EP0577955A1 - Hydropneumatic pressure transformer - Google Patents

Hydropneumatic pressure transformer Download PDF

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Publication number
EP0577955A1
EP0577955A1 EP93107954A EP93107954A EP0577955A1 EP 0577955 A1 EP0577955 A1 EP 0577955A1 EP 93107954 A EP93107954 A EP 93107954A EP 93107954 A EP93107954 A EP 93107954A EP 0577955 A1 EP0577955 A1 EP 0577955A1
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EP
European Patent Office
Prior art keywords
piston
working
space
bore
storage
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Granted
Application number
EP93107954A
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German (de)
French (fr)
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EP0577955B1 (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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • 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 hydraulic pressure intensifier according to the preamble of the main claim.
  • a hydraulic pressure intensifier of the generic type DE PS 28 18 332
  • the plunger is held in its starting position by a return spring, this spring simultaneously acting on a storage piston, whereby the low pressure is generated in the storage space.
  • the hydraulic fluid flows from the storage space into the enlarging working space under this low pressure.
  • the plunger is then driven and, above all, plunges into the bore in a radially sealing manner, the high pressure is generated in the working space when the plunger is moved further into the hydraulic fluid there, which further drives the working piston.
  • the hydraulic pressure booster according to the invention with the characterizing features of the main claim has the advantage over the fact that extreme precision is achieved in the repetition of the individual operations and with relatively little effort. If the plunger dives too early into the bore and the high-pressure seal there and no more hydraulic fluid can flow from the storage space into the working space via this channel, then hydraulic fluid flows from the storage space into the working space via the second connecting channel and thus prevents a negative pressure in the Working space is created, which can lead to the release of air bound in the hydraulic fluid, up to the foaming of the oil. Then when the plunger following the hasty working piston, the working space is completely filled with the hydraulic fluid that has flowed through the connecting channel in the meantime, so that the power stroke begins precisely at the same time as the plunger is moved.
  • a similar advantage also exists during the return stroke of the plunger if it leads the working piston so that a negative pressure can arise in the working space because hydraulic fluid can flow from the storage space into the working space via the connecting channel according to the invention, before the return stroke of the working piston Hydraulic fluid can flow back into the reservoir through the hole.
  • the return stroke of the working piston then takes place as described in detail.
  • additional power strokes can be carried out as required and different control sequences can also take place.
  • a second rapid stroke instead of a second rapid stroke, only a stopping in the working position after the first power stroke can take place, in which time the plunger returns, after which the second power stroke starts immediately with regard to the stroke after the first power stroke of the working piston.
  • the plunger moves back a little in an interim period, during which hydraulic fluid can flow from the storage space into the working space.
  • the stroke of the plunger required in several stages can be divided into several sections with a corresponding return stroke, so that the cross-sectional ratio of plunger to working piston can be chosen to be extremely different, with the advantage of an extraordinarily high pressure ratio.
  • a check valve that opens in the direction of the working space and closes in the direction of the storage space is arranged in the connecting channel.
  • This check valve can be equipped with or without a closing spring, it can be designed as a slide valve, ball valve or other check valve, such as a flap valve. Decisive for the opening of the check valve is the difference between the pressures in the work space and the storage space and of course the area acted on the movable valve part, as well as the force of the closing spring.
  • the check valve can be designed so that even very low pressures are sufficient to open it.
  • the connecting channel and check valve are arranged in the housing of the hydraulic pressure booster.
  • the two spaces are connected to one another via a line running outside the housing and in which the check valve is arranged.
  • the application of the invention is particularly advantageous in the case of a hydraulic pressure intensifier in the form of a hydropneutical pressure intensifier which has the features of claim 6.
  • a hydropneumatic pressure intensifier is known per se (DE PS 28 18 337) and, above all, has the problem that, due to the additional independent pneumatic actuation of the working piston, it leads the plunger or lags on the return stroke.
  • the invention can of course also be applied to such hydropneumatic pressure intensifiers in which the storage space on the one hand and the working space on the other hand are accommodated in two cylinders which are independent and in particular arranged in parallel, as are known per se and have also been supplied for a long time.
  • the decisive factor is that whatever the course, this additional connection channel is present between the storage space and the work space.
  • a working piston 2 is arranged axially displaceably in a working space 1 filled with hydraulic oil and is guided in a bore in a housing 3.
  • a piston rod 4 projecting outside the housing is arranged on the working piston 2 for power transmission.
  • a disc piston 5 is attached to the working piston 2 and piston rod 4. This disc piston 5 is radially sealed to a casing tube 6 and thereby separates two spaces 7 and 8, which are alternately supplied with compressed air for the rapid traverse of the working piston 2.
  • the working piston 2 is pushed downwards.
  • the working piston 2 is moved up again into the starting position shown.
  • a storage space 9 hydraulically connected to the working space 1 above the working space 1, in which a lower one by a storage piston 11 with a storage spring 12 Hydraulic accumulator pressure is generated, which is sufficient to keep the working space 1 filled with hydraulic oil from the storage space 9 during the rapid stroke of the working piston 2.
  • the storage piston 11 is guided in a radially sealing and axially displaceable tube 13.
  • a drive piston 14 of a plunger 15 which can be displaced in the direction of the working space 1 against the force of the storage spring 12.
  • the plunger 15 penetrates, radially sealed, the storage piston 11 and dips into the storage space 9.
  • the drive piston 14 with plunger 15 is driven by compressed air, which is conducted into a control chamber 16 above the drive piston 14. This control of compressed air occurs when the working piston 2 has ended its rapid traverse and before the actual pressure stroke of the working piston 2 is to begin. If the drive piston 14 is displaced by the compressed air, after a forward stroke the plunger 15 plunges into a connecting bore 17 leading from the storage space 9 to the work space 1, after which this connection is interrupted by the cooperation of a radial seal 18, so that the plunger 15 is submerged further Hydraulic fluid is displaced into the working space 1 there, with a corresponding action on the working piston 2.
  • the pneumatic pressure in the control chamber 16 is reduced, so that the storage spring 12 pushes the drive piston 14 back into the starting position shown.
  • the working piston 2 is pushed back into the starting position shown by the disk piston 5 via pressure reduction in the pneumatic chamber 7 or pressure build-up in the pneumatic chamber 8, hydraulic fluid being displaced back into the storage chamber 9 by the working piston 2 and the storage piston 11 being there against the force the storage spring 12 is moved back to the starting position shown.
  • a connecting channel 19 is provided, in which a check valve blocking in the direction of the storage space 9 is arranged, with a movable valve member 21 and a spring 22 then hydraulic fluid still flows from the storage space 9 into the working space 1 when the connecting bore 17 is blocked by the plunger 15 or the radial seal 18.
  • connection channel between the storage space 9 and the working space 1 is a line 23 running outside the housing 3, in which a correspondingly arranged check valve with a movable valve member 24 and a spring 25 is arranged, this check valve 24, 25 also locks towards storage space 9.

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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-Damping Devices (AREA)
  • Housings And Mounting Of Transformers (AREA)
  • Safety Valves (AREA)
  • Actuator (AREA)
  • Glass Compositions (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)
  • Colloid Chemistry (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)

Abstract

The invention relates to a hydropneumatic pressure transformer in which a storage space (9) and a working space (1) with an overflow bore (17) are connected to one another, into which a plunger piston (15) plunges to produce a pressure stage and thereby separates the two spaces and produces a high pressure in the working space (1). According to the invention, an additional connecting passage (19) with a non-return valve (21, 22) is provided.

Description

Die Erfindung geht aus von einem hydraulischen Druckübersetzer nach der Gattung des Hauptanspruchs. Bei einem bekannten hydraulischen Druckübersetzer der gattungsgemäßen Art (DE PS 28 18 332) ist der Tauchkolben über eine Rückstellfeder in seiner Ausgangslage gehalten, wobei diese Feder gleichzeitig einen Speicherkolben beaufschlagt, wodurch im Speicherraum der niedere Druck erzeugt wird. Sobald der Arbeitskolben für einen Eilhub freigegeben istbei diesem bekannten hydraulischen Druckübersetzer pneumatisch angetrieben- strömt die Hydraulikflüssigkeit vom Speicherraum in den sich vergrößernden Arbeitsraum und zwar unter diesem niederen Druck. Sobald dann der Tauchkolben angetrieben wird, und vor allem in die Bohrung radial dichtend eintaucht, wird im Arbeitsraum bei weiterem verschieben des Tauchkolbens in die dort vorhandene Hydraulikflüssigkeit der Hochdruck erzeugt, der den weiteren Antrieb des Arbeits-kolbens bewirkt. In der Praxis wurde festgestellt, daß an diesem Trennpunkt eine außerordentliche Sensibilität in der Steuerung besteht, die einerseits von den Druckunterschieden beeinflußt ist, bei der stets vorhandenen Kompressibilität von Hydraulikflüssigkeit und andererseits von der Arbeitsgeschwindigkeit, bei der sich vor allem die Massenträgheit der Einzelteile auswirkt. Nicht zuletzt hat auch die Radialdichtung in der Bohrung einen gewissen Einfluß auf die Steuerqualität.The invention is based on a hydraulic pressure intensifier according to the preamble of the main claim. In a known hydraulic pressure intensifier of the generic type (DE PS 28 18 332), the plunger is held in its starting position by a return spring, this spring simultaneously acting on a storage piston, whereby the low pressure is generated in the storage space. As soon as the working piston is released for a rapid stroke with this known hydraulic pressure intensifier, the hydraulic fluid flows from the storage space into the enlarging working space under this low pressure. As soon as the plunger is then driven and, above all, plunges into the bore in a radially sealing manner, the high pressure is generated in the working space when the plunger is moved further into the hydraulic fluid there, which further drives the working piston. In practice, it was found that there is an extraordinary sensitivity in the control at this separation point, which is influenced on the one hand by the pressure differences, by the always present compressibility of hydraulic fluid and on the other hand by the working speed, at which, above all, the inertia which affects individual parts. Last but not least, the radial seal in the bore has a certain influence on the control quality.

Umfangreiche Untersuchungen im Zusammenhang mit den Fertigungsfehlern die mit solchen hydraulischen Druckübersetzern auftraten, führten zur Vermutung oben genannter Steuerungsprobleme und zu Verbesserungen der einzelnen, die Steuerung beeinflußenden und, zum Teil oben genannten Teile und Steuerungen des hydraulischen Druckübersetzers, ohne das Erreichen einer wirklichen Verbesserung der Nachteile. Da mit solchen hydraulischen Druckübersetzern u.a. auch Clinch-verbindungen oder Nietverbindungen hergestellt werden, wirkt sich die unterschiedliche oder auch mangelnde Präzision auf die Qualität der Verbindung aus, wobei diese Mängel kaum mit dem bloßen Auge erkennbar sind, sondern erst durch modernste Meßgerät festgestellt wurden.Extensive studies in connection with the manufacturing errors that occurred with such hydraulic pressure intensifiers led to the presumption of the above-mentioned control problems and to improvements in the individual parts that influence the control and, in part, the parts and controls of the hydraulic pressure intensifier mentioned above, without achieving a real improvement in the disadvantages . As with such hydraulic pressure intensifiers i.a. Even clinch connections or rivet connections are made, the different or even lack of precision affects the quality of the connection, whereby these defects are hardly visible to the naked eye, but were only detected by the most modern measuring device.

Der erfindungsgemäße hydraulische Druckübersetzer mit den kennzeichnenden Merkmalen des Hauptanspruchs hat dem gegenüber den Vorteil, daß eine äußerste Präzision bei der Wiederholung der einzelnen Arbeitsgänge erzielt wird und zwar mit einem verhältnismäßig geringen Aufwand. Wenn der Tauchkolben zu früh in die Bohrung und die dort vorhandene Hochdruckdichtung eintaucht und keine Hydraulikflüssigkeit mehr über diesen Kanal vom Speicherraum in den Arbeitsraum fließen kann, so strömt erfindungsgemäß über den zweiten Verbindungskanal Hydraulikflüssigkeit vom Speicherraum in den Arbeitsraum und vermeidet damit, daß ein Unterdruck im Arbeitsraum entsteht, der zur Lösung von in der Hydraulikflüssigkeit gebundener Luft führen kann, bis hin zur Aufschäumung des Öls. Wenn dann der Tauchkolben dem vorgeeilten Arbeitskolben nachfolgt, ist der Arbeitsraum über die zwi-schenzeitlich durch den Verbindungskanal geströmte Hydrau-likflüssigkeit voll aufgefüllt, so daß hier präzise der Krafthub zeitgleich mit dem Verschieben des Tauchkolbens beginnt. Ein ähnlicher Vorteil besteht dann auch beim Rückhub des Tauchkolbens, wenn dieser dem Arbeitskolben vorauseilt, so daß im Arbeitsraum ein Unterdruck entstehen kann, weil über den erfindungsgemäßen Verbindungskanal sogleich Hydraulikflüssigkeit vom Speicherraum in den Arbeitsraum strömen kann, bevor dann, beim Rückhub des Arbeitskolbens, diese Hydraulikflüssigkeit über die Bohrung zurück in den Speicherraum strömen kann.The hydraulic pressure booster according to the invention with the characterizing features of the main claim has the advantage over the fact that extreme precision is achieved in the repetition of the individual operations and with relatively little effort. If the plunger dives too early into the bore and the high-pressure seal there and no more hydraulic fluid can flow from the storage space into the working space via this channel, then hydraulic fluid flows from the storage space into the working space via the second connecting channel and thus prevents a negative pressure in the Working space is created, which can lead to the release of air bound in the hydraulic fluid, up to the foaming of the oil. Then when the plunger following the hasty working piston, the working space is completely filled with the hydraulic fluid that has flowed through the connecting channel in the meantime, so that the power stroke begins precisely at the same time as the plunger is moved. A similar advantage also exists during the return stroke of the plunger if it leads the working piston so that a negative pressure can arise in the working space because hydraulic fluid can flow from the storage space into the working space via the connecting channel according to the invention, before the return stroke of the working piston Hydraulic fluid can flow back into the reservoir through the hole.

Ein weiterer sehr wesentlicher Vorteil der Erfindung, der sich in Art eines erfinderischen Verfahrens äußert, kann der Krafthub des Arbeitskolbens in mehreren Stufen erfolgen, wobei zwischen den Stufen der Tauchkolben um einen erforderlichen Hub zurückfahren kann, wobei während dieses Rückhubs Hydraulikflüssigkeit aus dem Speicherraum in den Arbeitsraum nachströmt. Der Arbeitsablauf bzw. Verfahrensablauf besteht dann aus folgenden Schritten:

  • pneumatischer Eilgang des Arbeitskolbens, bei gleichzeitigem Nachströmen von Hydraulikflüssigkeit aus dem Speicherraum in den Arbeitsraum und zwar über die Bohrung, sowie den Verbindungskanal.
  • Krafthub des Arbeitskolbens nach Betätigung des Tauchkolbens und dessen Eintauchen in die Bohrung
  • Beenden dieses ersten Krafthubs durch Beenden des Vorwärtshubs des Tauchkolbens
  • pneumatischer zweiter Eilhub des Arbeitskolbens bei gleichzeitigem leichten Rückhub des Tauchkolbens und Nachströmen von Hydraulikflüssigkeit über den Erfindungsgemäßen Verbindungskanal in den Arbeitsraum, diesen dabei Auffüllen
  • Vorwärtshub des Tauchkolbens in den Arbeitsraum mit gleichzeitigem Antrieb des Arbeitskolbens für dessen zweiten Krafthub.
Another very important advantage of the invention, which manifests itself in the manner of an inventive method, the power stroke of the working piston can take place in several stages, the plunger piston being able to move back by a required stroke between the stages, hydraulic fluid from the storage space during this return stroke Flows into the work area. The workflow or process flow then consists of the following steps:
  • pneumatic rapid traverse of the working piston, with simultaneous inflow of hydraulic fluid from the storage space into the working space, specifically through the bore and the connecting channel.
  • Power stroke of the working piston after actuation of the plunger and its immersion in the bore
  • End this first power stroke by ending the forward stroke of the plunger
  • pneumatic second rapid stroke of the working piston with simultaneous slight return stroke of the plunger and afterflow of hydraulic fluid via the connecting channel according to the invention into the working space, filling it up
  • Forward stroke of the plunger into the working area with simultaneous drive of the working piston for its second power stroke.

Der Rückhub des Arbeitskolbens erfolgt dann wie im einzelnen beschrieben. Statt zwei Krafthübe können auch je nach Bedarf zusätzliche Krafthübe durchgeführt werden und es können auch unterschiedliche Steuerfolgen stattfinden. So kann beispielsweise statt einem zweiten Eilhub lediglich ein Verharren in der Arbeitsstellung nach dem ersten Krafthub stattfinden, in welcher Zeit der Tauchkolben zurückfahrt, wonach dann bezüglich des Hubes nach dem ersten Krafthub des Arbeitskolbens sofort der zweite Krafthub ansetzt. Maßgebend an diesem Verfahren ist, daß der Tauchkolben in einem Zwischenzeitabschnitt ein Stück zurückfährt, während dem Hydraulikflüssigkeit vom Speicherraum in denArbeitsraum strömen kann. Auf diese Weise kann vor allem der bei mehreren Stufen erforderliche Hub des Tauchkolbens in mehrere Abschnitte mit entsprechendem Rückhub aufgeteilt werden, sodaß das Querschnittsverhältnis, Tauchkolben zu Arbeitskolben extrem unterschiedlich gewählt werden kann, mit dem Vorteil einer außerordentlich hohen Druckübersetzung.The return stroke of the working piston then takes place as described in detail. Instead of two power strokes, additional power strokes can be carried out as required and different control sequences can also take place. For example, instead of a second rapid stroke, only a stopping in the working position after the first power stroke can take place, in which time the plunger returns, after which the second power stroke starts immediately with regard to the stroke after the first power stroke of the working piston. What is decisive in this method is that the plunger moves back a little in an interim period, during which hydraulic fluid can flow from the storage space into the working space. In this way, the stroke of the plunger required in several stages can be divided into several sections with a corresponding return stroke, so that the cross-sectional ratio of plunger to working piston can be chosen to be extremely different, with the advantage of an extraordinarily high pressure ratio.

Nach einer Ausgestaltung der Erfindung ist im Verbindungskanal ein in Richtung Arbeitsraum öffnendes und in Richtung Speicherraum schließendes Rückschlagventil angeordnet. Dieses Rückschlagventil kann mit oder ohne Schließfeder ausgestattet sein, es kann als Schieberventil, Kugelventil oder sonstiges Rückschlagventil, wie beispielsweise Flatterventil ausgebildet sein. Maßgebend für das sich Öffnen des Rückschlagventils ist die Differenz der Drücke im Arbeitsraum und Speicherraum und natürlich die am beweglichen Ventilteil beaufschlagte Fläche, sowie die Kraft der Schließfeder. Hierbei ist das Rückschlagventil so ausbildbar, daß schon ganz geringe Drücke zu seinem Öffnen ausreichen.According to one embodiment of the invention, a check valve that opens in the direction of the working space and closes in the direction of the storage space is arranged in the connecting channel. This check valve can be equipped with or without a closing spring, it can be designed as a slide valve, ball valve or other check valve, such as a flap valve. Decisive for the opening of the check valve is the difference between the pressures in the work space and the storage space and of course the area acted on the movable valve part, as well as the force of the closing spring. Here, the check valve can be designed so that even very low pressures are sufficient to open it.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung sind Verbindungskanal und Rückschlagventil im Gehäuse des hydraulischen Druckübersetzers angeordnet.According to a further advantageous embodiment of the invention, the connecting channel and check valve are arranged in the housing of the hydraulic pressure booster.

Gemäß einer anderen vorteilhaften Ausgestaltung der Erfindung sind die beiden Räume über eine außerhalb des Gehäuses verlaufenden Leitung miteinander verbunden, in welcher das Rückschlagventil angeordnet ist.According to another advantageous embodiment of the invention, the two spaces are connected to one another via a line running outside the housing and in which the check valve is arranged.

Besonders vorteilhaft ist die Anwendung der Erfindung bei einem hydraulischen Druckübersetzer in Form eines hydropneutischen Druckübersetzers der die Merkmale des Anspruchs 6 aufweist. Ein solcher hydropneumatischer Druckübersetzer ist an sich bekannt (DE PS 28 18 337) und weist vor allem die Problematik auf, daß aufgrund der zusätzlichen unabhängigen pneumatischen Betätigung des Arbeitskolbens dieser dem Tauchkolben vorauseilt oder beim Rückhub nacheilt.The application of the invention is particularly advantageous in the case of a hydraulic pressure intensifier in the form of a hydropneutical pressure intensifier which has the features of claim 6. Such a hydropneumatic pressure intensifier is known per se (DE PS 28 18 337) and, above all, has the problem that, due to the additional independent pneumatic actuation of the working piston, it leads the plunger or lags on the return stroke.

Die Erfindung ist natürlich auch auf solche Hydropneumatische Druckübersetzer anwendbar, bei denen der Speicherraum einerseits und der Arbeitsraum andererseits in zwei, in soweit unabhängigen, insbesondere jedoch parallel angeordneten Zylindern untergebracht sind, wie sie an sich bekannt sind und auch seit längerer Zeit geliefert werden. Maßgebend ist, daß in welchem Verlauf auch immer, zwischen dem Speicherraum und dem Arbeitsraum dieser zusätzliche Verbindungskanal vorhanden ist.The invention can of course also be applied to such hydropneumatic pressure intensifiers in which the storage space on the one hand and the working space on the other hand are accommodated in two cylinders which are independent and in particular arranged in parallel, as are known per se and have also been supplied for a long time. The decisive factor is that whatever the course, this additional connection channel is present between the storage space and the work space.

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 of the drawing and the claims.

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

Fig. 1
einen hydropneumatischen Druckübersetzer im Längsschnitt und
Fig. 2
einen Ausschnitt aus Figur 1 mit einer Variante der Erfindung.
An embodiment of the object of the invention is shown in the drawing and described in more detail below. Show it:
Fig. 1
a hydropneumatic pressure intensifier in longitudinal section and
Fig. 2
a section of Figure 1 with a variant of the invention.

Bei dem in Fig. 1der Zeichnung dargestellten Ausführungsbeispiel ist in einem mit Hydrauliköl gefüllten Arbeitsraum 1 ein Arbeitskolben 2 axial verschiebbar angeordnet, der in einer Bohrung eines Gehäuses 3 geführt ist. An dem Arbeitskolben 2 ist zur Kraftübertragung eine nach außerhalb des Gehäuses ragende Kolbenstange 4 angeordnet. Außerdem ist ein Scheibenkolben 5 an Arbeitskolben 2 und Kolbenstange 4 befestigt. Dieser Scheibenkolben 5 ist zu einem Mantelrohr 6 hin radial abgedichtet und trennt dadurch zwei Räume 7 und 8, die für den Eilgang des Arbeitskolbens 2 abwechselnd mit Druckluft versorgt werden. Sobald im Pneumatikraum 7 ein Überdruck erzeugt wird, wird der Arbeitskolben 2 nach unten geschoben. Sobald im Pneumatikraum 8 ein Überdruck erzeugt wird, wird der Arbeitskolben 2 wieder nach oben in die dargestellt Ausgangslage verschoben.In the embodiment shown in FIG. 1 of the drawing, a working piston 2 is arranged axially displaceably in a working space 1 filled with hydraulic oil and is guided in a bore in a housing 3. A piston rod 4 projecting outside the housing is arranged on the working piston 2 for power transmission. In addition, a disc piston 5 is attached to the working piston 2 and piston rod 4. This disc piston 5 is radially sealed to a casing tube 6 and thereby separates two spaces 7 and 8, which are alternately supplied with compressed air for the rapid traverse of the working piston 2. As soon as an overpressure is generated in the pneumatic chamber 7, the working piston 2 is pushed downwards. As soon as an overpressure is generated in the pneumatic chamber 8, the working piston 2 is moved up again into the starting position shown.

Wie in der Zeichnung dargestellt ist oberhalb vom Arbeitsraum 1 ein mit dem Arbeitsraum 1 hydraulisch verbundener Speicherraum 9 vorhanden, in dem durch einen Speicherkolben 11 mit Speicherfeder 12 ein niedriger hydraulischer Speicherdruck erzeugt wird, der ausreicht, um beim Eilhub des Arbeitskolbens 2 den Arbeitsraum 1 mit Hydrauliköl aus dem Speicherraum 9 aufgefüllt zu halten. Der Speicherkolben 11 ist in einem Mantelrohr 13 radial dichtend und axial verschiebbar geführt. Ebenfalls radial dichtend und axial verschiebbar geführt ist in diesem Mantelrohr 13 ein Antriebskolben 14 eines Tauchkolbens 15 gelagert, der entgegen der Kraft der Speicherfeder 12 in Richtung Arbeitsraum 1 verschiebbar ist. Der Tauchkolben 15 durchdringt, radial abgedichtet, den Speicherkolben 11 und taucht in den Speicherraum 9. Der Antriebskolben 14 mit Tauchkolben 15 wird durch Druckluft angetrieben, die in einen Steuerraum 16 oberhalb des Antriebskolbens 14 geleitet wird. Diese Zusteuerung von Druckluft erfolgt dann, wenn der Arbeitskolben 2 seinen Eilgang beendet hat, und bevor der eigentliche Druckhub des Arbeitskolbens 2 beginnen soll. Wenn der Antriebskolben 14 durch die Druckluft verschoben wird, taucht nach Zurücklegung eines Vorhubes der Tauchkolben 15 in eine, vom Speicherraum 9 zum Arbeitsraum 1 führende Verbindungsbohrung 17, wonach diese Verbindung durch Mitwirkung einer Radialdichtung 18 unterbrochen ist, so daß bei weiterem Eintauchen des Tauchkolbens 15 in den Arbeitsraum 1 dort Hydraulikflüssigkeit verdrängt wird, unter entsprechender Beaufschlagung des Arbeitskolbens 2. Da die Querschnittsfläche des Antriebskolbens 14 wesentlich größer ist als jene des Tauchkolbens 15, ergibt sich eine entsprechend hohe Druckübersetzung vom Pneumatikdruck im Steuerraum 16 zum Hydraulikdruck im Arbeitsraum 1. Da wiederum die Querschnittsfläche vom Arbeitskolben 2 wesentlich größer ist als jene vom Tauchkolben 15, ergibt sich eine weitere, innerhalb des Arbeitsraums 1 bewirkte Kraftübersetzung zum Arbeitskolben 2 hin und damit die entsprechende Verstellkraft an der Kolbenstange 4.As shown in the drawing, there is a storage space 9 hydraulically connected to the working space 1 above the working space 1, in which a lower one by a storage piston 11 with a storage spring 12 Hydraulic accumulator pressure is generated, which is sufficient to keep the working space 1 filled with hydraulic oil from the storage space 9 during the rapid stroke of the working piston 2. The storage piston 11 is guided in a radially sealing and axially displaceable tube 13. Also radially sealing and axially displaceably guided in this casing tube 13 is a drive piston 14 of a plunger 15, which can be displaced in the direction of the working space 1 against the force of the storage spring 12. The plunger 15 penetrates, radially sealed, the storage piston 11 and dips into the storage space 9. The drive piston 14 with plunger 15 is driven by compressed air, which is conducted into a control chamber 16 above the drive piston 14. This control of compressed air occurs when the working piston 2 has ended its rapid traverse and before the actual pressure stroke of the working piston 2 is to begin. If the drive piston 14 is displaced by the compressed air, after a forward stroke the plunger 15 plunges into a connecting bore 17 leading from the storage space 9 to the work space 1, after which this connection is interrupted by the cooperation of a radial seal 18, so that the plunger 15 is submerged further Hydraulic fluid is displaced into the working space 1 there, with a corresponding action on the working piston 2. Since the cross-sectional area of the drive piston 14 is considerably larger than that of the plunger 15, there is a correspondingly high pressure ratio from the pneumatic pressure in the control chamber 16 to the hydraulic pressure in the working space 1. Since again If the cross-sectional area of the working piston 2 is substantially larger than that of the plunger 15, there is a further force transmission to the working piston 2 within the working space 1 and thus the corresponding adjusting force on the piston rod 4.

Für den Rückhub der Kolbenstange 4 wird der pneumatische Druck im Steuerraum 16 abgebaut, so daß die Speicherfeder 12 den Antriebskolben 14 in die gezeigte Ausgangslage zurückschiebt. Gleichzeitig wird über Druckabbau im Pneumatikraum 7, bzw. Druckaufbau im Pneumatikraum 8 der Arbeitskolben 2 durch den Scheibenkolben 5 wieder in die gezeigte Ausgangslage geschoben, wobei durch den Arbeitskolben 2 Hydraulikflüssigkeit zurück in den Speicherraum 9 verdrängt wird und wobei dort der Speicherkolben 11 entgegen der Kraft der Speicherfeder 12 zurück in die gezeigte Ausgangslage verschoben wird.For the return stroke of the piston rod 4, the pneumatic pressure in the control chamber 16 is reduced, so that the storage spring 12 pushes the drive piston 14 back into the starting position shown. At the same time, the working piston 2 is pushed back into the starting position shown by the disk piston 5 via pressure reduction in the pneumatic chamber 7 or pressure build-up in the pneumatic chamber 8, hydraulic fluid being displaced back into the storage chamber 9 by the working piston 2 and the storage piston 11 being there against the force the storage spring 12 is moved back to the starting position shown.

Erfindungsgemäß ist außer der Verbindungsbohrung 17 zwischen dem Arbeitsraum 1 und dem Speicherraum 9 im Gehäuse 3 ein Verbindungskanal 19 vorgesehen, in dem ein in Richtung Speicherraum 9 sperrndes Rückschlagventil angeordnet ist, mit einem beweglichen Ventilglied 21 und einer Feder 22. Über diesen Kanal 19 kann auch dann noch Hydraulikflüssigkeit vom Speicheraum 9 in den Arbeitsraum 1 strömen, wenn die Verbindungsbohrung 17 durch den Tauchkolben 15 bzw. die Radialdichtung 18 gesperrt ist.According to the invention, in addition to the connecting bore 17 between the working space 1 and the storage space 9 in the housing 3, a connecting channel 19 is provided, in which a check valve blocking in the direction of the storage space 9 is arranged, with a movable valve member 21 and a spring 22 then hydraulic fluid still flows from the storage space 9 into the working space 1 when the connecting bore 17 is blocked by the plunger 15 or the radial seal 18.

Gemäß der in Figur 2 dargestellten Variante der Erfindung dient als Verbinmdungskanal zwischen Speicherraum 9 und Arbeitsraum 1 eine außerhalb des Gehäuses 3 verlaufende Leitung 23, in der ein entsprechend angeordnetes Rückschlagventil mit einem beweglichen Ventilglied 24 und einer Feder 25 angeordnet ist, wobei dieses Rückschlagventil 24, 25 ebenfalls in Richtung Speicherraum 9 sperrt.According to the variant of the invention shown in FIG. 2, the connection channel between the storage space 9 and the working space 1 is a line 23 running outside the housing 3, in which a correspondingly arranged check valve with a movable valve member 24 and a spring 25 is arranged, this check valve 24, 25 also locks towards storage space 9.

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

BezugszahlenlisteList of reference numbers

11
Arbeitsraumworking space
22nd
ArbeitskolbenPiston
33rd
Gehäusecasing
44th
KolbenstangePiston rod
55
ScheibenkolbenDisc piston
66
MantelrohrCasing pipe
77
PneumatikraumPneumatic room
88th
PneumatikraumPneumatic room
99
SpeicherraumStorage space
1010th
1111
SpeicherkolbenAccumulator piston
1212th
SpeicherfederSpring
1313
MantelrohrCasing pipe
1414
AntriebskolbenDrive piston
1515
TauchkolbenPlunger
1616
SteuerraumControl room
1717th
VerbindungsbohrungConnecting hole
1818th
RadialdichtungRadial seal
1919th
VerbindungskanalConnecting channel
2020th
--
2121
bewegliches Ventilgliedmovable valve member
2222
Federfeather
2323
Leitungmanagement
2424th
bewegliches Ventilgliedmovable valve member
2525th
Federfeather

Claims (6)

Hydraulischer Druckübersetzer - mit einem mit Hydraulikflüssigkeit gefüllten Arbeitsraum (3) in einem Aggregatsgehäuse (1) in dem ein Arbeitskolben (2) arbeitet, dessen Kolbenstange (4) nach außerhalb des Gehäuses (1) führt, - mit einem ebenfalls mit Hydraulikflüssigkeit gefüllten Speicherraum (9), welcher mit dem Arbeitsraum (3) hydraulisch verbunden ist und in dieser Verbindung eine Bohrung (17) definierten Querschnitts aufweist, sowie - mit einem Tauchkolben (15) kleineren Durchmessers als der Arbeitskolben (2), welcher nach einem Eilhub des Arbeitskolbens (2) unter niederem Druck und Nachströmen von Hydraulikflüssigkeit aus dem Speicher-raum (9) in den Arbeitsraum (3) radial dichtend in die Bohrung (17) taucht und im Arbeitsraum (3), einen entsprechenden Hochdruck erzeugent, und beim Rückhub wieder aus der Bohrung (17) austaucht, so daß die Hydraulikflüssigkeit vom Arbeitsraum (3) wieder zurück in den Speicherraum (9) strömen kann dadurch gekennzeichnet, daß zwischen Arbeitsraum (3) und Speicherraum (9) außer der die Bohrung (17) aufnehmenden Verbindung ein Verbindungskanal (19, 23) angeordnet ist, welcher bei Eintreten des Hochdrucks gesperrt wird und bei niederem Druck in Strömungsrichtung zum Arbeitsraum (3) hin geöffnet ist.Hydraulic pressure intensifier - With a working space (3) filled with hydraulic fluid in an aggregate housing (1) in which a working piston (2) works, the piston rod (4) of which leads outside the housing (1), - With a likewise filled with hydraulic fluid storage space (9) which is hydraulically connected to the working space (3) and in this connection has a bore (17) of defined cross section, and - With a plunger (15) of smaller diameter than the working piston (2), which after a rapid stroke of the working piston (2) under low pressure and afterflow of hydraulic fluid from the storage chamber (9) into the working chamber (3) radially sealing in the Bore (17) dips and generates a corresponding high pressure in the work area (3) and emerges again from the bore (17) on the return stroke, so that the hydraulic fluid can flow back into the storage area (9) from the work area (3) characterized in that between the working space (3) and the storage space (9) in addition to the connection receiving the bore (17) there is a connecting channel (19, 23) which is blocked when the high pressure occurs and at low pressure in Flow direction to the work area (3) is open. Hydraulischer Druckübersetzer nach Anspruch 1, dadurch gekennzeichnet, daß im Verbindungskanal (19, 23) ein in Richtung Arbeitsraum (3) öffnendes und in Richtung Speicherraum (9) schließendes Rückschlagventil (21, 22, 24, 25) angeordnet ist.Hydraulic pressure intensifier according to Claim 1, characterized in that a check valve (21, 22, 24, 25) which opens in the direction of the working space (3) and closes in the direction of the storage space (9) is arranged in the connecting channel (19, 23). Hydraulischer Druckübersetzer nach Anspruch 2, dadurch gekennzeichnet, daß das bewegliche Ventilglied (21, 24) des Rückschlagventils durch eine Feder (22, 25) belastet ist.Hydraulic pressure intensifier according to claim 2, characterized in that the movable valve member (21, 24) of the check valve is loaded by a spring (22, 25). Hydraulischer Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Verbindungskanal (19) im Gehäuse (1) verläuft.Hydraulic pressure intensifier according to one of the preceding claims, characterized in that the connecting channel (19) runs in the housing (1). Hydraulischer Druckübersetzer nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Verbindungskanal durch eine im wesentlichen außerhalb des Gehäuses verlaufende Leitung (23) gebildet wird.Hydraulic pressure intensifier according to one of claims 1 to 3, characterized in that the connecting channel is formed by a line (23) running essentially outside the housing. Hydraulischer Druckübersetzer nach einem der vorhergehenden Ansprüche, gekennzeichnet als hydropneumatischer Druckübersetzer mit folgenden Merkmalen: - achsgleiche bzw achsparallele Anordnung von Arbeitskolben (2), und Arbeitsraum (3) einerseits, Bohrung (17), Speicherraum (9) und Tauchkolben (15) anderterseits; - Betätigung des Tauchkolbens (15) entgegen einer Rückstellkraft (12) durch einen pneumatisch beaufschlagten Antriebskolben (14); - einer die Verbindung aufnehmende Querwand zwischen Arbeitsraum (3) und Speicherraum (9), in der die Bohrung (17) enthalten ist, wobei in der Bohrung (17) eine hochdruckgeeignete Lippendichtung (18) vorhanden ist; - einem den Speicherdruck erzeugenden, pneumatisch oder mechanisch belasteten, axial verschiebbaren und radial dichtenden Speicherkolben (11), der den Speicherraum (9) von einem luftgefüllten Raum trennt und - einem Hilfskolben (5) (Scheibenkolben auf dem Arbeitskolben (2)), der für die Eilgange beiderseits abwechselnd pneumatisch druckbeaufschlagbar ist. Hydraulic pressure intensifier according to one of the preceding claims, characterized as a hydropneumatic pressure intensifier with the following features: - Axial or parallel arrangement of the working piston (2) and working space (3) on the one hand, bore (17), storage space (9) and plunger (15) on the other; - Actuation of the plunger (15) against a restoring force (12) by a pneumatically actuated drive piston (14); - A transverse wall receiving the connection between the working space (3) and the storage space (9), in which the bore (17) is contained, a lip seal (18) suitable for high pressure being present in the bore (17); - A pneumatically or mechanically loaded, axially displaceable and radially sealing storage piston (11) generating the storage pressure, which separates the storage space (9) from an air-filled space and - An auxiliary piston (5) (disc piston on the working piston (2)), which can be pressurized alternately on both sides for the rapid traverse.
EP93107954A 1992-07-02 1993-05-15 Hydropneumatic pressure transformer Expired - Lifetime EP0577955B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4221638 1992-07-02
DE4221638A DE4221638B4 (en) 1992-07-02 1992-07-02 Method for a hydraulic pressure booster

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EP0577955B1 EP0577955B1 (en) 1997-04-09

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JP (1) JPH06213202A (en)
KR (1) KR100292553B1 (en)
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DE (2) DE4221638B4 (en)
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CA2099469A1 (en) 1994-01-03
DE4221638B4 (en) 2005-11-03
CA2099469C (en) 1999-09-21
EP0577955B1 (en) 1997-04-09
DE59306086D1 (en) 1997-05-15
KR940002509A (en) 1994-02-17
ATE151504T1 (en) 1997-04-15
US5381661A (en) 1995-01-17
KR100292553B1 (en) 2001-06-01
JPH06213202A (en) 1994-08-02
DE4221638A1 (en) 1994-03-03
ES2101160T3 (en) 1997-07-01
DK0577955T3 (en) 1997-10-20

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