to delimit a pneumatic space 17 which is surrounded by a casing tube 18 and in which the drive piston 19 of a plunger 21 is mounted, which can be displaced in the working space 3 against the hydraulic pressure.
  • the plunger 21 penetrates the partition 15 and the storage piston 11 in a radially sealed manner and dips with its free end into the storage space 9.
  • the drive piston 19 with the plunger 21 is driven by compressed air which is conducted into a drive space 22 above the drive piston 21, as a result of which the high-pressure operation is initiated.
  • the plunger 21, after covering a certain stroke dips into a connecting bore 23 leading from the storage space 9 to the working space 3, this connection being interrupted with the participation of a radial seal 24.
  • hydraulic fluid With a further stroke of the plunger 21 and a correspondingly deeper immersion in the working space 3, hydraulic fluid is displaced there, so that a high working pressure is generated in the working space 3 due to the relatively small plunger diameter.
  • This pressure corresponds to the transmission ratio of the working surfaces of the drive piston 19 to the plunger 21, starting from the pneumatic pressure acting on the drive piston 19.
  • the resulting high hydraulic pressure acts directly on the working piston 2 and causes the desired high force on the piston rod 4.
  • the pneumatic pressure in the drive chamber 22 is reduced and a corresponding pneumatic pressure is built up in the pneumatic chamber 17, so that the drive piston 19 with the plunger 21 is pushed back into the starting position shown, after which from the working chamber 3, through the working piston 2 displaced, hydraulic fluid flows into the storage space 9 and the working piston 2, driven by the auxiliary piston 5 and compressed air in the pneumatic space 8, is displaced into the starting position also shown.
  • the various pneumatic spaces are leading to the outside of the hydropneumatic pressure intensifier 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 chamber 22 through the channel 29.
  • control Connection channels 26 and 28 for the pneumatic spaces 8 and 17 are connected to one another via a pneumatic control line 31, so that when the pneumatic control pressure is supplied via them, the auxiliary piston 5 and the drive piston 19 are pushed into the starting position shown.
  • the pressure in the pneumatic control line 31 is reduced and passed into a pneumatic control line 32 which connects the connecting channels 25, 27 and 29 to one another, the connecting channel 29 being connected upstream of a pressure-controlled valve 33.
  • the supplied pneumatic pressure is thus first supplied to the connecting channels 25 and 27 and thus to the pneumatic chamber 7 and the control chamber 12, after which the auxiliary piston 5 with the working piston 2 is pushed down in rapid traverse and the accumulator piston 11 corresponding to the one overflowing from the storage chamber 9 into the working chamber 3 Hydraulic amount is replenished.
  • the hydraulic volume in the work space 3 and the storage space 9 is constant overall, apart from leak quantities that have to be refilled every now and then.
  • the accumulator piston 11 is arranged between the oil-filled storage chamber 9 and the control chamber 12 filled with air of different pressure according to the above-mentioned control, the main aim being to prevent oil air from the storage space 9 into the control space 12 and vice versa into the storage space 9.
  • an absolute air-oil separation on the storage piston 11 is used for this purpose, in which it has annular grooves 34 and 35 with radial seals 36 and 37 on the one hand both towards the casing tube 13 and towards the plunger 21.
  • the radial seals 37 to the plunger 21 are shown once as a round cord seal and once as a sleeve seal.
  • annular groove 38 is arranged on the outer surface of the accumulator piston 11 and is vented to the outside of the unit via a ventilation hole 39 arranged in the outer casing 13.
  • the vent hole 39 is arranged in relation to the annular groove 38, or the maximum possible stroke of the accumulator piston 11, so that it always remains in register with the annular groove 38.
  • annular groove 42 is provided in the central bore 41 of the storage piston 11, which is penetrated by the plunger 21, and is connected by a continuous radial bore 43 to the always vented annular groove 38 on the outer surface of the storage piston 11.

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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)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Damping Devices (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 Druckubersetzern 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 intensifier according to the preamble of the main claim. A main problem with such hydropneumatic pressure boosters is the sealing between the storage space and the control space, since the hydraulic pressures in the storage space and the pneumatic pressures in the control space change continuously during a work cycle, and do not necessarily change synchronously, with the risk that oil will leak out the storage space enters the control room and this causes leakage losses, which can affect the working capacity of the hydropneumatic pressure intensifier, or there is a risk that air from the control room gets into the storage space, where it is absorbed by the oil with the disadvantage that it enters the Workspace arrives and there tends to be more compressible during the high pressure phase of the pressure stroke with all the resulting disadvantages for the ability of the unit to work.

Bei einem bekannten gattungsgemäßen hydropneumatischen Druckübersetzer (DE-OS 2810 894) sind aus diesem Grunde sowohl zur Wand des Arbeitszylinders hin, als auch zur Mantelffläche 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.For this reason, in a known generic hydropneumatic pressure intensifier (DE-OS 2810 894), two radial seals are provided both towards the wall of the working cylinder and towards the outer surface of the plunger with the purpose of achieving an optimal air-oil separation. It is particularly problematic here that the tendency of the air to get from the control chamber into the storage space is not present in the low-pressure phase, but rather in the high-pressure phase, with small amounts of air being "pumped past" the radial seals as wall laminates during the axial movement of the storage piston .

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.The hydropneumatic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage over the fact that there is a low pressure in the ventilation ring grooves, for example atmospheric pressure, so that any air volume passing to the control chamber can be derived.
Should oil quantities get into the ventilation ring grooves from the storage space, this is not disadvantageous, at least for the respective work process, but it is only necessary to add oil to the storage space if there is a considerable loss of oil.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung dient zu 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.According to a further advantageous embodiment of the invention, a bore in the working cylinder is used for ventilation, which is always in overlap with the circumferential surface groove regardless of the working stroke of the storage piston. Both in the starting position and in the end position - possibly with only a small amount remaining in the storage space - is completely relieved, whereby the vent hole can lead directly to the atmosphere.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist die in der Bohrungswand vorhandene Entlastungsringnut mit jener auf der Mantelflache 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 a further advantageous embodiment of the invention, the relief ring groove in the bore wall is connected to that on the lateral surface by at least one radial bore of the storage piston. Such a radial bore can be carried out in a simple manner as a transverse bore, the beginning and end of this radial bore each ending in the annular groove surface and thus having 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, on both sides of the ventilation ring grooves there are additionally known sealing ring grooves for receiving radial seals.

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 can be found in the following description, the drawing and the claims.

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und wird im Folgenden naher beschrieben.
Es zeigen:

Fig. 1
einen hydropneumatischen Druckübersetzer im Längsschnitt und
Fig. 2
einen Ausschnitt aus Fig. 1 im vergrößerten Maßstab.
An embodiment of the object of the invention is shown in the drawing and will be described in more detail below.
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 pressure intensifier shown in FIGS. 1 and 2, a working piston 2 is arranged axially displaceably and radially sealingly in a housing 1 and delimits a working space 3 filled with hydraulic oil with it. A piston rod 4 projecting outside the housing is arranged on the working piston 2. In addition, the working piston 2 as a collar has an auxiliary piston 5, which is radially sealed off from a casing tube 6 and thereby separates two pneumatic spaces 7 and 8, which are alternately supplied with pneumatic pressure for the rapid traverse of the working piston 2. As soon as there is sufficient working pressure in the pneumatic space 7, the working piston 2 is pushed down and vice versa, with a correspondingly high pressure in the pneumatic space 8 and a reduced pressure in the pneumatic space 7, the working piston 2 is moved back into the starting position shown.

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 working space 3 and hydraulically connected to it is a storage space 9 for hydraulic oil, the storage pressure of which is generated by a storage piston and the pneumatic pressure in a control space 12. The accumulator piston 11 is guided in a jacket tube 13, which delimits the accumulator chamber 9 and the control chamber 12, in a radially sealing and axially displaceable manner, in the manner of a free piston. The casing tube 13 is closed on the one hand by a housing part 14 of the housing 1 and on the other hand by a partition wall 15, with corresponding twists on the housing part 14 and partition wall 15 for pushing on the casing tube 13, with additional static seals 16. On the side facing away from the control chamber 12 the partition 15 serves to delimit a pneumatic space 17 which is surrounded by a casing tube 18 and in which the drive piston 19 of a plunger 21 is mounted, which can be displaced in the working space 3 against the hydraulic pressure.

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 and the storage piston 11 in a radially sealed manner and dips with its free end into the storage space 9. The drive piston 19 with the plunger 21 is driven by compressed air which is conducted into a drive space 22 above the drive piston 21, as a result of which the high-pressure operation is initiated. Here, the plunger 21, after covering a certain stroke, dips into a connecting bore 23 leading from the storage space 9 to the working space 3, this connection being interrupted with the participation of a radial seal 24. With a further stroke of the plunger 21 and a correspondingly deeper immersion in the working space 3, hydraulic fluid is displaced there, so that a high working pressure is generated in the working space 3 due to the relatively small plunger diameter. This pressure corresponds to the transmission ratio of the working surfaces of the drive piston 19 to the plunger 21, starting from the pneumatic pressure acting on the drive piston 19. 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 in the drive chamber 22 is reduced and a corresponding pneumatic pressure is built up in the pneumatic chamber 17, so that the drive piston 19 with the plunger 21 is pushed back into the starting position shown, after which from the working chamber 3, through the working piston 2 displaced, hydraulic fluid flows into the storage space 9 and the working piston 2, driven by the auxiliary piston 5 and compressed air in the pneumatic space 8, is displaced into the starting position also shown.

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 spaces are leading to the outside of the hydropneumatic pressure intensifier 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 chamber 22 through the channel 29. According to an exemplary type of control Connection channels 26 and 28 for the pneumatic spaces 8 and 17 are connected to one another via a pneumatic control line 31, so that when the pneumatic control pressure is supplied via them, the auxiliary piston 5 and the drive piston 19 are pushed into the starting position shown. For the working stroke, however, the pressure in the pneumatic control line 31 is reduced and passed into a pneumatic control line 32 which connects the connecting channels 25, 27 and 29 to one another, the connecting channel 29 being connected upstream of a pressure-controlled valve 33. The supplied pneumatic pressure is thus first supplied to the connecting channels 25 and 27 and thus to the pneumatic chamber 7 and the control chamber 12, after which the auxiliary piston 5 with the working piston 2 is pushed down in rapid traverse and the accumulator piston 11 corresponding to the one overflowing from the storage chamber 9 into the working chamber 3 Hydraulic amount is replenished. The hydraulic volume in the work space 3 and the storage space 9 is constant overall, apart from leak quantities that have to be refilled every now and then. As soon as the piston rod 4 encounters resistance (end of the rapid traverse), the pressure in the pneumatic control line 32 increases and the pressure-controlled valve 33 releases the inflow to the connecting channel 29 and thus to the drive chamber 22, so that the drive piston 19 with plunger 21 downwards 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 arranged between the oil-filled storage chamber 9 and the control chamber 12 filled with air of different pressure according to the above-mentioned control, the main aim being to prevent oil air from the storage space 9 into the control space 12 and vice versa into the storage space 9. According to the invention, an absolute air-oil separation on the storage piston 11 is used for this purpose, in which it has annular grooves 34 and 35 with radial seals 36 and 37 on the one hand both towards the casing tube 13 and towards the plunger 21. The radial seals 37 to the plunger 21 are shown once as a round cord seal and once as a sleeve seal. In order to maintain an absolute pressure reduction and thereby the air-oil separation in the area between the radial seals, an annular groove 38 is arranged on the outer surface of the accumulator piston 11 and is vented to the outside of the unit via a ventilation hole 39 arranged in the outer casing 13. The vent hole 39 is arranged in relation to the annular groove 38, or the maximum possible stroke of the accumulator piston 11, so that it always remains in register with the annular groove 38. In addition, an annular groove 42 is provided in the central bore 41 of the storage piston 11, which is penetrated by the plunger 21, and is connected by a continuous radial bore 43 to the always vented annular groove 38 on the outer surface of the storage piston 11.

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

BezugszahlenlisteList of reference numbers

11
Gehäusecasing
22nd
Arbeitskolben SteuerleitungPiston control line
33rd
Arbeitsraum SteuerleitungControl room workspace
44th
Kolbenstange gesteuertesPiston rod controlled
55
HilfskolbenAuxiliary piston
66
MantelrohrCasing pipe
77
PneumatikraumPneumatic room
88th
PneumatikraumPneumatic room
99
SpeicherraumStorage space
1010th
--
1111
SpeicherkolbenAccumulator piston
1212th
SteuerraumControl room
1313
MantelrohrCasing pipe
1414
GehäuseteilHousing part
1515
Trennwandpartition wall
1616
Statische DichtungStatic seal
1717th
PneumatikraumPneumatic room
1818th
MantelrohrCasing pipe
1919th
AntriebskolbenDrive piston
2020th
--
2121
TauchkolbenPlunger
2222
AntriebsraumDrive room
2323
VerbindungsbohrungConnecting hole
2424th
RadialdichtungRadial seal
2525th
AnschlußkanalConnecting channel
2626
AnschlußkanalConnecting channel
2727
AnschlußkanalConnecting channel
2828
AnschlußkanalConnecting channel
2929
AnschlußkanalConnecting channel
3030th
--
3131
PneumatischePneumatic
3232
PneumatischePneumatic
3333
Druckabhängig VentilPressure dependent valve
3434
RingnutRing groove
3535
RingnutRing groove
3636
RadialdichtungRadial seal
3737
RadialdichtungRadial seal
3838
RingnutRing groove
3939
EntlüftungsbohrungVent hole
4040
--
4141
Zentrale BohrungCentral hole
4242
RingnutRing groove
4343
RadialbohrungRadial bore

Claims (8)

Hydropneumatischer Druckübersetzer - mit einem in einem Aggregatsgehäuse angeordneten Arbeitsraum (3) für wechselnde Drücke, nämlich einem niederen Speicherdruck und einem hohen Arbeitsdruck, - mit einem den Arbeitsraum (3) stirnseitig begrenzenden und durch den Arbeitsdruck im Aggregatsgehäuse (1) für seinen Arbeitshub betätigbaren Arbeitskolben (2), der durch eine Kolbenstange (4) nach außen geführt ist, - mit einem mit dem Arbeitsraum (3) hydraulisch verbindbaren in einem Mantelrohr (13) angeordneten Speicherraum (9), aus dem während eines Eilgangs des Arbeitshubs Hydrauliköl unter Speicherdruck in den Arbeitsraum (3) strömt und beim Rückhub wieder zurückströmt, - mit einem als Hochdruckerzeuger pneumatisch oder hydraulisch betätigbaren und nach dem Eilgang des Arbeitskolbens 2 in den Arbeitsraum 3 tauchenden Tauchkolben (21), - mit einem den Speicherraum (9) begrenzenden axial im Mantelrohr (13) verschiebbaren und vom Tauchkolben (21) durchdrungenen Speicherkolben (11), der radial sowohl zum Tauchkolben (21) als auch zum Mantelrohr (13) abgedichtet ist, - mit einem auf der dem Speicherraum (9) abgewandten Seite des Speicherkolbens (11) vorhandenen und mit luftunterschiedlichen Drucks beaufschlagbaren Steuerraum (12) und - mit einer den Steuerraum (12) begrenzenden und mit dem Mantelrohr (13) fest verbundenen, sowie vom Tauchkolben (21) durchdrungenen Trennwand (15), dadurch gekennzeichnet, daß zur absoluten Öl-Lufttrennung auf der Mantelfläche des Speicherkolbens (11) und zwar in Hubrichtung zwischen den Radialdichtungen (36, 34) eine druckentlastete Außenringnut (38) vorgesehen ist und
daß in der Wand der Innenbohrung (41) die vom Tauchkolben (21) durchdrungen ist, ebenfalls zwischen den Radialdichtungen (37) eine Innenringnut (42) angeordnet ist.Hydropneumatic pressure intensifier with a working space (3) arranged in a unit housing for changing pressures, namely a low storage pressure and a high working pressure, - With a working piston (2) which delimits the working space (3) at the front and can be actuated by the working pressure in the unit housing (1) for its working stroke, which is guided to the outside by a piston rod (4), - With a storage space (9) which can be hydraulically connected to the working space (3) in a casing tube (13) and from which hydraulic oil flows into the working space (3) under storage pressure during a rapid traverse of the working stroke and flows back again on the return stroke, with a plunger (21) which can be actuated pneumatically or hydraulically as a high-pressure generator and plunges into the working space 3 after the rapid traverse of the working piston 2, - With a storage space (9) delimiting axially displaceable in the casing tube (13) and penetrated by the plunger (21), the storage piston (11), which is sealed radially to both the plunger (21) and the casing tube (13), - With a control chamber (12) which is present on the side of the storage piston (11) facing away from the storage space (9) and can be acted upon with different air pressure - With a partition (15) delimiting the control chamber (12) and firmly connected to the casing tube (13) and penetrated by the plunger (21), characterized in that a pressure-relieved outer ring groove (38) is provided for absolute oil-air separation on the lateral surface of the accumulator piston (11), namely in the stroke direction, and
that in the wall of the inner bore (41) which is penetrated by the plunger (21), an inner annular groove (42) is also arranged between the radial seals (37). Hydropneumatischer Druckübersetzer nach Anspruch 1, dadurch gekennzeichnet, daß zur Druckentlastung der Außenringnut (38) eine mit der Außenringnut (38) stets in Überdeckung stehende Entlüftungsbohrung (39) im Mantelrohr (13) angeordnet ist.Hydropneumatic pressure intensifier according to Claim 1, characterized in that a vent hole (39) which is always in overlap with the outer ring groove (38) is arranged in the casing tube (13) to relieve the pressure on the outer ring groove (38). Hydropneumatischer Druckübersetzer nach Anspruch 2, dadurch gekennzeichnet, daß die Entlüftungsbohrung (39) zur Atmosphäre hin führt.Hydropneumatic pressure intensifier according to claim 2, characterized in that the vent hole (39) leads to the atmosphere. Hydropneumatischer Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Außenringnut (38) mit der Innenringnut (42) durch eine Radialbohrung (43) im Speicherkolben (11) verbunden ist.Hydropneumatic pressure intensifier according to one of the preceding claims, characterized in that the outer ring groove (38) is connected to the inner ring groove (42) by a radial bore (43) in the accumulator piston (11). Hydropneumatischer Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß auf beiden Seiten der Außenringnut (38) bzw. Innenringnut (42) seperate Dichtungsringnuten (34, 35) vorgesehen sind zur Aufnahme von Radialdichtungen (36, 37).Hydropneumatic pressure intensifier according to one of the preceding claims, characterized in that separate sealing ring grooves (34, 35) are provided on both sides of the outer ring groove (38) or inner ring groove (42) for receiving radial seals (36, 37). Hydropneumatischer Druckübersetzer nach einem der vorhergehenden Ansprüche dadurch gekennzeichnet, daß in der Trennwand (15) radial nach außen führende Anschluß-kanäle (27, 28) für Druckluft vorhanden sind.Hydropneumatic pressure intensifier according to one of the preceding claims, characterized in that there are connection channels (27, 28) for compressed air leading radially outwards in the partition (15). Hydropneumatischer Druckübersetzer, dadurch gekennzeichnet, daß der auf der dem Steuerraum (12) abgewandten Seite der Trennwand (15) vorhandene Raum (17) luftdruckgesteuert ist, für die Rückstellung eines mit dem Tauchkolben (21) verbundenen Antriebskolbens (19).Hydropneumatic pressure intensifier, characterized in that the space (17) on the side of the partition (15) facing away from the control chamber (12) is controlled by air pressure for the resetting of a drive piston (19) connected to the plunger (21). Hydropneumatischer Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß ein Hilfskolben (5) mit dem Arbeitskolben (2) verbunden ist, der für einen Eilgang beiderseits abwechselnd pneumatisch beaufschlagbar ist.Hydropneumatic pressure intensifier according to one of the preceding claims, characterized in that an auxiliary piston (5) is connected to the working piston (2), which can be alternately acted upon pneumatically for rapid traverse on both sides.
EP93110428A 1992-07-02 1993-06-30 Hydropneumatic pressure intensifier Expired - Lifetime EP0579037B2 (en)

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DE4223411A DE4223411A1 (en) 1992-07-02 1992-07-02 Hydropneumatic pressure intensifier

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US5377488A (en) 1995-01-03
EP0579037B1 (en) 1997-09-24
JPH06159303A (en) 1994-06-07
ATE158642T1 (en) 1997-10-15
EP0579037B2 (en) 2003-01-22
DE59307411D1 (en) 1997-10-30

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