EP1488111B1 - Linear, hydraulic pivot drive - Google Patents

Linear, hydraulic pivot drive Download PDF

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Publication number
EP1488111B1
EP1488111B1 EP03718601A EP03718601A EP1488111B1 EP 1488111 B1 EP1488111 B1 EP 1488111B1 EP 03718601 A EP03718601 A EP 03718601A EP 03718601 A EP03718601 A EP 03718601A EP 1488111 B1 EP1488111 B1 EP 1488111B1
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EP
European Patent Office
Prior art keywords
piston
linear
pivot drive
drive according
output shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
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EP03718601A
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German (de)
French (fr)
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EP1488111A1 (en
Inventor
Ulf Breuer
Peter JÄNKER
Thomas Lorkowski
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Airbus Defence and Space GmbH
Airbus Operations GmbH
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EADS Deutschland GmbH
Airbus Operations GmbH
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Publication of EP1488111A1 publication Critical patent/EP1488111A1/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
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/068—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the helical type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating

Definitions

  • the present invention relates to a linear, hydraulic pivot drive according to the preamble of claim 1.
  • Such linear drives find e.g. for flap control aerodynamic Profile application. It is particularly advantageous that on conventional linkage or control rods that are outside the aerodynamic profile on the control flap are hinged and thus adversely affect the aerodynamic conditions, can be waived.
  • a well-known drive for controlling a rotor blade aileron for example, in GB 2 299 562 A.
  • To implement a hydraulically induced Axial movement of a shaft in a rotary motion is the shaft with a coarse thread Mistake.
  • the coarse thread engages in several bushes, concentric the shaft surrounded so that the bushings undergo a rotation during axial displacement of the shaft.
  • a torque support of the shaft is required to turn their To prevent rotation effectively.
  • This causes, which holds the shaft.
  • the mechanism includes several components, below Other separate holes in which the shaft are inserted, and retaining pins. A Such arrangement not only has relatively large dimensions, but also leads to intensive assembly and maintenance work.
  • mini flaps which differs from conventional flaps with 10 - Distinguish 30% clean wing depth by a depth of only 1-3% have and as in a Sp Rudklappe from a fixed and a consisted part.
  • An aerodynamic profile with such Mini flap is for example in our unpublished patent application DE 101 56th 733 described.
  • a deflection of the mini flap with conventional levers would not only unfavorable flow conditions bring with it, but also a high Weight, as several levers would be required. Likewise, a high montagesowie Maintenance required.
  • the flap actuator should be on a greater integration of the functional tasks of drive and load-bearing structure be aligned. In addition, there is a linear or area force or power distribution desirable to meet the flap specific requirements.
  • the object of the present invention is to provide a linear, To create hydraulic rotary actuator, which has a small size and a simple structure, so that it can be integrated into existing structures and low maintenance required.
  • a linear, hydraulic rotary actuator the a housing with connections for introducing a hydraulic medium comprises, a within the housing arranged piston, which by the action of the hydraulic Medium is axially displaceable, as well as provided with steep threads output shaft, which cooperates with the piston to the axial movement of the piston in a To transmit rotational movement, and according to the invention is characterized in that the output shaft is inserted in the piston, the coarse thread in the same direction are formed and engage in the piston, and that the piston cross section a Has polygon profile to effectively prevent a rotational movement of the piston.
  • the piston cross section in the form of a polygon profile is the Torque support for preventing rotation of the piston by itself guaranteed.
  • the polygon profile is in the engagement region of Output shaft and piston provided, i. in the cross-sectional area of the piston, where Output shaft and piston engage each other.
  • the polygon profile be formed along the entire piston.
  • the polygon profile is a P4C profile according to DIN standard.32712. It is particularly advantageous that the axial Displacement under torque is ensured. In this way are none additional mechanisms and components required to turn the piston to prevent. A simple structure is guaranteed. Furthermore, it is advantageous that by Such an embodiment of the rotary actuator much smaller than known Arrangements is. It is particularly useful in this case that the output shaft on both sides is introduced into the piston.
  • the output shaft has two separate sections has, at their respectively engaging in the piston ends the same direction Steep thread are arranged. In this way it is achieved that the direction of rotation of the Output shaft sections is identical.
  • the output shaft sections are rotationally symmetric via a spacer pin interconnected, wherein the spacer pin in each in the Output shaft sections provided holes is introduced. This is especially true With regard to assembly and maintenance advantageous.
  • the piston is provided on both sides with threaded bushes into which the Steep thread of the output shaft sections engage.
  • threaded bushes into which the Steep thread of the output shaft sections engage.
  • the piston has a central bore through which the Distance pin is performed.
  • the spacer pin is stored in a simple manner.
  • a bearing can be arranged in the central bore.
  • axial-radial bearings preferably rolling bearings, for storing the Output shaft provided.
  • Alternative can be the axial and radial components as well be formed separately. These bearings allow a good reception of both axial as well as radial forces.
  • the hydraulic medium can be introduced bidirectionally into the housing is what pivoting a hinged to the housing flap in allows different directions.
  • the pivoting drive according to the invention finds particular to Klappenauslenkung Rotor blades or aircraft wings use. It is particularly advantageous the drive in a hinge connection of a hinged to an aerodynamic profile Integrate flap, with a plurality of such drives linear in the Articulated connection is integrated.
  • the drive comprises a housing 2, the two terminals 3, 4 for a hydraulic medium (e.g., a fluid). Inside the housing 2 is a piston 5 and arranged with the piston 5 in connection with the output shaft 6. to better illustration, the housing 2 and the piston 5 in Figure 1 partially in shown sectional view.
  • the output shaft 6 is inserted on both sides.
  • the output shaft 6 is preferably at least two separate sections 6a, 6b. Each engaging in the piston 5 ends of the Output shaft sections 6a, 6b are with co-rotating coarse threads 8a, 8b Mistake. By the co-trained coarse thread 8a, 8b ensures that the direction of rotation of the two output shaft sections 6a, 6b is identical, as follows will be described in more detail.
  • the piston 5 is correspondingly threaded on both sides 5a, 5b provided to the engagement of the drive shaft sections 6a, 6b in the piston 5 to guarantee.
  • the threads 5a, 5b are in the form of threaded bushings designed.
  • the two output shaft sections 6a, 6b over a spacer pin 7 rotationally symmetrical with each other (Fig. 2).
  • the Piston 5 is provided with a central bore 10 in which the spacer pin 7, preferably using a sealing ring 11, stores.
  • the spacer pin 7 is in corresponding, introduced in the output shaft sections 6a, 6b holes 9a, 9b introduced.
  • a bias of the spacer pin 7 can by suitable elastic Elements 16 (e.g., rubbers or the like) can be achieved as well as into the bores 9a, 9b are introduced.
  • suitable elastic Elements 16 e.g., rubbers or the like
  • the storage of the axle package within the housing 2 must be part of the axially through catch the force generated by the piston 5.
  • the output shaft 6 must be in radial Be led direction. This is done by axial-radial bearings, which are shown in Figs. 1 and 2 with Reference numerals 12 and 13 are designated.
  • the axial or radial Components of the bearings to be formed separately.
  • rolling bearings used.
  • the bearings 12, 13 are typically integrated into the housing covers 14, 15, which close the housing 2 in each case on both sides tight. The dimensions of the individual components coordinated so that the axle pack through the Housing cover 14, 15 axially biased in conjunction with the elastic member 16 is.
  • Cross-section of the piston 5 has for this purpose a polygonal profile, preferably a P4C profile according to DIN standard 32712.
  • the polygon profile extends substantially over the cross-sectional area provided with the threads 5a, 5b; i.e. the polygon profile is arranged substantially where the coarse thread 8a, 8b of the output shaft. 6 engage in the piston 5.
  • this is also the term "intervention area” used.
  • the polygon profile can also over the entire length of the piston 5 extend.
  • a sectional view of the piston 5 along that shown in Fig. 2 Line D, D ' is shown in FIG.
  • Such a polygon profile allows that on the one hand enough power is transmitted to the output shaft. On the other hand is by ensures a so-called "slippage" of the output shaft 6, which in turn a Turning the piston 5 prevented.
  • Fig. 4 shows an application of the pivoting drive according to the invention for deflection a so-called mini flap.
  • the rear end of an aerodynamic profile 20 shown schematically.
  • a flap 22 At the bottom 21 of the profile 20 is a flap 22 via a hinged joint 23 hinged.
  • the pivot axis 24 of the hinge connection 23 runs parallel to the trailing edge 25 of the profile.
  • inventive Part-turn actuators 1 arranged linear or rod-shaped.
  • the connections 3, 4 of the individual Part-turn actuators 1 are preferably supplied in parallel.
  • the inlet of the hydraulic Medium is again bidirectional, depending on the desired pivoting direction. By Such an arrangement, the operating forces are introduced surface and not how until now selectively.
  • the in Fig. 4 shown "broom handle assembly" are integrated into the hinge joint 23.
  • Integrated, rotationally symmetric actuator systems are already smaller with diameters 28 mm.
  • the diameter of the pivot drive not more than 20 mm.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Hydraulic Motors (AREA)

Description

Die vorliegende Erfindung betrifft einen linienförmigen, hydraulischen Schwenkantrieb gemäß dem Oberbegriff des Anspruchs 1.The present invention relates to a linear, hydraulic pivot drive according to the preamble of claim 1.

Derartige linienförmige Antriebe finden z.B. zur Klappensteuerung aerodynamischer Profile Anwendung. Hierbei ist es insbesondere von Vorteil, dass auf übliche Gestänge bzw. Steuerstangen, die ausserhalb des aerodynamischen Profils an der Steuerklappe angelenkt sind und somit die aerodynamischen Verhältnisse negativ beeinflussen, verzichtet werden kann.Such linear drives find e.g. for flap control aerodynamic Profile application. It is particularly advantageous that on conventional linkage or control rods that are outside the aerodynamic profile on the control flap are hinged and thus adversely affect the aerodynamic conditions, can be waived.

Ein bekannter Antrieb zur Steuerung eines Rotorblatt-Querruders ist beispielsweise in GB 2 299 562 A beschrieben. Zur Umsetzung einer hydraulisch hervorgerufenen Axialbewegung einer Welle in eine Drehbewegung, ist die Welle mit einem Steilgewinde versehen. Das Steilgewinde greift in mehrere Buchsen ein, die die Welle konzentrisch umgeben, so dass beim axialen Verschieben der Welle die Buchsen eine Drehung erfahren. Dabei ist eine Drehmomentabstützung der Welle erforderlich, um wiederum deren Drehung wirksam zu verhindern. Dies wird durch einen zusätzlichen Mechanismus bewirkt, der die Welle festhält. Der Mechanismus umfasst mehrere Komponenten, unter anderem separate Bohrungen, in die die Welle eingeführt sind, sowie Festhaltestifte. Eine derartige Anordnung weist nicht nur relativ große Abmessungen auf, sondern führt auch zu intensiver Montage- und Wartungsarbeit.A well-known drive for controlling a rotor blade aileron, for example, in GB 2 299 562 A. To implement a hydraulically induced Axial movement of a shaft in a rotary motion, is the shaft with a coarse thread Mistake. The coarse thread engages in several bushes, concentric the shaft surrounded so that the bushings undergo a rotation during axial displacement of the shaft. In this case, a torque support of the shaft is required to turn their To prevent rotation effectively. This is done through an additional mechanism causes, which holds the shaft. The mechanism includes several components, below Other separate holes in which the shaft are inserted, and retaining pins. A Such arrangement not only has relatively large dimensions, but also leads to intensive assembly and maintenance work.

Weiterhin ist ein linienförmiger, hydraulischer Schwenkantrieb aus dem Dokument DD-A-26 813 bekannt, wobei ein axial in einem Gehäuse verschiebbarer kolben über ein Steilgewinde auf eine durchgehende welle wirkt.Furthermore, a line-shaped, hydraulic rotary actuator from the document DD-A-26 813 known, wherein a axially displaceable piston in a housing via a Steep thread acts on a continuous wave.

Ferner sind sogenannte Steilgewinde-Schwenkmotoren bekannt, die eine axiale Verschiebung eines hydraulischen Arbeitskolbens über Steilgewinde in eine Drehbewegung einer Abtriebswelle umsetzen. Die Drehmomentabstützung des Arbeitskolben erfolgt z.B. durch zwei gegensinnig verlaufende Gewinde, die beidseitig in den Kolben eingreifen. Dies führt jedoch zu einer gegensinnigen Drehrichtung der Abtriebswelle, was für manche Anwendungen unerwünscht ist. Die Gewinde können ausser axial hintereinander auch radial geschachtelt angeordnet sein. Hierbei ist insbesondere aufgrund der nicht beliebig reduzierbaren Steighöhe der Steilgewinde eine beliebige Verkleinerung der Anordnung nicht möglich. Kommerzielle Antriebe sind somit in der Regel relativ groß. Ferner ist es von Nachteil, dass bei derartigen konventionellen hydraulischen Schwenkantrieben eine Konzentration auf punktuelle Lastverteilungen erfolgt.Furthermore, so-called steep-thread swivel motors are known which have an axial Displacement of a hydraulic working piston via coarse thread in one Convert rotary motion of an output shaft. The torque support of the Working piston is e.g. by two opposing threads, the two sides in engage the piston. However, this leads to an opposite direction of rotation Output shaft, which is undesirable for some applications. The threads can be arranged also axially nested one behind the other radially. This is in particular due to the not arbitrarily reducible rise height of the coarse thread one Any reduction of the arrangement is not possible. Commercial drives are thus usually relatively large. Furthermore, it is disadvantageous that in such conventional hydraulic rotary actuators a focus on selective load distributions he follows.

In jüngster Zeit sind aerodynamische Strukturen mit kleineren Klappenanordnungen entwickelt worden (sogenannte Miniklappen), die sich von herkömmlichen Klappen mit 10 - 30 % Cleanflügeltiefe dadurch unterscheiden, dass sie eine Tiefe von lediglich 1- 3 % aufweisen und wie bei einer Spreizklappe aus einem feststehenden und einem ausgeschlagenen Teil bestehen. Ein aerodynamisches Profil mit einer derartigen Miniklappe ist beispielsweise in unserer unveröffentlichten Patentanmeldung DE 101 56 733 beschrieben. Ein Auslenken der Miniklappe mit herkömmlichen Stellhebeln würde nicht nur ungünstige Strömungsverhältnisse mit sich bringen, sondern auch ein hohes Gewicht, da mehrere Stellhebel erforderlich wären. Ebenso wäre ein hoher Montagesowie Wartungsaufwand erforderlich.Recently, there are aerodynamic structures with smaller flap arrangements have been developed (so-called mini flaps), which differs from conventional flaps with 10 - Distinguish 30% clean wing depth by a depth of only 1-3% have and as in a Spreizklappe from a fixed and a consisted part. An aerodynamic profile with such Mini flap is for example in our unpublished patent application DE 101 56th 733 described. A deflection of the mini flap with conventional levers would not only unfavorable flow conditions bring with it, but also a high Weight, as several levers would be required. Likewise, a high montagesowie Maintenance required.

Folglich sind neue Aktuatorsysteme notwendig, die insbesondere den Anforderungen einer hohen Miniaturisierung gerecht werden. Aufgrund der strukturellen Anforderungen steht lediglich sehr begrenzter Bauraum zur Verfügung. Die Klappen-Aktuatorik sollte auf eine stärkere Integration der funktionellen Aufgaben von Antrieb und tragender Struktur ausgerichtet sein. Daneben ist eine linienförmige bzw. flächige Kraft- bzw. Leistungsverteilung wünschenswert, um den klappenspezifischen Erfordernissen gerecht zu werden.Consequently, new actuator systems are necessary, in particular the requirements of a high miniaturization. Due to the structural requirements only very limited space available. The flap actuator should be on a greater integration of the functional tasks of drive and load-bearing structure be aligned. In addition, there is a linear or area force or power distribution desirable to meet the flap specific requirements.

Somit liegt der vorliegenden Erfindung die Aufgabe zu Grunde, einen linienförmigen, hydraulischen Schwenkantrieb zu schaffen, der eine geringe Baugröße sowie einen einfachen Aufbau aufweist, so dass er in bestehende Strukturen integriert werden kann und geringen Wartungsaufwand erfordert.Thus, the object of the present invention is to provide a linear, To create hydraulic rotary actuator, which has a small size and a simple structure, so that it can be integrated into existing structures and low maintenance required.

Die Aufgabe wird durch einen linienförmigen, hydraulischen Schwenkantrieb gelöst, der ein Gehäuse mit Anschlüssen zum Einführen eines hydraulischen Mediums umfasst, einen innerhalb des Gehäuses angeordneten Kolben, der durch Einwirken des hydraulischen Mediums axial verschiebbar ist, sowie eine mit Steilgewinden versehene Abtriebswelle, die mit dem Kolben zusammenwirkt, um die axiale Bewegung des Kolbens in eine Rotationsbewegung zu übertragen, und sich erfindungsgemäß dadurch auszeichnet, dass die Abtriebswelle in den Kolben eingebracht ist, wobei die Steilgewinde gleichsinnig ausgebildet sind und in den Kolben eingreifen, und dass der Kolbenquerschnitt ein Polygon-Profil aufweist, um eine Drehbewegung des Kolbens wirksam zu verhindern.The object is achieved by a linear, hydraulic rotary actuator, the a housing with connections for introducing a hydraulic medium comprises, a within the housing arranged piston, which by the action of the hydraulic Medium is axially displaceable, as well as provided with steep threads output shaft, which cooperates with the piston to the axial movement of the piston in a To transmit rotational movement, and according to the invention is characterized in that the output shaft is inserted in the piston, the coarse thread in the same direction are formed and engage in the piston, and that the piston cross section a Has polygon profile to effectively prevent a rotational movement of the piston.

Durch das Ausbilden des Kolbenquerschnittes in Form eines Polygon-Profils wird die Drehmomentabstützung zum Verhindern einer Drehung des Kolbens durch diesen selbst gewährleistet. Zweckmäßigerweise ist das Polygon-Profil im Eingriffsbereich von Abtriebswelle und Kolben vorgesehen, d.h. in dem Querschnittsbereich des Kolbens, wo Abtriebswelle und Kolben ineinander eingreifen. Alternativ kann das Polygonprofil entlang des gesamten Kolbens ausgebildet sein. Vorzugsweise ist das Polygonprofil ein P4C-Profil nach DIN Norm.32712. Besonders vorteilhaft ist hierbei, dass die axiale Verschiebbarkeit unter Momentenkraft gewährleistet ist. Auf diese Weise sind keine zusätzlichen Mechanismen und Komponenten erforderlich, um eine Drehung des Kolbens zu unterbinden. Ein einfacher Aufbau ist gewährleistet. Ferner ist es vorteilhaft, dass durch eine derartige Ausgestaltung der Schwenkantrieb wesentlich kleiner als bekannte Anordnungen ist. Besonders zweckmäßig ist es hierbei, dass die Abtriebswelle beidseitig in den Kolben eingebracht ist.By forming the piston cross section in the form of a polygon profile is the Torque support for preventing rotation of the piston by itself guaranteed. Conveniently, the polygon profile is in the engagement region of Output shaft and piston provided, i. in the cross-sectional area of the piston, where Output shaft and piston engage each other. Alternatively, the polygon profile be formed along the entire piston. Preferably, the polygon profile is a P4C profile according to DIN standard.32712. It is particularly advantageous that the axial Displacement under torque is ensured. In this way are none additional mechanisms and components required to turn the piston to prevent. A simple structure is guaranteed. Furthermore, it is advantageous that by Such an embodiment of the rotary actuator much smaller than known Arrangements is. It is particularly useful in this case that the output shaft on both sides is introduced into the piston.

Dabei ist es insbesondere von Vorteil, dass die Abtriebswelle zwei separate Abschnitte aufweist, an deren jeweils in den Kolben eingreifenden Enden die gleichsinnigen Steilgewinde angeordnet sind. Auf diese Weise wird erreicht, dass die Drehrichtung der Abtriebswellenabschnitte identisch ist.It is particularly advantageous that the output shaft has two separate sections has, at their respectively engaging in the piston ends the same direction Steep thread are arranged. In this way it is achieved that the direction of rotation of the Output shaft sections is identical.

Vorzugsweise sind die Abtriebswellenabschnitte über einen Distanzstift rotationssymmetrisch miteinander verbunden, wobei der Distanzstift in jeweilige in den Abtriebswellenabschnitten vorgesehene Bohrungen eingeführt ist. Dies ist insbesondere im Hinblick auf Montage sowie Wartung vorteilhaft. Preferably, the output shaft sections are rotationally symmetric via a spacer pin interconnected, wherein the spacer pin in each in the Output shaft sections provided holes is introduced. This is especially true With regard to assembly and maintenance advantageous.

Zweckmäßigerweise ist der Kolben beidseitig mit Gewindebuchsen versehen, in die die Steilgewinde der Abtriebswellenabschnitte eingreifen. Auf diese Weise wird, wie bereits erwähnt, eine einheitliche Drehrichtung der Abtriebswellenabschnitte bewirkt. Zudem gewährleistet dies eine möglichst große Kraftübertragung.Conveniently, the piston is provided on both sides with threaded bushes into which the Steep thread of the output shaft sections engage. In this way, as already mentioned causes a uniform direction of rotation of the output shaft sections. moreover this ensures the greatest possible power transmission.

Ferner ist es vorteilhaft, dass der Kolben eine zentrale Bohrung aufweist, durch den der Distanzstift durchgeführt ist. Dadurch wird der Distanzstift auf einfache Weise gelagert. Zu diesem Zweck kann ein Lager in der zentralen Bohrung angeordnet sein.Further, it is advantageous that the piston has a central bore through which the Distance pin is performed. As a result, the spacer pin is stored in a simple manner. For this purpose, a bearing can be arranged in the central bore.

Zweckmäßigerweise sind Axial-Radial-Lager, vorzugsweise Wälzlager, zum Lagern der Abtriebswelle vorgesehen. Alternative können die axialen und radialen Komponenten auch separat ausgebildet sein. Diese Lager ermöglichen eine gut Aufnahme sowohl von axialen als auch radialen Kräften.Appropriately, axial-radial bearings, preferably rolling bearings, for storing the Output shaft provided. Alternative can be the axial and radial components as well be formed separately. These bearings allow a good reception of both axial as well as radial forces.

Besonders vorteilhaft ist es, die Axial-Radial-Lager in Gehäusedeckel zu integrieren, die wiederum das Gehäuse dicht abschließen. Dies bringt vorteilhafterweise eine kompakte Bauweise mit sich.It is particularly advantageous to integrate the axial-radial bearings in housing cover, the in turn close the housing tightly. This advantageously brings a compact Construction with itself.

Ferner ist es zweckmäßig, dass das hydraulische Medium bidirektional in das Gehäuse einführbar ist, was ein Schwenken einer an dem Gehäuse angelenkten Klappe in unterschiedliche Richtungen ermöglicht.Furthermore, it is expedient that the hydraulic medium can be introduced bidirectionally into the housing is what pivoting a hinged to the housing flap in allows different directions.

Der erfindungsgemäße Schwenkantrieb findet insbesondere zur Klappenauslenkung an Rotorblättern oder Flugzeugtragflächen Verwendung. Dabei ist es insbesondere vorteilhaft, den Antrieb in eine Gelenkverbindung einer an ein aerodynamisches Profil angelenkten Klappe zu integrieren, wobei eine Mehrzahl derartiger Antriebe linienförmig in die Gelenkverbindung integriert ist.The pivoting drive according to the invention finds particular to Klappenauslenkung Rotor blades or aircraft wings use. It is particularly advantageous the drive in a hinge connection of a hinged to an aerodynamic profile Integrate flap, with a plurality of such drives linear in the Articulated connection is integrated.

Im Folgenden wird die Erfindung an Hand der beigefügten Abbildungen in näheren Einzelheiten erläutert. In denen zeigt:

Fig.1
eine schematische dreidimensionale Darstellung des erfindungsgemäßen Schwenkantriebs;
Fig. 2
eine Schnittansicht des erfindungsgemäßen Schwenkantriebs;
Fig. 3
eine Querschnittsansicht des in dem erfindungsgemäßen Schwenkantriebs verwendeten Kolben; und
Fig. 4
mehrere, linienförmig angeordnete Schwenkantriebe, die in eine Gelenkverbindung einer an einem aerodynamischen Profil angelenkten Klappe integriert sind.
In the following the invention with reference to the accompanying drawings will be explained in more detail. In which shows:
Fig.1
a schematic three-dimensional representation of the pivot drive according to the invention;
Fig. 2
a sectional view of the pivot drive according to the invention;
Fig. 3
a cross-sectional view of the piston used in the rotary actuator according to the invention; and
Fig. 4
a plurality of linearly arranged pivot drives, which are integrated into a hinge connection of a hinged to an aerodynamic profile flap.

Fig. 1 zeigt in dreidimensionaler Ansicht einen erfindungsgemäßen linienförmigen, hydraulischen Schwenkantrieb 1 zum Umsetzen einer Axialbewegung in eine Drehbewegung. Der Antrieb umfasst ein Gehäuse 2, das zwei Anschlüsse 3, 4 für ein hydraulisches Medium (z.B. ein Fluid) aufweist. Im Inneren des Gehäuses 2 ist ein Kolben 5 sowie eine mit dem Kolben 5 in Verbindung stehende Abtriebswelle 6 angeordnet. Zur besseren Darstellung ist das Gehäuse 2 sowie der Kolben 5 in Fig 1. teilweise in geschnittener Ansicht gezeigt. In den symmetrisch ausgebildeten Kolben 5 ist die Abtriebswelle 6 beidseitig eingebracht. Um das Einführen sowie die Wartung des Schwenkantriebes zu erleichtern, besteht die Abtriebswelle 6 vorzugsweise zumindest aus zwei separaten Abschnitten 6a, 6b. Die jeweils in den Kolben 5 eingreifenden Enden der Abtriebswellenabschnitte 6a, 6b sind mit gleichsinnig verlaufenden Steilgewinden 8a, 8b versehen. Durch die gleichsinnig ausgebildeten Steilgewinde 8a, 8b ist sichergestellt, dass die Drehrichtung der beiden Abtriebswellenabschnitte 6a, 6b identisch ist, was nachstehend noch genauer beschrieben wird.1 shows a three-dimensional view of a line-shaped, hydraulic rotary actuator 1 for converting an axial movement in one Rotation. The drive comprises a housing 2, the two terminals 3, 4 for a hydraulic medium (e.g., a fluid). Inside the housing 2 is a piston 5 and arranged with the piston 5 in connection with the output shaft 6. to better illustration, the housing 2 and the piston 5 in Figure 1 partially in shown sectional view. In the symmetrical piston 5 is the Output shaft 6 inserted on both sides. To introduce and maintain the To facilitate pivot drive, the output shaft 6 is preferably at least two separate sections 6a, 6b. Each engaging in the piston 5 ends of the Output shaft sections 6a, 6b are with co-rotating coarse threads 8a, 8b Mistake. By the co-trained coarse thread 8a, 8b ensures that the direction of rotation of the two output shaft sections 6a, 6b is identical, as follows will be described in more detail.

Wie Fig. 2 besser zu entnehmen ist, ist der Kolben 5 entsprechend beidseitig mit Gewinden 5a, 5b versehen, um den Eingriff der Antriebswellenabschnitte 6a, 6b in den Kolben 5 zu gewährleisten. Geeigneterweise sind die Gewinde 5a, 5b in Form von Gewindebuchsen ausgestaltet. Innerhalb des Kolbens 5 sind die beiden Abtriebswellenabschnitte 6a, 6b über einen Distanzstift 7 rotationssymmetrisch miteinander verbunden (Fig. 2). Hierzu ist der Kolben 5 mit einer zentralen Bohrung 10 versehen, in dem der Distanzstift 7, vorzugsweise unter Verwendung eines Dichtringes 11, lagert. Gleichzeitig ist der Distanzstift 7 in entsprechende, in den Abtriebswellenabschnitten 6a, 6b eingebrachte Bohrungen 9a, 9b eingeführt. Eine Vorspannung des Distanzstiftes 7 kann durch geeignete elastische Elemente 16 (z.B. Gummis oder dergleichen) erzielt werden, die ebenso in die Bohrungen 9a, 9b eingeführt sind. Auf diese Weise entsteht ein rotationssymmetrisches Achspaket, das im wesentlichen aus Abtriebswellenabschnitten 6a, 6b und Distanzstift 7 besteht.As can be seen better in FIG. 2, the piston 5 is correspondingly threaded on both sides 5a, 5b provided to the engagement of the drive shaft sections 6a, 6b in the piston 5 to guarantee. Suitably, the threads 5a, 5b are in the form of threaded bushings designed. Within the piston 5, the two output shaft sections 6a, 6b over a spacer pin 7 rotationally symmetrical with each other (Fig. 2). For this is the Piston 5 is provided with a central bore 10 in which the spacer pin 7, preferably using a sealing ring 11, stores. At the same time, the spacer pin 7 is in corresponding, introduced in the output shaft sections 6a, 6b holes 9a, 9b introduced. A bias of the spacer pin 7 can by suitable elastic Elements 16 (e.g., rubbers or the like) can be achieved as well as into the bores 9a, 9b are introduced. This creates a rotationally symmetrical axle package, which consists essentially of output shaft sections 6a, 6b and spacer pin 7.

Die Lagerung des Achspaketes innerhalb des Gehäuses 2 muss einen Teil der axial durch den Kolben 5 erzeugten Kraft auffangen. Zusätzlich muss die Abtriebswelle 6 in radialer Richtung geführt werden. Dies erfolgt durch Axial-Radial-Lager, die in Figs. 1 und 2 mit Bezugsziffern 12 und 13 bezeichnet sind. Alternativ können die axialen bzw. radialen Komponenten der Lager getrennt ausgebildet sein. Vorzugsweise werden jedoch Wälzlager verwendet. Die Lager 12, 13 sind typischerweise in die Gehäusedeckel 14, 15 integriert, die das Gehäuse 2 jeweils beidseitig dicht abschließen. Dabei sind die Abmessungen der einzelnen Bauteile so aufeinander abgestimmt, dass das Achspaket durch die Gehäusedeckel 14, 15 in Verbindung mit dem elastischen Element 16 axial vorgespannt ist.The storage of the axle package within the housing 2 must be part of the axially through catch the force generated by the piston 5. In addition, the output shaft 6 must be in radial Be led direction. This is done by axial-radial bearings, which are shown in Figs. 1 and 2 with Reference numerals 12 and 13 are designated. Alternatively, the axial or radial Components of the bearings to be formed separately. Preferably, however, rolling bearings used. The bearings 12, 13 are typically integrated into the housing covers 14, 15, which close the housing 2 in each case on both sides tight. The dimensions of the individual components coordinated so that the axle pack through the Housing cover 14, 15 axially biased in conjunction with the elastic member 16 is.

Im folgenden wird die Funktionsweise des erfindungsgemäßen Schwenkantriebs an Hand von Figs. 1 und 2 beschrieben. Über den Anschluss 3 wird das hydraulische Medium in Pfeilrichtung in das Gehäuse 2 eingeführt. Aufgrund des dadurch auf den Kolben 5 einwirkenden Druckes wird dieser axial nach links (s. Pfeilrichtung) verschoben. Um die axiale Bewegung des Kolbens 5 in eine Drehbewegung der Abtriebswelle 6 zu übertragen, die, wie geschildert, mit dem Kolben 5 über die Steilgewinde 8a, 8b zusammenwirkt, ist eine Drehmomentabstützung erforderlich. Mit anderen Worten, die Drehbewegung des Kolbens 5 muss wirksam verhindert werden, ansonsten ist eine Umsetztung der Axialbewegung in eine Drehbewegung nicht möglich. Die Drehmomentabstützung wird erfindungsgemäß durch die Querschnittsform des Kolbens 5 selbst gewährleistet. Der Querschnitt des Kolbens 5 weist hierzu ein Polygon-Profil auf, das vorzugsweise ein P4C-Profil nach DIN-Norm 32712 ist. Das Polygon-Profil erstreckt sich dabei im wesentlichen über den Querschnittsbereich, der mit den Gewinden 5a, 5b versehen ist; d.h. das Polygon-Profil ist im wesentlichen dort angeordnet, wo die Steilgewinde 8a, 8b der Abtriebswelle 6 in den Kolben 5 eingreifen. Im Folgenden wird hierfür auch der Begriff "Eingriffsbereich" verwendet. Selbstverständlich kann sich das Polygonprofil auch über die gesamte Länge des Kolbens 5 erstrecken. Eine Schnittansicht des Kolbens 5 entlang der in Fig. 2 gezeigten Linie D, D' ist in Fig. 3 dargestellt. Ein derartiges Polygon-Profil ermöglicht, dass einerseits genügend Kraft auf die Abtriebswelle übertragen wird. Andererseits ist dadurch ein sogenanntes "Durchrutschen" der Abtriebswelle 6 gewährleistet, was wiederum ein Drehen des Kolbens 5 verhindert.In the following the operation of the rotary actuator according to the invention is on hand of Figs. 1 and 2 described. Via port 3, the hydraulic medium in Arrow direction introduced into the housing 2. Due to the thereby on the piston. 5 acting pressure is this axially shifted to the left (see arrow direction). To the axial movement of the piston 5 in a rotational movement of the output shaft 6 to transmit which, as described, with the piston 5 via the coarse thread 8a, 8b cooperates, is a torque support required. In other words, the rotational movement of the Piston 5 must be effectively prevented, otherwise a Umsetztung the Axial movement in a rotary motion not possible. The torque support is According to the invention ensured by the cross-sectional shape of the piston 5 itself. Of the Cross-section of the piston 5 has for this purpose a polygonal profile, preferably a P4C profile according to DIN standard 32712. The polygon profile extends substantially over the cross-sectional area provided with the threads 5a, 5b; i.e. the polygon profile is arranged substantially where the coarse thread 8a, 8b of the output shaft. 6 engage in the piston 5. In the following, this is also the term "intervention area" used. Of course, the polygon profile can also over the entire length of the piston 5 extend. A sectional view of the piston 5 along that shown in Fig. 2 Line D, D 'is shown in FIG. Such a polygon profile allows that on the one hand enough power is transmitted to the output shaft. On the other hand is by ensures a so-called "slippage" of the output shaft 6, which in turn a Turning the piston 5 prevented.

Zum Umkehren der Drehrichtung der Abtriebswelle 6 bzw. der Schwenkrichtung des Antriebs 1 wird lediglich die Einlassrichtung des hydraulischen Mediums geändert. Der Anschluss 4 wird zum Einlass und der Anschluss 3 wird zum Auslass für das hydraulische Medium. Das Einführen des Mediums erfolgt also je nach gewünschter Schwenkrichtung bidirektional. Ferner sei angemerkt, dass Kolbenhub, der in Fig. 2 mit Bezugsziffer 17 bezeichnet ist, und Gewindesteigung aufeinander abgestimmt sind, um einen vordefininierten Auslenkwinkel zu erhalten. Ausserdem muss die Steigung des Gewindes so groß sein, dass keine Selbsthemmung des Antriebs auftritt. Dabei ist der Antrieb um so effizienter, je steiler das Gewinde ausfällt. Mit der Steilheit des Gewindes steigt auch die axiale notwendige Bewegung des Kolbens (Hub 17), um einen bestimmten Schwenkwinkel zu erreichen. Gleichzeitig wird damit das hydraulische Arbeitsvolumen und somit eine Feinpositionierung bzw. Regelbarkeit des Schwenkwinkels einfacher.For reversing the direction of rotation of the output shaft 6 and the pivoting direction of the Drive 1 only changes the inlet direction of the hydraulic medium. Of the Port 4 becomes the inlet and port 3 becomes the outlet for the hydraulic Medium. The introduction of the medium thus takes place depending on the desired pivoting direction bidirectional. It should also be noted that piston stroke, the in Fig. 2 with reference numeral 17th is designated, and thread pitch are matched to a predefined To obtain deflection angle. In addition, the pitch of the thread must be so big be that no self-locking of the drive occurs. The drive is the same more efficient, the steeper the thread turns out. With the steepness of the thread also increases axial necessary movement of the piston (stroke 17) to a certain To reach the swivel angle. At the same time, this will increase the hydraulic working volume and thus a fine positioning or controllability of the pivot angle easier.

Fig. 4 zeigt eine Anwendung des erfindungsgemäßen Schwenkantriebes zur Auslenkung einer sogenannten Miniklappe. In Fig. 4 ist das hintere Ende eines aerodynamischen Profils 20 schematisch dargestellt. An der Unterseite 21 des Profils 20 ist eine Klappe 22 über eine gelenkförmige Verbindung 23 angelenkt. Die Schwenkachse 24 der Gelenkverbindung 23 verläuft parallel zur Hinterkante 25 des Profils. Um eine gleichmäßige Kraftübertragung entlang der Schwenkachse 24 zu erzieien, sind mehrere erfindungsgemäße Schwenkantriebe 1 linien- bzw. stabförmig angeordnet. Die Anschlüsse 3, 4 der einzelnen Schwenkantriebe 1 sind vorzugsweise parallel versorgt. Der Einlass des hydraulischen Mediums erfolgt wiederum bidirektional, je nach gewünschter Schwenkrichtung. Durch eine derartige Anordnung werden die Betätigungskräfte flächig eingebracht und nicht wie bisher punktuell. Aufgrund der geringen Baugröße des Schwenkantriebs 1 kann die in Fig. 4 gezeigte "Besenstielanordnung" in die Gelenkverbindung 23 integriert werden. Derartige integrierte, rotationssymmetrische Aktuatorsysteme sind bereits mit Durchmessern kleiner 28 mm hergestellt worden. Vorzugsweise beträgt der Durchmesser des Schwenkantriebes nicht mehr als 20 mm.Fig. 4 shows an application of the pivoting drive according to the invention for deflection a so-called mini flap. In Fig. 4, the rear end of an aerodynamic profile 20 shown schematically. At the bottom 21 of the profile 20 is a flap 22 via a hinged joint 23 hinged. The pivot axis 24 of the hinge connection 23 runs parallel to the trailing edge 25 of the profile. For a uniform power transmission along the pivot axis 24 to create, several are inventive Part-turn actuators 1 arranged linear or rod-shaped. The connections 3, 4 of the individual Part-turn actuators 1 are preferably supplied in parallel. The inlet of the hydraulic Medium is again bidirectional, depending on the desired pivoting direction. By Such an arrangement, the operating forces are introduced surface and not how until now selectively. Due to the small size of the pivot drive 1, the in Fig. 4 shown "broom handle assembly" are integrated into the hinge joint 23. such Integrated, rotationally symmetric actuator systems are already smaller with diameters 28 mm. Preferably, the diameter of the pivot drive not more than 20 mm.

Claims (15)

  1. Linear, hydraulic pivot drive (1), comprising
    a casing (2) with connections (3, 4) for introducing a hydraulic medium;
    a piston (5) arranged inside the casing (2), which piston is axially displaceable due to the action of the hydraulic medium;
    an output shaft (6) provided with coarse threads (8a, 8b), which shaft interacts with the piston (5) to translate the axial movement of the piston (5) into a rotational movement,
    characterized in that the output shaft (6) has two separate partial sections (6a, 6b), which are introduced on both sides into the piston (5) and engage in the piston (5) via coarse threads (8a, 8b) formed in the same direction, so that a torque with identical direction of rotation can be tapped at both partial sections (6a, 6b), the piston cross-section having a polygon.profile to prevent a rotary movement of the piston (5).
  2. Linear, hydraulic pivot drive according to claim 1, characterized in that the polygon profile is provided substantially in the area of engagement of output shaft (6) and piston (5).
  3. Linear, hydraulic pivot drive according to claim 1, characterized in that the polygon profile is a P4C profile.
  4. Linear, hydraulic pivot drive according to claim 1, characterized in that the output shaft (6) has two separate sections (6a, 6b), arranged at the respective ends of which engaging in the piston (5) are the coarse threads (8a, 8b) formed in the same direction.
  5. Linear, hydraulic pivot drive according to claim 4, characterized in that the output shaft sections (6a, 6b) are connected to one another symmetrically with respect to rotation via a distance pin (7), the distance pin (7) being inserted into respective holes (9a, 9b) of the output shaft sections (6a, 6b).
  6. Linear, hydraulic pivot drive according to claim 1, characterized in that the piston (5) is provided on both sides with threaded bushes (5a, 5b), in which the coarse threads (8a, 8b) of the output shaft sections (6a, 6b) engage.
  7. Linear, hydraulic pivot drive according to claim 5, characterized in that the piston (5) has a central hole (10) for guiding the distance pin (7).
  8. Linear, hydraulic pivot drive according to claim 1, characterized in that axial-radial bearings (12, 13) are provided for supporting the output shaft (6).
  9. Linear, hydraulic pivot drive according to claim 8, characterized in that the axial-radial bearings (12, 13) are rolling bearings.
  10. Linear, hydraulic pivot drive according to claim 8, characterized in that the axial-radial bearings (12, 13) are integrated into casing covers (14, 15), the casing covers (14, 15) completing the casing (2) on both sides.
  11. Linear, hydraulic pivot drive according to claim 1, characterized in that the hydraulic medium can be introduced bidirectionally into the casing (2).
  12. Linear, hydraulic pivot drive, characterized in that several drives (1) according to claims 1 to 12 are arranged in a linear or bar-shaped manner in order to obtain a uniform transfer of force along the linear extension.
  13. Linear, hydraulic pivot drive according to claim 12, characterized in that the hydraulic connections (3, 4) of the individual drives (1) are connected in parallel.
  14. Use of the drive according to one of claims 1 to 12 for the deflection of flaps of aerodynamic profile sections, in particular rotor blades and aircraft lifting sections.
  15. Use of the drive according to one of claims 1 to 12 for the deflection of a flap (22) deflected via a hinge joint (23) onto an aerodynamic profile section (20), a plurality of such drives (1) being integrated linearly into the hinge joint (23).
EP03718601A 2002-02-25 2003-02-21 Linear, hydraulic pivot drive Expired - Fee Related EP1488111B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10207830A DE10207830B4 (en) 2002-02-25 2002-02-25 Linear hydraulic swivel drive
DE10207830 2002-02-25
PCT/DE2003/000541 WO2003072955A1 (en) 2002-02-25 2003-02-21 Linear, hydraulic pivot drive

Publications (2)

Publication Number Publication Date
EP1488111A1 EP1488111A1 (en) 2004-12-22
EP1488111B1 true EP1488111B1 (en) 2005-12-07

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EP03718601A Expired - Fee Related EP1488111B1 (en) 2002-02-25 2003-02-21 Linear, hydraulic pivot drive

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US (1) US7028602B2 (en)
EP (1) EP1488111B1 (en)
JP (1) JP4227527B2 (en)
CA (1) CA2476903C (en)
DE (2) DE10207830B4 (en)
ES (1) ES2251683T3 (en)
WO (1) WO2003072955A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005033697A1 (en) * 2005-07-19 2007-03-22 Airbus Deutschland Gmbh Control surface e.g. rudder, operating mechanism for airplane, has gearing placed downstream of hydraulic motor so that drive shaft of motor drives input shaft of gearing, and output shaft coincides with rotational axis of rudder
DE202006016354U1 (en) 2006-10-23 2008-02-28 Asturia Automotive Systems Ag Device for compensation and / or transmission of forces / moments and rotational movements between two components
FI120917B (en) 2008-02-08 2010-04-30 Kinshofer Gmbh Hydraulically operated swivel
EP2703288B1 (en) 2012-08-31 2018-03-14 Claverham Limited Electromechanical linear actuator for in blade rotor control
KR101637037B1 (en) * 2014-12-22 2016-07-07 김선규 Hydraulic cylinder
CN106151152A (en) * 2015-03-12 2016-11-23 盐城工业职业技术学院 Four station double acting hydraulic cylinders
JP6780819B2 (en) * 2017-10-03 2020-11-04 Smc株式会社 A rotating unit and a cylinder device provided with the rotating unit
KR102124335B1 (en) * 2018-09-06 2020-06-19 주식회사 포스코 Separating apparatus and separating method

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE26813C (en) * C. WETTER in London Innovation in electromagnets and magnetic cores for dynamo-electric machines and similar devices
DE1024804B (en) * 1956-09-18 1958-02-20 Ernst Heinkel Fahrzeugbau G M Hydraulic flap drive, especially for aircraft
DD26813A1 (en) * 1962-04-16 1964-01-27 Hydraulic angle motor
US4603616A (en) * 1983-05-25 1986-08-05 Zaytran Inc. Rotary actuator
GB2299562A (en) * 1995-04-01 1996-10-09 Nigel Howard Mckrill Actuator for helicopter rotor blade aileron
DE19628117C2 (en) * 1996-07-12 1998-05-14 Walter Voss Gmbh Armaturenfabr Rotary drive, in particular swivel motor
DE10156733B4 (en) * 2001-11-19 2006-04-20 Eads Deutschland Gmbh Aerodynamic profile with adjustable flap

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Publication number Publication date
US20050178927A1 (en) 2005-08-18
ES2251683T3 (en) 2006-05-01
WO2003072955A1 (en) 2003-09-04
EP1488111A1 (en) 2004-12-22
US7028602B2 (en) 2006-04-18
JP4227527B2 (en) 2009-02-18
JP2005525516A (en) 2005-08-25
DE10207830A1 (en) 2003-09-11
CA2476903C (en) 2010-11-23
DE10207830B4 (en) 2004-07-01
DE50301861D1 (en) 2006-01-12
CA2476903A1 (en) 2003-09-04

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