EP0043865B1 - Hydraulic oscillating-piston drive - Google Patents

Hydraulic oscillating-piston drive Download PDF

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Publication number
EP0043865B1
EP0043865B1 EP80104075A EP80104075A EP0043865B1 EP 0043865 B1 EP0043865 B1 EP 0043865B1 EP 80104075 A EP80104075 A EP 80104075A EP 80104075 A EP80104075 A EP 80104075A EP 0043865 B1 EP0043865 B1 EP 0043865B1
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EP
European Patent Office
Prior art keywords
shaft
piston
steps
axial
housing
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Expired
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EP80104075A
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German (de)
French (fr)
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EP0043865A1 (en
Inventor
Marlies Meyer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schuett Friedrich
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Schuett Friedrich
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Publication date
Application filed by Schuett Friedrich filed Critical Schuett Friedrich
Priority to DE8080104075T priority Critical patent/DE3067255D1/en
Priority to AT80104075T priority patent/ATE6881T1/en
Priority to EP80104075A priority patent/EP0043865B1/en
Publication of EP0043865A1 publication Critical patent/EP0043865A1/en
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Publication of EP0043865B1 publication Critical patent/EP0043865B1/en
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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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type

Definitions

  • the invention relates to a hydraulic swivel piston drive, in particular for working pressures above 100 bar, with a stepped central swivel shaft in a cross-divided housing, which has a standing piston, with between two shaft stages in an annular cylinder space, which is between the two shaft stages, the central shaft piece lying in between and the housing is delimited, a hydraulic swivel piston is arranged detachably and is connected to the shaft by an axial fastening element in the form of a threadless cylindrical pin with 0-rings at the ends.
  • a hydraulic swivel piston drive of the type described above which has a one-piece axial fastening element for the swivel piston.
  • This axial fastening element allows the pivoting piston to rotate around the fastening element, so that the pressure of the medium causes the pivoting piston to be supported on the pivot shaft as a result of its pivoting and thereby increases the sealing effect.
  • the axial fastening element is not locked in relation to the swivel shaft and, like the standing piston, allows axial mobility.
  • the axial mobility of the standing piston as well as the pivoting mobility of the pivoting piston serve to increase the sealing effect of the overall system.
  • the axial fastening element is formed in two parts, the two parts being threadless cylindrical pins which have axial locking elements at their ends for securing against axial displacement in the bores of the shaft steps and between the cylinder pins and their bores in the shaft steps there is an undersize, so that the pivoting piston having a circumferential seal can be moved radially with respect to the shaft within predetermined limits.
  • This configuration of the axial fastening element ensures that the pivoting piston cannot carry out any self-rotating movement, but only a radial movement according to the invention.
  • This radial movement according to the invention which is only permissible because the pivoting piston has a circumferential elastic seal, is considerably more favorable for the service life of the drive and for the tightness of the overall system, as has surprisingly been shown.
  • Plastic deformations of the swivel shaft, the swivel and the standing piston are avoided with certainty. At the same time, a non-contact movement sequence is possible.
  • a further embodiment of the invention provides that the width of the gaps is between 0.02 and 0.05 mm and that the gaps are sealed to the outside by a compact seal.
  • the surface of the shaft stages in the gap and sealing area is hardened, in particular nitrided. In this way it is achieved that in the initial state, if the dynamic centering of the swivel shaft has not yet taken place, no seizure is possible if the shaft and housing come into contact.
  • Fig. 1 denotes the output-side housing half and 2 the opposite housing half, which are preferably screwed together using Allen screws 3.
  • the O-ring 4 is used to seal the housing halves 1 and 2.
  • Inside the housing 1, 2 there is the central pivot shaft 5 with the toothing part 6, via which the torque is transmitted to the machine.
  • the pivoting piston 8 which has the shape of a toroidal section.
  • the cylindrical pins 7 have an undersize in relation to their bores in the shaft 5 and are secured at their ends against axial displacement by the O-rings 9 and by simple fastening means, for example a punch marking 10.
  • the pivoting piston 8 is thus fastened such that it can be moved slightly in the radial direction within the predetermined limits of the undersize.
  • the swinging piston shaft system is therefore not completely rigid. This advantageously improves the operating behavior and in particular the durability of the drive according to the invention.
  • the sealing gap 12 which together with the compact seals 11 ensures a complete seal of the cylinder space 13 with respect to the roller bearings 14 and 15.
  • the tightness achieved by the sealing gap 12 and the compact seals is so great that it is not necessary to ensure that leakage oil is returned.
  • the amount of leak oil is so small that it is not noticeable.
  • roller bearings 14 and 15 are clamped to the housing parts 1 and 2 by means of clamping screws 16 and 17 and are designed as self-lubricating bearings with permanent grease lubrication. To prevent the ingress of dust or splash water, etc., the housing still has the bearing seal 18 on the outside.
  • the standing piston 19 is fastened with a bolt 20 in the housing part 1, which advantageously has a longitudinal pressure compensation bore.
  • the hydraulic swivel piston drive can be screwed to a driven machine or to a stand via the bolt holes 21.
  • FIG. 2 shows in particular the arrangement of the seals 22 of the standing piston 8.
  • These are simple ring seals which seal the pivoting piston or the standing piston against both the housing and the central pivot shaft.
  • the pressure oil supply line 25 opens, which corresponds to the only indicated pressure oil supply line on the other side of the standing piston.
  • the fastening bolt 20 of the standing piston 19 is screwed into the opening 26.
  • the hydraulic rotary piston drive shown in FIGS. 1 and 2 is designed in its dimensioning of the individual parts for a working pressure of 150 bar and a test pressure of 180 bar. Without departing from the scope of the invention, however, it is also possible to switch to larger or smaller pressures. In all cases, the fastening of the pivoting piston 8 on the shaft 5 via a pair of axial cylindrical pins 7 results in the pivoting piston 8 being fastened, which is elastic as far as necessary and yet can reliably transmit a high torque according to the task. The service life and stability of the drive are significantly improved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Braking Systems And Boosters (AREA)
  • Valve Device For Special Equipments (AREA)
  • Clamps And Clips (AREA)

Abstract

1. Hydraulic swivel piston drive, especially for working pressures exceeding 100 bar, with a stepped central swivel shaft (5, 5a) in a cross-divided housing (1, 2) that has a stand piston (19), a detachable hydraulic swivel piston (8) being arranged between two shaft steps (5a) in a circular cylinder chamber (13) that is limited by the two shaft steps (5a), the central shaft section in between and the housing (1, 2) and jointed to the shaft (5, 5a) by means of an axial fastener (7) in the form of a cylindrical pin without thread with O-rings (9) at the ends, characterized in that the axial fastener is of two-part design, the two parts being cylindrical pins without thread (7) provided with axial blocking elements (10) at their ends to prevent axial shifting in the bores of the shaft steps (5a), the cylindrical pins being undersized as against their bores in the shaft steps (5a) so that the swivel piston (8) that is surrounded by a sealing (22) can move radially within the set limits towards the shaft (5, 5a).

Description

Die Erfindung betrifft einen Hydraulik-Schwenkkolbenantrieb, insbesondere für Arbeitsdrücke über 100 bar, mit einer gestuften zentralen Schwenkwelle in einem quergeteilten Gehäuse, das einen Standkolben aufweist, wobei zwischen zwei Wellenstufen in einem kreisringförmigen Zylinderraum, der von den beiden Wellenstufen, dem dazwischen liegenden zentralen Wellenstück und dem Gehäuse gegrenzt wird, ein Hydraulik-Schwenkkolbenlösbar angeordnet und durch ein Axial-Befestigungselement in gewindeloser Zylinderstiftform mit 0- Ringen an den Enden mit der Welle verbunden ist.The invention relates to a hydraulic swivel piston drive, in particular for working pressures above 100 bar, with a stepped central swivel shaft in a cross-divided housing, which has a standing piston, with between two shaft stages in an annular cylinder space, which is between the two shaft stages, the central shaft piece lying in between and the housing is delimited, a hydraulic swivel piston is arranged detachably and is connected to the shaft by an axial fastening element in the form of a threadless cylindrical pin with 0-rings at the ends.

Aus der DE-A Nr. 2321043 ist ein Hydraulik-Schwenkkolbenantrieb der vorbeschriebenen Art bekannt, der ein einteiliges Axial-Befestigungselement für den Schwenkkolben aufweist. Dieses Axial-Befestigungselement erlaubt dem Schwenkkolben, sich um das Befestigungselement zu drehen, so dass der Druck des Mediums bewirkt, dass sich der Schwenkkolben infolge seines Schwenkens auf der Schwenkwelle abstützt und dadurch die Dichtwirkung erhöht. Das Axial-Befestigungselement ist gegenüber der Schwenkwelle nicht arretiert und erlaubt ebenso wie der Standkolben eine axiale Beweglichkeit. Hierbei dient die axiale Beweglichkeit des Standkolbens ebenso wie die Schwenkbeweglichkeit des Schwenkkolbens einer Erhöhung der Dichtwirkung des Gesamtsystems.From DE-A No. 2321043, a hydraulic swivel piston drive of the type described above is known, which has a one-piece axial fastening element for the swivel piston. This axial fastening element allows the pivoting piston to rotate around the fastening element, so that the pressure of the medium causes the pivoting piston to be supported on the pivot shaft as a result of its pivoting and thereby increases the sealing effect. The axial fastening element is not locked in relation to the swivel shaft and, like the standing piston, allows axial mobility. The axial mobility of the standing piston as well as the pivoting mobility of the pivoting piston serve to increase the sealing effect of the overall system.

Es ist Aufgabe der Erfindung, einen gattungsgleichen Hydraulik-Schwenkkolbenantrieb anzugeben, bei dem die Dichtigkeit des Gesamtsystems weiter erhöht wird, die Lebensdauer der einzelnen Elemente steigt und insbesondere plastische Verformungen der Schwenkwelle, des Schwenk- und des Standkolbens mit Sicherheit vermieden werden.It is an object of the invention to provide a hydraulic swivel piston drive of the same type, in which the tightness of the overall system is further increased, the service life of the individual elements increases and, in particular, plastic deformations of the swivel shaft, the swivel and the standing piston are avoided with certainty.

Die Aufgabe wird dadurch gelöst, dass das Axial-Befestigungselement zweiteilig ausgebildet ist, wobei die beiden Teile gewindelose Zylinderstifte sind, die an ihren Enden Axialarretierungselemente zur Sicherung gegen axiales Verschieben in den Bohrungen der Wellenstufen aufweisen und wobei zwischen den Zylinderstiften und ihren Bohrungen in den Wellenstufen ein Untermass besteht, so dass der eine umlaufende Dichtung aufweisende Schwenkkolben gegenüber der Welle radial in vorgegebenen Grenzen beweglich ist.The object is achieved in that the axial fastening element is formed in two parts, the two parts being threadless cylindrical pins which have axial locking elements at their ends for securing against axial displacement in the bores of the shaft steps and between the cylinder pins and their bores in the shaft steps there is an undersize, so that the pivoting piston having a circumferential seal can be moved radially with respect to the shaft within predetermined limits.

Durch diese Ausbildung des Axial-Befestigungselements wird erreicht, dass der Schwenkkolben keine Eigendrehbewegung ausführen kann, sondern nur noch erfindungsgemäss eine radiale Bewegung. Diese erfindungsgemässe radiale Bewegung, die nur zulässig ist, da der Schwenkkolben eine umlaufende elastische Dichtung aufweist, ist für die Lebensdauer des Antriebs und für die Dichtigkeit des Gesamtsystems, wie sich Überraschenderweise gezeigt hat, wesentlich günstiger. Plastische Verformungen der Schwenkwelle, des Schwenk- und des Standkolbens werden mit Sicherheit vermieden. Gleichzeitig ist ein berührungsfreier Bewegungsablauf möglich.This configuration of the axial fastening element ensures that the pivoting piston cannot carry out any self-rotating movement, but only a radial movement according to the invention. This radial movement according to the invention, which is only permissible because the pivoting piston has a circumferential elastic seal, is considerably more favorable for the service life of the drive and for the tightness of the overall system, as has surprisingly been shown. Plastic deformations of the swivel shaft, the swivel and the standing piston are avoided with certainty. At the same time, a non-contact movement sequence is possible.

In weiterer Ausgestaltung der Erfindung ist vorgesehen, dass je ein Spalt beidseitig neben dem Zylinderraum zwischen Gehäuse und den Umfangsflächen der Wellenstufen vorhanden ist, der etwa so gross ist wie das Untermass der Zylinderstifte gegenüber ihren Bohrungen in den Wellenstufen. Auf diese Art und Weise ergibt sich sehr vorteilhaft eine Ausbildung von Dichtspalten beidseitig neben dem Zylinderraum, dessen Grösse ein Fressen des Schwenkkolbens ausschliesst. In der Arbeitsstellung befindet sich der Schwenkkolben in einer mittleren Stellung im Zylinderraum, da sich durch die symmetrische Ausbildung ein hydrodynamisches Gleichgewicht zwischen Innen- und Aussenseite des Schwenkkolbens einstellt.In a further embodiment of the invention, there is a gap on both sides next to the cylinder space between the housing and the circumferential surfaces of the shaft steps, which is approximately as large as the undersize of the cylindrical pins compared to their bores in the shaft steps. In this way, there is very advantageously a formation of sealing gaps on both sides next to the cylinder space, the size of which prevents the pivoting piston from seizing. In the working position, the swivel piston is in a middle position in the cylinder chamber, since the symmetrical design creates a hydrodynamic balance between the inside and outside of the swivel piston.

I n weiterer Ausgestaltung der Erfindung ist vorgesehen, dass die Weite der Spalte zwischen 0,02 und 0,05 mm beträgt und dass die Spalte nach aussen durch eine Kompaktdichtung abgedichtet sind. Überraschenderweise hat sich ergeben, dass eine einfache kostengünstige Kompaktdichtung bei der hohen Bewegungsgewindigkeit des Schwenkkolbens und der Schwenkwelle eine dynamische, automatische Stabilisierung der Schwenkwelle im Gehäuse ergibt. Hierbei wirkt der Spalt neben dem Zylinderraum wie der Spalt zwischen Welle und Lagerschale eines Gleitlagers. Die Kompaktdichtung kann daher relativ unelastisch sein, ohne ihre sehr gut dichtende Wirkung zu verlieren. So ergibt sich ein minimaler Leck- ölanfall, der keine Leckölrückführung notwendig macht.A further embodiment of the invention provides that the width of the gaps is between 0.02 and 0.05 mm and that the gaps are sealed to the outside by a compact seal. Surprisingly, it has been found that a simple, inexpensive compact seal with the high movement speed of the swivel piston and the swivel shaft results in dynamic, automatic stabilization of the swivel shaft in the housing. The gap next to the cylinder space acts like the gap between the shaft and the bearing shell of a plain bearing. The compact seal can therefore be relatively inelastic without losing its very good sealing effect. This results in a minimal amount of leakage oil, which makes no leakage oil return necessary.

In weiterer Ausgestaltung der Erfindung ist vorgesehen, dass die Oberfläche der Wellenstufen im Spalt- und Dichtungsbereich gehärtet, insbesondere nitriergehärtet ist. Auf diese Art und Weise wird erreicht, dass im Anfangszustand, wenn die dynamische Zentrierung der Schwenkwelle noch nicht erfolgt ist, kein Fressen bei einer eventuellen Berührung von Welle und Gehäuse möglich ist.In a further embodiment of the invention, it is provided that the surface of the shaft stages in the gap and sealing area is hardened, in particular nitrided. In this way it is achieved that in the initial state, if the dynamic centering of the swivel shaft has not yet taken place, no seizure is possible if the shaft and housing come into contact.

Die Erfindung wird anhand von Zeichnungen näher erläutert, die ein besonders bevorzugtes Ausführungsbeispiel zeigen und aus denen weitere vorteilhafte Einzelheiten entnehmbar sind.The invention is explained in more detail with reference to drawings which show a particularly preferred exemplary embodiment and from which further advantageous details can be found.

Die Zeichnungen zeigen im einzelnen:

  • in Fig. 1 einen Teillängsschnitt durch den Hydraulik-Schwenkkolbenantrieb, und
  • in Fig. 2 einen Teilquerschnitt durch den Hydraulic-Schwenkkolbenantrieb.
The drawings show in detail:
  • in Fig. 1 shows a partial longitudinal section through the hydraulic swing piston drive, and
  • in Fig. 2 a partial cross section through the hydraulic swing piston drive.

In Fig. 1 bezeichnet 1 die abtriebsseitige Gehäusehälfte und 2 die gegenüberliegende Gehäusehälfte, die vorzugsweise über Innensechskantschrauben 3 miteinander verschraubt sind. Zur Abdichtung der Gehäusehälften 1 und 2 dient der O-Ring 4. Im Inneren des Gehäuses 1,2 befindet sich die zentrale Schwenkwelle 5 mit dem Verzahnungsteil 6, über den das Drehmoment auf die Arbeitsmaschine übertragen wird.In Fig. 1, 1 denotes the output-side housing half and 2 the opposite housing half, which are preferably screwed together using Allen screws 3. The O-ring 4 is used to seal the housing halves 1 and 2. Inside the housing 1, 2 there is the central pivot shaft 5 with the toothing part 6, via which the torque is transmitted to the machine.

Über die Zylinderstifte 7 in vorgegebenen Grenzen mit der Welle 5 radial beweglich verbunden ist der Schwenkkolben 8, der die Form eines Torusabschnittes aufweist. Die Zylinderstifte 7 weisen erfindungsgemäss ein Untermass gegenüber ihren Bohrungen in der Welle 5 auf und sind an ihren Enden durch die O-Ringe 9 und durch einfache Befestigungsmittel, z.B. eine Körnermarkierung 10, gegen axiales Verschieben gesichert. So ergibt sich eine Befestigung des Schwenkkolbens 8 derart, dass der in radialer Richtung geringfügig in den vorgegebenen Grenzen des Untermasses beweglich ist. Das Schwenkkolben-Wellen-System ist also nicht völlig starr. Dies verbessert vorteilhaft das Betriebsverhalten und insbesondere die Dauerhaltbarkeit des erfindungsgemässen Antriebs wesentlich.About the cylinder pins 7 in predetermined sizes zen with the shaft 5 is radially movably connected to the pivoting piston 8, which has the shape of a toroidal section. According to the invention, the cylindrical pins 7 have an undersize in relation to their bores in the shaft 5 and are secured at their ends against axial displacement by the O-rings 9 and by simple fastening means, for example a punch marking 10. The pivoting piston 8 is thus fastened such that it can be moved slightly in the radial direction within the predetermined limits of the undersize. The swinging piston shaft system is therefore not completely rigid. This advantageously improves the operating behavior and in particular the durability of the drive according to the invention.

Zwischen dem Zentralwellenteil 5a mit grossem Durchmesser und den Gehäusehälften 1 und 2 befindet sich auf der Innenseite der Kompaktdichtungen 11 der Dichtungsspalt 12, der zusammen mit den Kompaktdichtungen 11 für eine vollständige Abdichtung des Zylinderraumes 13 gegenüber den Rollenlagern 14 und 15 sorgt. Überraschenderweise ist die durch den Dichtungsspalt 12 und die Kompaktdichtungen erreichte Dichtigkeit so gross, dass für eine Rückführung von Leck- öl nicht gesorgt zu werden braucht. Die Leckölmenge ist so gering, dass sie sich nicht bemerkbar macht.Between the central shaft part 5a with a large diameter and the housing halves 1 and 2 is located on the inside of the compact seals 11, the sealing gap 12, which together with the compact seals 11 ensures a complete seal of the cylinder space 13 with respect to the roller bearings 14 and 15. Surprisingly, the tightness achieved by the sealing gap 12 and the compact seals is so great that it is not necessary to ensure that leakage oil is returned. The amount of leak oil is so small that it is not noticeable.

Die Rollenlager 14 und 15 sind durch Spannschrauben 16 und 17 mit den Gehäuseteilen 1 und 2 verspannt und als selbstschmierende Lager mit Dauerfettschmierung ausgebildet. Zur Vermeidung des Eintritts von Staub- oder Spritzwasser usw. weist das Gehäuse aussen noch die Lagerdichtung 18 auf.The roller bearings 14 and 15 are clamped to the housing parts 1 and 2 by means of clamping screws 16 and 17 and are designed as self-lubricating bearings with permanent grease lubrication. To prevent the ingress of dust or splash water, etc., the housing still has the bearing seal 18 on the outside.

Der Standkolben 19 ist mit einem Bolzen 20 in dem Gehäuseteil 1 befestigt, der vorteilhaft eine längsverlaufende Druckausgleichsbohrung aufweist. Über die Bolzenlöcher 21 kann der Hydraulik-Schwenkkolbenantrieb an eine Arbeitsmaschine oder an einen Ständer angeschraubt werden.The standing piston 19 is fastened with a bolt 20 in the housing part 1, which advantageously has a longitudinal pressure compensation bore. The hydraulic swivel piston drive can be screwed to a driven machine or to a stand via the bolt holes 21.

Fig. 2 zeigt insbesondere die Anordnung der Dichtungen 22 des Standkolbens 8. Es handelt sich um einfache Ringdichtungen, die den Schwenk- bzw. den Standkolben sowohl gegenüber dem Gehäuse als auch gegenüber der zentralen Schwenkwelle abdichten. In die Ecken 23 des Standkolbens 19 bzw. in Anschlagposition auch in die Ecke 24 des Schwenkkolbens 8 mündet die Druckölzu- bzw. -ableitung 25 ein, der auf der anderen Seite des Standkolbens die nur angedeutete Druckölzuleitung entspricht. In die Öffnung 26 wird der Befestigungsbolzen 20 des Standkolbens 19 eingeschraubt.2 shows in particular the arrangement of the seals 22 of the standing piston 8. These are simple ring seals which seal the pivoting piston or the standing piston against both the housing and the central pivot shaft. In the corners 23 of the standing piston 19 or in the stop position also in the corner 24 of the pivoting piston 8, the pressure oil supply line 25 opens, which corresponds to the only indicated pressure oil supply line on the other side of the standing piston. The fastening bolt 20 of the standing piston 19 is screwed into the opening 26.

Der in den Fig. 1 und 2 gezeigte Hydraulik-Schwenkkolbenantrieb ist in seiner Bemessung der Einzelteile für einen Arbeitsdruck von 150 bar und einen Prüfdruck von 180 bar ausgelegt. Ohne den Rahmen der Erfindung zu verlassen, kann jedoch auch auf grössere oder kleinere Drücke übergegangen werden. In allen Fällen wird durch die Befestigung des Schwenkkolbens 8 auf der Welle 5 über ein Paar von axialen Zylinderstiften 7 eine Befestigung des Schwenkkolbens 8 erreicht, die soweit wie nötig elastisch ist und doch aufgabengemäss ein hohes Drehmoment sicher übertragen kann. Dabei werden die Lebensdauer und die Standfestigkeit des Antriebs erheblich verbessert.The hydraulic rotary piston drive shown in FIGS. 1 and 2 is designed in its dimensioning of the individual parts for a working pressure of 150 bar and a test pressure of 180 bar. Without departing from the scope of the invention, however, it is also possible to switch to larger or smaller pressures. In all cases, the fastening of the pivoting piston 8 on the shaft 5 via a pair of axial cylindrical pins 7 results in the pivoting piston 8 being fastened, which is elastic as far as necessary and yet can reliably transmit a high torque according to the task. The service life and stability of the drive are significantly improved.

Claims (4)

1. Hydraulic swivel piston drive, especially for working pressures exceeding 100 bar, with a stepped central swivel shaft (5, 5a) in a cross- divided housing (1, 2) that has a stand piston (19), a detachable hydraulic swivel piston (8) being arranged between two shaft steps (5a) in a circular cylinder chamber (13) that is limited by the two shaft steps (5a), the central shaft section in between and the housing (1, 2) and jointed to the shaft (5, 5a) by means of an axial fastener (7) in the form of a cylindrical pin without thread with 0-rings (9) at the ends, characterized in that the axial fastener is of two-part design, the two parts being cylindrical pins without thread (7) provided with axial blocking elements (10) at their ends to prevent axial shifting in the bores of the shaft steps (5a), the cylindrical pins being undersized as against their bores in the shaft steps (5a) so that the swivel piston (8) that is surrounded by a sealing (22) can move radially within the set limits towards the shaft (5, 5a).
2. Hydraulic swivel piston drive according to claim 1, characterized in that there is a gap (12) on both sides of the cylinder chamber (13) between housing (1, 2) and the peripheral areas of the shaft steps (5a) that roughly corresponds to the measure of undersize of the cylindrical pins (7) as against their bores in the shaft steps.
3. Hydraulic swivel piston drive according to claim 2, characterized in that the width of the gap (12) ranges between 0.02 and 0.05 mm and the gap (12) is sealed to the outward by means of a compact packing (11).
4. Hydraulic swivel piston drive according to one of the above claims, characterized in that the surfaces of the shaft steps (5a) are hardened, especially nitrogen-hardened in the gap and sealing area.
EP80104075A 1980-07-14 1980-07-14 Hydraulic oscillating-piston drive Expired EP0043865B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE8080104075T DE3067255D1 (en) 1980-07-14 1980-07-14 Hydraulic oscillating-piston drive
AT80104075T ATE6881T1 (en) 1980-07-14 1980-07-14 HYDRAULIC SWING PISTON DRIVE.
EP80104075A EP0043865B1 (en) 1980-07-14 1980-07-14 Hydraulic oscillating-piston drive

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP80104075A EP0043865B1 (en) 1980-07-14 1980-07-14 Hydraulic oscillating-piston drive

Publications (2)

Publication Number Publication Date
EP0043865A1 EP0043865A1 (en) 1982-01-20
EP0043865B1 true EP0043865B1 (en) 1984-03-28

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EP80104075A Expired EP0043865B1 (en) 1980-07-14 1980-07-14 Hydraulic oscillating-piston drive

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EP (1) EP0043865B1 (en)
AT (1) ATE6881T1 (en)
DE (1) DE3067255D1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107100912B (en) * 2017-05-12 2018-07-20 广东顺德朗途精密制造有限公司 A kind of double hydraulic cylinder operated all-around mobile hydraulic cylinder device

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2459475A (en) * 1943-12-02 1949-01-18 Fred K Van Almelo Differential pressure fluid servomotor
US3198090A (en) * 1962-10-22 1965-08-03 Houdaille Industries Inc Rotary hydraulic actuator comprising a one-piece unitary body and mounting end portion
FR2097456A5 (en) * 1970-07-07 1972-03-03 Tranchant Mecanique Sa
DE2321043C3 (en) * 1973-04-26 1978-11-02 Suedhydraulik Marktoberdorf/Allgaeu Steinbach Kg, 8952 Marktoberdorf Rotary piston cylinder
DE2843610C2 (en) * 1978-10-06 1983-04-07 Schütt, Friedrich, 4755 Holzwickede Swing piston hydraulic drive

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DE3067255D1 (en) 1984-05-03
ATE6881T1 (en) 1984-04-15
EP0043865A1 (en) 1982-01-20

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