EP1991792B1 - Moteur-couple - Google Patents

Moteur-couple Download PDF

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Publication number
EP1991792B1
EP1991792B1 EP07723087.8A EP07723087A EP1991792B1 EP 1991792 B1 EP1991792 B1 EP 1991792B1 EP 07723087 A EP07723087 A EP 07723087A EP 1991792 B1 EP1991792 B1 EP 1991792B1
Authority
EP
European Patent Office
Prior art keywords
shaft
piston
rotary motor
housing
accordance
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.)
Not-in-force
Application number
EP07723087.8A
Other languages
German (de)
English (en)
Other versions
EP1991792A1 (fr
Inventor
Thomas Friedrich
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.)
Kinshofer GmbH
Original Assignee
Kinshofer GmbH
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Filing date
Publication date
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Publication of EP1991792A1 publication Critical patent/EP1991792A1/fr
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Publication of EP1991792B1 publication Critical patent/EP1991792B1/fr
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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
    • 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
    • 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 rotary motor, preferably rotary drive for construction machinery, hoists, trucks and the like, with an elongated, approximately tubular housing, at least one axially slidably received in the housing piston, which is axially driven by application of a pressure medium in a pressure chamber and at least an axially fixed in the housing, about a rotational axis rotatably received shaft, wherein the piston has a Wellen pressgangsausinstituung with which the piston is axially displaceable on the shaft.
  • a problem here is the sealing of the piston relative to the shaft and / or with respect to the housing.
  • piston designs are disadvantageous in terms of size and associated with high production costs.
  • different power relationships result for the operation in different directions of rotation.
  • the US 3,183,792 shows a rotary motor in which the longitudinally displaceably guided piston sits on a helically twisted portion of the drive shaft.
  • the said drive shaft is arranged offset eccentrically to the cylinder longitudinal axis.
  • the piston is threaded according to this document on two lateral, opposite guide pins, which prevent rotation of the piston.
  • a rotary motor known whose longitudinally displaceably guided piston sits on a helically rotated drive shaft, which is arranged eccentrically and thus prevents rotation of the piston.
  • the piston sits on two transversely spaced drive shafts, which are coupled together via a spur gear.
  • JP 61-278606 A a rotary motor is known, the shaft of which has a helical cam portion on which a counterpart inserted into the axially displaceable piston slides, which is intended to effect a seal.
  • the training of both the shaft and the piston is quite complicated here, also can not be effected over the entire travel of the piston constant rotational movement.
  • the shows JP 63-130905 A a rotary motor in which the shaft has a helical toothing on which the piston sits with a matching screw thread-shaped teeth.
  • the present invention has the object to provide an improved rotary motor of the type mentioned, which avoids the disadvantages of the prior art and further develops the latter in an advantageous manner.
  • a cost-effective and easy-to-seal piston shaft assembly is to be created, which allows the generation of high torques and large rotation angle with favorable efficiency with a short engine length, regardless of the pressure medium used.
  • the present invention thus leaves the previous approach to provide a screw engagement between the shaft and the piston and implement the axial movement of the piston in a rotational movement between the shaft and housing via a rotationally fixed guidance of the piston on the housing.
  • the piston actuates the shaft on the crank principle in conjunction with the wedging action of the pitch of a helical engagement path.
  • the hitherto always pursued approach can be left, that the piston of rotary motors, which implement an axial movement of the piston in a rotational movement of the shaft, in whatever form to secure against rotation, what the present invention ignores.
  • the shaft forms a crankshaft whose axis of rotation is offset from the shaft passage recess.
  • the respective shaft piece sliding through the shaft passage recess has a lever arm relative to the axis of rotation of the shaft, which forms the radial force produced by the axial displacement of the piston and the pitch of the spiral engagement track between the shaft and the piston and / or between the piston and the housing Rotary movement of the shaft relative to the housing or vice versa.
  • the Wellen pressgangsausNeillung is arranged approximately centrally in the piston relative to the piston cross-sectional area, being dispensed with an anti-rotation of the piston, so that a rotatability of the piston relative to the housing is given.
  • the usable simple geometries of the shaft and also the piston benefit not only a simple and cost-effective production per se, which is also easily and quickly adaptable to changing installation dimensions, but also an improved surface finish on the shaft and the piston, whereby friction losses can be reduced , This, together with the lower surface pressures, results in a higher efficiency of the engine and, moreover, also permits use without lubricant-containing pressure media.
  • piston and cylinder simple rotationally symmetric manufacturing processes can be used.
  • the vortex technique can be used in particular for the shaft.
  • the shaft has a helical course around its axis of rotation.
  • the crank portion of the shaft is, so to speak, entangled spatially in the form of a helix about the axis of rotation.
  • the helical turn advantageously has a constant radial distance from the axis of rotation of the shaft, while the pitch viewed in the axial direction can change.
  • the helical crank portion has a constant pitch to convert axial movements of the piston in a uniform rotational movement.
  • the housing may be a simple cylinder tube with a cylindrical inner circumferential surface, which may be formed in particular circular cylindrical in the simplest embodiment of the invention, since a rotationally fixed guidance of the piston in the housing is not necessary.
  • the shaft with its crank portion could also have a straight course parallel to and spaced from its axis of rotation.
  • the housing could have a spirally twisted inner circumferential surface, so that upon axial movement of the piston, it will make a helical movement about the axis of rotation of the shaft.
  • the spirally twisted formation of the inner lateral surface of the housing may optionally also be provided in combination with the above-described helical formation of the shaft, so to speak to add the slopes and, accordingly, a greater translation between the axial adjusting movement of the piston and the rotational movement of the shaft relative to the housing to reach.
  • the pair of force-producing surface pairs on the piston and housing and / or on the piston and shaft simultaneously forms a sealing surface pair. which seals the pressure chamber for pressurizing the piston.
  • a sealing surface pair which seals the pressure chamber for pressurizing the piston.
  • an extremely short length can be realized.
  • the entire housing inner diameter surface is only available in a reduced manner around the shaft cross section as a piston pressure surface.
  • the same torques can be generated with the same hydraulic or pneumatic pressures in both directions of drive.
  • for a given pressure results in a maximum torque output.
  • the seal is designed such that between the piston and the housing and / or between the piston and shaft each pressure pockets are formed, which can be fed from the piston driving the pressure chambers.
  • peripheral circumferential sectors may be delimited by axially extending sealing elements in the circumferential direction on the piston skirt outer surface and / or on the lateral surface of the shaft passage recess in the piston, so that the corresponding peripheral sectors each form a pressure pocket, wherein one of the pressure pockets with the pressure chamber on the a piston side and the opposite pressure pocket with the pressure chamber on the opposite side of the piston can be brought into fluid communication.
  • the pressure pockets are thus fed from different sides of the piston.
  • an overpressure protection is provided between the two pressure chambers of the engine, at least one which has a pressure chamber connecting a two pressure chambers, which in the normal case, i. is closed at a pressure below a predetermined threshold value of a pressure relief valve, which opens only when the said threshold value is exceeded.
  • the overpressure protection can basically be integrated in the shaft in the form of a shaft recess.
  • the overpressure protection can also be integrated in the piston, which facilitates the introduction of the overpressure channel, in particular in the case of a helical course of the shaft.
  • the shaft can advantageously be mounted on at least one end by means of a bearing plate or disk on the housing, preferably between the bearing plate and shaft, a releasable connection can be provided.
  • a helically formed recess may be provided in the bearing plate, in which the shaft is received in register with a helical section.
  • the helical shaft portion in the LagerplattenausEnglishung by a positive locking element which may have various configurations, axially and / or radially braced or spread.
  • the shaft can be mounted differently at its two ends, preferably at one end by a fixed bearing and the other end by a floating bearing, so that the shaft is axially fixed only on one side.
  • the entire construction of the housing is such or the bearing of the shaft designed such that the shaft together with the seated piston and preferably also together with the shaft supporting the bearing plate are taken out axially to one side of the housing can, which can be made accessible in a simple manner for the purpose of the seal replacement or maintenance of the piston and the seals.
  • the engine may have a total, in particular unsymmetrical shape, in particular with regard to the end-side bearings.
  • the shaft or its crank section can basically have different cross-sectional geometries.
  • the shaft has a simple circular cross-section.
  • the shaft may also have a flattened, in particular oval or ellipsoidal cross-section.
  • a flattened, in particular oval or ellipsoidal cross-section advantages can be achieved with regard to the removal of the bending moment and the support of the deformation.
  • the shaft can thereby better conform to a corresponding mating contour, so that a better support can be achieved.
  • the shaft may have other polygonal-shaped cross-sections, which may be advantageous for the compensation of bending forces, depending on the application, for example, in longer-lasting designs.
  • the shaft may have a constant along its optionally helically bent axis constant cross section in the invention, wherein advantageously the shaft surface smooth without grooves and projections, as they would be present in a screw thread toothing, is formed.
  • the surface of the shaft can correspond to a continuous envelope surface, as occurs when, for example, a ball or a possibly differently shaped cross-sectional piece is moved along the optionally helically curved shaft axis.
  • the shaft cross-sections thus advantageously have a constant geometry along the optionally curved longitudinal axis without cracks or other irregularities such as toothed grooves or the like.
  • the shaft can advantageously be manufactured as an endless profile, which is cut to the desired length depending on the application, optionally also bearing journals being formed can be.
  • the shaft may have an integrally formed bearing journal on one side, while the other shaft terminates on the other side in its helical profile, which is supported on a bearing plate.
  • the journal is advantageously according to an embodiment of the invention larger than the shaft in the region of its helical profile.
  • the bearing pin can correspond approximately to the envelope, which wraps said helix or helical profile of the shaft.
  • the piston can also basically have different cross-sectional shapes.
  • the piston has an annular outer peripheral contour, wherein in particular one of receiving pockets for sealing elements except circular cylindrical outer surface may be provided.
  • the Wellen pressgangsaus originallyung in the piston may have different cross-sectional shapes, which are adapted in a further development of the invention to the respective shaft cross-section.
  • a rolling bearing may be provided preferably in the form of a ball bushing.
  • abrasion-resistant and low-friction plastics can be used to minimize friction, from which the piston can be made, where appropriate, even the same sealing elements can be molded with.
  • the rotary motor shown comprises a tubular, cylindrical housing 1, which is closed at its two end faces in each case by a Lagerdekkel 2.
  • the housing 1 can be made of an endless profile, which has been cut to the desired length.
  • a piston 3 is received axially displaceable, which divides the interior of the housing 1 into two pressure chambers 4 and 5, which can be acted upon in the illustrated embodiment via pressure medium lines in the bearing caps 2 with pressure medium, so that, depending on which the two chambers 4 or 5 is acted upon with pressure medium, the piston 3 moves axially in the housing 1 back and forth.
  • a drive shaft 6 is accommodated in the housing 1, which is rotatably mounted in the illustrated embodiment on both bearing caps 2, so that it can be rotated about an axis of rotation 7 parallel to the longitudinal axis of the cylindrical housing 1.
  • the drive shaft 6 in the illustrated embodiment is helically rotated about the said axis of rotation 7, wherein the drive shaft 6 to the said axis of rotation 7 has an eccentricity, which gives the respective engagement portion of the shaft with the piston a lever arm with respect to the axis of rotation 7.
  • the drive shaft 6 is screwed, so to speak, about the axis of rotation 7 around and actuates the lever arm on the wedge effect of the slope.
  • 1 to 3 drawn execution circular It can consist of an endless profile which has been cut to the desired length.
  • the piston 3 has a Wellen pressgangsausNOung 10 with which the piston 3 is longitudinally displaceable on the drive shaft 6, wherein the piston according to its preferably helical Wellen prepare for a rotation in the displacement on the shaft.
  • the Wellenen takegangsausappelung 10 is circular in cross section as the drive shaft 6, wherein viewed in the axial direction, the Wellen shedsaus principlesung 10 is adapted to the curved course of the drive shaft 6 and has a dekkungs Disease curved course with the shaft.
  • the geometry ratios and the arrangement of the drive shaft 6 are selected such that the Wellen oncegangsaus Principleung 10 is located substantially centrally in the cross-sectional area center of gravity of the piston 3, so that the piston 3 is balanced with respect to the forces induced by the drive shaft 6, in particular no tilting moments occur.
  • the drive shaft 6 is radially offset with its axis of rotation 7 with respect to the longitudinal center axis of the housing 1 and the piston 3, and advantageously as far as possible, so that the drive shaft 6 with a center as possible between their two ends or depending on the slope with several portions of the inner circumferential surface of the housing 1 is present or supported thereon. In Fig. 2 this point is indicated by the reference numeral 11.
  • the surface pairs which cause the transmission of force between the drive shaft 6 and the piston 3 and between the piston 3 and the housing 1, so the outer surface of the drive shaft 6 and the inner circumferential surface of the Wellen pressgangsausNFung 10 on the one hand and the piston outer lateral surface and the housing inner circumferential surface on the other hand sealing surface pairs, which seal the pressure chambers 4 and 5.
  • gaskets 12 and 13 are integrated in these surface pairs in order to avoid pressure losses.
  • the shaft seal 12 is seated in the illustrated embodiment in the Wellen shedgangsausEnglishung 10 and slides on the outer surface of the drive shaft 6 from.
  • the housing seal 13 is seated on the piston outer lateral surface and seals the piston 3 with respect to the housing 1, on which said seal 13 slides off. Both seals are formed in the illustrated embodiment as sealing rings.
  • the lever length and the pitch of the helical drive shaft 6 can be set almost arbitrarily.
  • a low pitch and a large lever arm generate great moments.
  • the piston surface can be used effectively, with equal forces in both directions can be achieved.
  • the entire housing internal cross-sectional area minus the shaft cross-sectional area is available as the effective piston area.
  • due to the low surface pressures and lubricant-free or low-pressure media such as water or air can be used.
  • the drive shaft 6 extends in its helical shape and pitch in the bearing plate 8 and transmits through its spiral shape over the entire surface of the torque on the bearing plate, where they can be secured only by means of an axial and / or radial securing, for example in the form of a screw 14 against withdrawal. If, for example, the pressure chamber 4, the in Fig. 4 shown, mandated with pressure medium, this pushes the piston 3 to the right, which is transmitted to the drive shaft 6, an axial force, the drive shaft 6 according to Fig.
  • the bearing plate 8 can remove the torque via a plurality of screw 15, whereby seals 16 and 17, the seal of the pressure chamber 4 is ensured.
  • Fig. 6 shows the drive shaft 6 with a directly connected or connected shaft frusto-conical output shaft 9.
  • the diameter of the output shaft stub 9 and the width of the bearing plate 8 is not greater than the diameter of the output shaft 6 itself, so that a shaft seal 12 for sealing the piston 3 relative to the shaft 6 can be pushed over the drive shaft stub 9 away on the drive shaft 6.
  • This is advantageously supported by a bevel 18 on the bearing plate 8.
  • the entire drive shaft 6 together with the connected output stub shaft 9 is designed such that an elastic sealing ring with an inner diameter corresponding to the outer diameter of the drive shaft 6, can be slid over the entire shaft assembly.
  • the drive shaft 6 is preferably connected at one of its ends releasably connected to a separately formed plate 8 as the location Fig. 33 ff show.
  • the support of the drive shaft 6 via a separate bearing plate 8 makes it possible to remove very high axial and transverse forces with superimposed torques without having to accept excessive production costs.
  • the drive shaft 6 sits with its spiral or helical course in a likewise spiral or helical recess 50 in the bearing plate 8.
  • the helical shaft portion is axially and / or radially fixed in the helical recess 51 of the bearing plate by means of a positive locking element 51 and possibly advantageously braced or spread, whereby the releasable joints caused by the helix radial clearance can be eliminated.
  • the form-locking element 51 is formed in this embodiment of a - roughly speaking - crescent-shaped thrust plate 52 which engages in a radially extending groove 53 in the drive shaft 6 and is supported on the bearing plate 8.
  • the bearing plate 8 is pushed on the drive shaft inward or rotated until the thrust plate 52 can be placed in the groove 53, after which the bearing plate 8 retracted can be.
  • the end face provided in the bearing plate 8 recess for receiving the thrust plate 52 can this purpose in FIG.
  • recess 54 which has oversize in the circumferential direction to allow the turning back.
  • the thrust plate 52 spreads between the preferably wedge-shaped groove 53 and the preferably conical recess 54 in the bearing plate 8, whereby a backlash, preloaded axial and radial lock is created.
  • FIGS. 35 and 36 show, instead of in Fig. 33 also show a toothed plate 56 used as a positive locking element for securing the shaft and the bearing plate use.
  • the toothed plate 56 is toothed at one end and tapered at the other end or wedge-shaped in order to be able to be tipped.
  • fastening screws 55 By means of fastening screws 55, a backlash-free radial and axial securing can also be created here, cf. Figs. 35 and 36 , wherein advantageously no rotation of the flange is necessary.
  • a thrust support ring 57 In the execution of the FIGS. 37 and 38 is used as a form-locking element 51 for fixing the drive shaft 6 in the helical recess of the bearing plate 8, a thrust support ring 57.
  • the bearing plate 8 is in this case in two parts, wherein advantageously the parting plane lies outside the fluid guide.
  • the thrust support ring may be designed to be multi-part or one-piece slotted resilient.
  • the thrust support ring 57 may be formed on the inside and / or outside conical and / or tapered, so that when contracting the two bearing plate parts axial and radial clamping of the connection is achieved.
  • a nominal gap may be present between the two bearing plate parts with respect to the helical recess formed in them, so that the two bearing plate parts during linear tightening of the clamping device connecting them while preventing relative rotation of the two bearing plate parts, which by linear guides, for example.
  • guide pins - preferably by means of guide screws 58 - can be effected, brace with respect to the helical contour and jammed on the drive shaft 6.
  • the drive shaft 6 can be held in the LagerplattenausEnglishung 50 by means of a sliding nut 59, as in the FIGS. 39 to 44 shown.
  • the thrust nut 59 is provided with an external thread and an internal thread, so that it can be screwed to the bearing plate 8 and the drive shaft 6 in order to clamp the drive shaft 6 in the Lagerplattenausnaturalung 50. According to the FIGS.
  • the thrust nut 59 is screwed by means of an internal thread to the drive shaft 6, wherein the helical contour is discontinued in the bearing plate 8, so that the drive shaft 6 with its shoulder, which forms the transition from the Helixkontur the drive shaft 6 to its threaded portion against the corresponding Shoulder can be stretched in the LagerplattenausEnglishung.
  • the thrust nut is supported on the bearing plate side on a conical Schubmutterausnaturalung, so that a Radialspiel eliminating centering is achieved, see. Fig. 42 ,
  • the helical contour of the drive shaft has a diameter taper, which can be produced in a simple manner, and thus a shoulder 60 with which it can be tensioned against the inside of the bearing plate 8.
  • a simple clamping nut 61 is screwed on the end face on the shaft end, which spans against the bearing plate 8 and thus pulls the shoulder 60 of the drive shaft 6 against the bearing plate 8, see.
  • Fig. 44
  • FIGS. 45 and 46 can be fixed by a slot thrust plate 62 in the helical recess 50 of the bearing plate 8, the drive shaft 6, which is inserted radially from the outside into a slot in the bearing plate 8 until it engages in a circumferentially provided groove on the drive shaft 6, see.
  • Fig. 46 The slot thrust plate 62 can be approximately lens-shaped overall - roughly speaking.
  • FIGS. 47 and 48 show a basically similar design, but here the slot thrust plate 62 is inserted from the inside into a slot-shaped recess in the bearing plate 8, which is formed deeper than the width of the slot thrust plate, so that the slot thrust plate 62 can first be inserted so deeply that the Drive shaft goes into the Lagerplattenaus Principleung 50.
  • the slot thrust plate 62 is then advantageously through pushed a cone or an eccentric screw 63 radially inwardly into the groove in the drive shaft 6 and clamped, see. FIGS. 47 and 48 , In principle, this could also be reversed and the slot thrust plate 62 first sunk in a too deep shaft groove and then stretched outwards into the bearing plate slot.
  • the drive shaft 6 has an end face, preferably a conical recess, into which an expansion cone 64 can be inserted axially in order to widen the wave contour.
  • the expansion cone can be pulled by a clamping screw in the shaft recess.
  • the expansion cone can be pressed.
  • the drive shaft can be widened into the plastication area, so that joint compression occurs.
  • FIGS. 51 and 52 An alternative drive shaft bearing plate connection show the FIGS. 51 and 52 .
  • the shaft section seated in the bearing plate recess 50 has a plurality of cylindrical, preferably also slightly conical, steps 65, which are preferably arranged within the helical contour or within the helical envelope surface of the drive shaft 6, so that they can be machined or otherwise machined out of the helix contour ,
  • the gradations are offset relative to each other with respect to their respective geometric axes, cf. 51 so that 50 moments are transmitted via the congruently formed gradations of LagerplattenausEnglishung can.
  • this design of the drive shaft-bearing plate connection allows a linear right-angled or paraxial pressing process and a simple manufacturing process.
  • the axial securing can be provided separately, for example in the form of a screw nut, which is screwed onto the shaft end and stretches against the bearing plate 8, cf. Fig. 52 ,
  • the drive shaft 6 may also have eccentrically offset circumferential surface sections 66 and 67 in the region of its shaft section located in the bearing plate 8, which may be formed in particular by a one-sided conical bevel in the otherwise helical contour of the drive shaft 6.
  • the bearing plate recess is designed to be complementary. By the offset of the two peripheral surface portions 66 and 67 and torques can be transmitted.
  • the drive shaft is axially secured as before by a nut and clamped to the bearing plate.
  • FIGS. 55 and 56 continue to show a pin connection between the drive shaft 6 and the bearing plate 8, wherein also here the drive shaft 6 is seated with a helically contoured shaft portion in the likewise helical Lagerplattenaus strictlyung.
  • Several pins 68 preferably threaded pins are advantageously introduced outside the fluid guide between the bearing plate 8 and the drive shaft 6, wherein the pins 68 are screwed in the illustrated embodiment radially from the outside into the bearing plate 8 until they engage in the drive shaft 6, see.
  • Fig. 56
  • the piston 3 of the rotary motor can basically be designed differently.
  • a piston carrier 19 is annular and forms with its radially outer portion of the outer circumferential surface of the piston 3.
  • the front end of the piston carrier 19 has two circular recesses, in each of which two inner half shells 20 and 21 can be used, each together an annular shell form, the inner circumferential surface together form the Wellen pressgangsaus principleung 10.
  • 20 and 21 of the inner sealing ring 12 can be used between the front-mounted inner half-shell pairs.
  • the one-piece piston carrier 19 advantageously has an inner diameter which is sufficiently large to be slid over the end bearing plates 8 of the drive shaft 6.
  • FIGS. 9 and 10 An alternative, also multi-part piston training show the FIGS. 9 and 10 ,
  • the piston 3 consists of two piston half-shells 22 and 23, which are auffactsetzbar in the radial direction.
  • the parting line 24 advantageously extends arcuately, as this Fig. 9 shows. In particular, it can follow the likewise arcuate course of the shaft passage recess 10, which corresponds to the helical course of the drive shaft 6.
  • the two piston half-shells 22 and 23 can be screwed together by means of screws 25 and centering sleeves 26.
  • Fig. 9 shows, two inner sealing rings 12 and two outer sealing rings 13 are provided on the piston 3 in the illustrated embodiment.
  • the piston 3 may also be formed in one piece.
  • FIGS. 11 and 12 show the FIGS. 11 and 12 , which requires the corresponding releasable connection of the drive shaft 6 with the bearing plates 8 and a formation of the bearing or driven shaft journal within the inner envelope of the drive shaft 7, as still in connection with FIGS. 30 to 32 is described.
  • two axially spaced-apart inner seals 12 and outer seals 13 are provided, each extending in an annular manner around the corresponding piston outer and inner circumferential surface. This can advantageously be used to fill between the respectively formed between a pair of sealing rings, annular pressure pockets 27 and 28 with hydraulic or pneumatic pressure from the respective pressure-responsive pressure chamber 4 and 5 respectively.
  • corresponding feed bores 29 are formed in the piston, on the one hand in the end faces open the piston 3 and on the other hand open into said pressure pockets 27 and 28 on the lateral surfaces of the piston between the sealing rings.
  • the connection of the feed holes 29 can be controlled with the respective pressure side, see. Fig. 11 .
  • the induced radial forces can be at least partially intercepted and on the other hand, the friction can be considerably reduced, which significantly improves the efficiency of the rotary motor.
  • the piston 3 may also have an oval cylindrical shape.
  • the piston chamber can be better utilized on the one hand by the displacement of the force application point.
  • the false lever to the flat side of the piston is smaller.
  • a greater wave jump can be achieved.
  • the envelope 31 of the helically bent drive shaft 6 is better, ie over a longer curve section to the inner circumferential surface of the housing 1.
  • a better support of the drive shaft 6 can be achieved on the housing 1, which is particularly important for longer designs in which the axial forces can induce larger shaft bends.
  • the drive shaft 6 may have an oval or ellipsoidal cross-section. This improves the stability of the drive shaft 6 in the bending direction.
  • the flat side of the oval or ellipsoidal cross section of the drive shaft 6 can better conform to the likewise oval or ellipsoid inner surface of the housing 1, whereby a better support is achieved.
  • the supporting effect can be further improved by the fact that the inner circumferential surface of the overall - roughly speaking - oval-shaped housing 1 experiences a constriction in the middle, so that the narrow side is better used on the envelope 31 of the drive shaft 6, as this Fig. 15 shows.
  • the drive shaft 6 can also receive an egg-shaped or polygonal cross-section which is thicker towards the envelope outside and thinner toward the inside, whereby the drive shaft 6 is optimized in terms of its bending and torsional rigidity.
  • the housing 1 and the outer circumferential surface of the piston 3 has such a polygonal cylinder contour, which is thicker on one side and thinner to the side on which the drive shaft 6 is supported.
  • a compact, force balanced cylinder can be achieved.
  • an adjustable spool 32 may be provided, which is associated with the pressure medium supply or discharge line 33 through which the pressure chamber 4 and 5 can be filled and emptied.
  • the opening cross section of said conduit 33 can be changed. Will he be completely closed, like this Fig. 17 shows, the piston 3 can not go further to the left; he has reached his final position.
  • two rotary motors can be synchronized in a simple manner with respect to their rotational movements over the printing medium.
  • the two rotary motors can be identical to each other and essentially the execution of the FIGS. 1 to 3 correspond.
  • the pressure chambers 4 and 5 of the respective motors are each filled via a common pressure line 34 and 35, which forks on a flow divider 36 and leads into the respective pressure chambers 4 and 5 of the two motors.
  • Fig. 19 shows, however, an embodiment of a rotary motor with two mechanically synchronized via a common piston 3 drive shafts 6.
  • the piston 3 in this embodiment advantageously has a flattened cross-section, in particular it may be formed oval or ellipsoidzylindrisch so that arranged on the resulting flat sides of the correspondingly shaped housing 1, the two drive shafts 6 can be.
  • the common piston 3 has in this case two Wellen pressgangsausEnglishisme 10, with which the piston 3 slides slidably on the two drive shafts 6.
  • the resulting radial forces, which are induced by the shaft in the piston 3 can be compensated.
  • a guide rod 37 may be used in the interior of the housing 1, which connects the two end - side housing - or bearing cap 2 together.
  • the piston 3 has a corresponding recess which is slidably seated on said guide rod 37.
  • the guide rod 37 causes in addition to the piston guide a power input for the hydraulic pressure by connecting advantageously the front-side housing sections.
  • the piston area is reduced, which can be of importance in particular for very large engine designs.
  • the waves can according to a further preferred embodiment of the invention also as in Fig. 20A shown to achieve a transverse force compensation.
  • Fig. 20A shows, acting in the installation position of the shafts shown there, the forces acting on the piston by the waves forces F1 and F2 against each other, so that the resulting bearing reaction force corresponds to about zero.
  • the axes of rotation 7 of the drive shafts 6 are not on the connecting line between the two Wellen pressgangsausEnglishept, but are offset transversely thereto, see.
  • Fig. 20A
  • the drive shaft 6 is also designed as a crankshaft, but it has a straight course, which is offset from the axis of rotation 7 of the drive shaft and extending parallel to said axis of rotation 7 , see. Fig. 21 .
  • the inner circumferential surface of the housing 1 is helically or helically about the axis of rotation 7 of the drive shaft 6 around in twisted or screwed, so that the piston 3 performs a helical rotation about the axis of rotation 7 at an axial displacement around.
  • the drive shaft 6 is rotated according to a crank.
  • Fig. 23 shows in the housing 1 and / or in the bearing cap 2 a Abtriebsüber GmbHs- or reduction gear 38 may be integrated.
  • the drive shaft 6 bearing bearing plate 8 have a spur gear, which meshes with an output gear 39 which drives an abrasion shaft 40, which is also mounted on the housing 1, the end side closing bearing cap 2 and passes through it, see.
  • Fig. 23 shows in the housing 1 and / or in the bearing cap 2 a Abtriebsüber GmbHs- or reduction gear 38 may be integrated.
  • the drive shaft 6 bearing bearing plate 8 have a spur gear, which meshes with an output gear 39 which drives an abrasion shaft 40, which is also mounted on the housing 1, the end side closing bearing cap 2 and passes through it, see.
  • Fig. 23 shows in the housing 1 and / or in the bearing cap 2 a Abtriebsüber GmbHs- or reduction gear 38 may be integrated.
  • the drive shaft 6 bearing bearing plate 8 have a spur gear, which meshes with an output gear 39 which drives an abra
  • FIGS. 24 and 25 show an embodiment that basically the of FIGS. 1 to 3 is similar and in other areas this corresponds.
  • the drive shaft 6 is not rigidly connected to the bearing discs or plates 8, but connected like a ball joint with them.
  • FIGS. 26 and 27 Similar to the execution of the FIGS. 11 and 12 also show the FIGS. 26 and 27 a one-piece piston, in which two axially spaced inner seals 12 and outer seals 13 are provided, each annular run around the corresponding piston outer and inner circumferential surface around. Unlike the execution after Fig. 11 In addition to this circumferentially extending seals axially extending sealing elements are provided which on opposite sides of the piston (see. Fig. 27 ) connect the two axially spaced seals 12 and 13 together. By said axial sealing webs 12a and 13a, the circumferentially between the seals 12 and 13 extending pressure pockets 27 and 28 are divided so that they are half-ring shaped on opposite circumferential sides.
  • the pressure pockets can be fed from the pressure chambers 4 and 5, depending on which side of the pressure applied to the piston 3. As FIGS. 26 and 27 show, said pressure pockets 27 and 28 fed via feed holes 29a and 29b once from the pressure chamber 4 and once fed from the pressure chamber 5.
  • FIGS. 28 and 29 show a corresponding piston training like the FIGS. 26 and 27 , In contrast, however, there are no two spaced apart, provided in the circumferential direction seals provided, but only such a seal, however, by an S-shaped curve, see.
  • Fig. 28 or simplified only diagonal course in sections on the pressure chamber 4 side facing and in an opposite section to the pressure chamber 5 facing side of the piston 3 is offset, in each case over about half the circumference of the piston.
  • This S-shaped or diagonal course like him Fig. 28 also shows two sector-shaped pressure pockets are divided from each other, which are fed in the above manner from the various pressure chambers 4 and 5 ago.
  • FIG. 30 shown further embodiment of the present invention are also formed between the piston 3 and the housing 1 and between the piston 3 and the shaft 6 opposed pressure pockets, which are delimited in the illustrated embodiment, however, by an annular seal 13 and 12, respectively each extends diagonally across the circumference of the piston, as this Fig. 30 shows.
  • the pockets get this way an oblique wedge-like training in which the depth of the pressure pockets viewed in the circumferential direction increases or decreases in opposite directions. It is understood that here is the one pressure pocket with the one piston side and the other pressure pocket with the other side of the piston in pressure communication, so that when pressure is applied to a pressure chamber which is fed a pressure pocket and pressurizing the other pressure chamber of the rotary motor, the other pressure pocket. This also allows a corresponding pressure relief can be achieved.
  • FIG. 30 shown embodiment of the rotary motor by the formation of the shaft 6 and the associated output shaft journal 9.
  • the shaft 6 has a relatively large shaft diameter with a relatively small eccentricity of the axis of rotation 7.
  • the bearing or drive shaft journal 9 are advantageously formed in the interior of the inner envelope profile of the shaft 6 and can thereby be integrally formed integrally with the shaft body.
  • Reference numeral 41 denotes the inner envelope profile of the shaft 6, within which said bearing or driven shaft journal 9 extends.
  • the shaft 6 is attached in the illustrated embodiment via two bearings 42 on the housing covers, which may be rigidly connected to the housing 1 in this embodiment.
  • the shaft 6 is clamped between two tapered roller bearings, which shorten the relevant for the bending of the shaft, effective bearing distance.
  • the bearing caps can be clamped on each other or on the housing 1.
  • seals 44 and 45 the respective bearing cap on the one hand against the bearing or driven shaft journal 9 and on the other hand sealed against the housing.
  • a particularly advantageous embodiment of the rotary motor shows Fig. 57
  • the housing or the bearing of the shaft is designed such that the drive shaft 6 can be taken out together with the seated piston 3 and together with the bearing cap 8 axially to one side of the housing 1, thereby easily to the Purpose of a seal change or maintenance of the piston and the seals can be made accessible.
  • a second bearing plate need not be dismantled for this purpose first.
  • the engine may have a total, in particular unsymmetrical shape, in particular with regard to the end-side bearings.
  • the drive shaft 6 is mounted differently at its two ends, namely at one end by a fixed bearing and the other end by a floating bearing, so that the shaft is axially fixed only on one side.
  • a statically determined storage of the shaft is achieved with a total of compact design with a play-free recording of the axial forces.
  • This compact design is particularly advantageous when using the rotary motor as a blade drive due to the very cramped space there.
  • the shaft is advantageously mounted at one end by means of a bearing plate or disk 8 in one of the aforementioned embodiments of the housing 1, preferably between the bearing plate and shaft releasably connected to one of the above embodiments according to the FIGS. 33 to 56 can be provided.
  • the drive shaft 6 has an integrally integrally formed shaft extension 69, which sits in a front-side housing cover and the floating bearing of the drive shaft 6 forms.
  • the shaft extension 69 has a larger diameter than the helical crankshaft section of the drive shaft 6 and can correspond in particular to about the helix of the drive shaft 6 inscribing imaginary cylindrical envelope surface, which in turn can correspond to the original shaft blank contour from which the shaft is worked out.
  • an overpressure protection 70 is provided between the two pressure chambers 4 and 5 of the engine, which has at least one connecting the two pressure chambers overpressure channel 71, which in the normal case, ie is closed by a pressure relief valve 72 at pressures below a predetermined threshold, which opens only when the said threshold value is exceeded.
  • the overpressure protection can basically be integrated in the shaft in the form of a shaft recess, as this Figure 57 shows.
  • the overpressure protection can alternatively or additionally also be integrated in the piston 3, which facilitates the introduction of the overpressure channel 72, in particular in the case of a helical course of the shaft 6.
  • an access point in the form of a screw plug 73 is provided in one of the frontal housing cover through which provided on the piston 3 pressure relief valve 72 through the housing can be actuated from the outside, cf. Fig. 57 ,
  • Fig. 57 shows, provided on the piston outside and inside seals 12 and 13 each have a diagonal course, whereby the oil skimming effect is vortail. Due to the constant change of plant in right-left-run a lubricating film cushion is built up by the repeatedly filling lubricating film bags, which seal themselves automatically when load changes on the cylinder wall.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (26)

  1. Moteur-couple, de préférence servomoteur à fraction de tour pour machines de chantier, engins de levage, camions et similaires, avec un carter oblong, de forme environ tubulaire (1), au moins un piston (3) logé axialement de manière mobile dans le carter (1), qui est actionnable axialement par admission d'un fluide de pression dans une chambre de pression (4, 5), ainsi qu'au moins un arbre (6) logé de manière fixe et rotative autour d'un axe de rotation (7) dans le carter (1), le piston (3) possédant un creux de passage d'arbre (10), avec lequel le piston (3) est assis de manière mobile axialement sur l'arbre (6), caractérisé en ce que l'arbre (6) constitue un vilebrequin, dont l'axe de rotation (7) est décalé par rapport au creux de passage d'arbre (10) du piston (3), le creux de passage d'arbre (10) étant disposé de manière centrée dans le piston (3) par rapport à la surface de section transversale de piston et le piston (3) étant rotatif par rapport au carter (1).
  2. Moteur-couple selon la revendication précédente, l'arbre (6) possédant un tracé hélicoïdal autour de son axe de rotation (7).
  3. Moteur-couple selon la revendication 1, l'arbre (6) possédant un tracé droit parallèle à son axe de rotation (7).
  4. Moteur-couple selon une quelconque des revendications précédentes, le carter (1) possédant une surface d'enveloppe intérieure en spirale.
  5. Moteur-couple selon la revendication 2, le carter (1) possédant une surface d'enveloppe intérieure cylindrique circulaire.
  6. Moteur-couple selon une quelconque des revendications précédentes, l'arbre (6) possédant une section transversale circulaire et le piston (3) possédant un contour de circonférence externe circulaire.
  7. Moteur-couple selon une quelconque des revendications précédentes, le creux de passage d'arbre (10) étant adapté dans le piston (3) à la section transversale de l'arbre (6), correspondant notamment à la section transversale d'arbre et/ou étant adapté dans son tracé axial au tracé axial du contour d'arbre.
  8. Moteur-couple selon une quelconque des revendications précédentes, une paire de surfaces entraînant le guidage mobile axialement et/ou l'appui mécanique radial du piston (3) sur le piston (3) et sur le carter (1) et/ou simultanément sur le piston (3) et sur l'arbre (6) constituant une paire de surfaces étanches pour l'étanchéité de la chambre de pression (4, 5) pour la pressurisation du piston (3).
  9. Moteur-couple selon une quelconque des revendications précédentes, un joint (12) étant inséré entre l'arbre (6) et le creux de passage d'arbre (10) dans le piston (3) et/ou un joint (13) étant inséré entre la surface d'enveloppe externe du piston et la surface d'enveloppe interne du carter, le joint (12), (13) étant constitué de sorte que des sacs de compression (27, 28) alimentables à partir de la chambre de compression (4, 5) sont constitués entre le piston (3) et le carter (1) et/ou entre le piston (3) et l'arbre (6).
  10. Moteur-couple selon la revendication précédente, des secteurs circonférentiels (41), (42) situés face l'un à l'autre étant limités sur la surface d'enveloppe externe du piston et/ou sur la surface d'enveloppe interne du creux de passage d'arbre (10) par des éléments d'étanchéité et/ou des sections d'éléments d'étanchéité (43, 44) s'étendant axialement dans le sens circonférentiel du piston (3) et constituant respectivement un sac de compression (27, 28), dont l'un est en relation de pression et d'écoulement avec l'une des faces frontales de piston et l'autre avec la face frontale de piston située en face, des secteurs circonférentiels (41), (42) situés face l'un à l'autre étant limités sur la surface d'enveloppe externe du piston et/ou sur la surface d'enveloppe interne du creux de passage d'arbre (10) par un élément d'étanchéité s'étendant diagonalement sur la circonférence du piston et constituant respectivement un sac de compression (27, 28), dont l'un est en relation de pression et d'écoulement avec l'une des faces frontales de piston et l'autre avec la face frontale de piston située en face.
  11. Moteur-couple selon une quelconque des revendications précédentes, un montage sur palier à roulement étant prévu entre le carter (1) et le piston (3) et/ou entre le piston (3) et l'arbre (6).
  12. Moteur-couple selon une quelconque des revendications précédentes, le piston (3) étant constitué en plusieurs parties, de sorte que chaque partie de piston est mobile individuellement par l'intermédiaire d'un talon de butée sur une extrémité de vilebrequin.
  13. Moteur-couple selon une quelconque des revendications précédentes, le piston (3) possédant un support de piston (19) annulaire, qui constitue au moins partiellement la surface d'enveloppe externe de piston et sur lequel une paire semi-monocoque interne est posable, qui constitue le creux de passage d'arbre à l'état assemblé.
  14. Moteur-couple selon une quelconque des revendications précédentes, le piston (3) possédant sur ses deux faces frontales situées l'une en face de l'autre des surfaces de piston effectives de taille identique.
  15. Moteur-couple selon une quelconque des revendications précédentes, le carter (1) et le palier de l'arbre (6) sur le carter étant constitués de sorte que l'arbre (6) est démontable axialement hors du carter (1) avec le piston assis dessus, notamment aussi avec une rondelle de palier (8) fixée sur l'arbre.
  16. Moteur-couple selon une quelconque des revendications précédentes, l'arbre (6) étant constitué différemment à ses deux extrémités et/ou logé différemment.
  17. Moteur-couple selon la revendication précédente, l'arbre (6) étant logé à une extrémité avec un palier fixe axial et sur son autre extrémité, avec un palier libre axial sur le carter (1).
  18. Moteur-couple selon une quelconque des revendications précédentes, l'arbre (6) étant logé respectivement à au moins une de ses extrémités sur une plaque et/ou une rondelle de palier (8), qui limite frontalement une chambre de pression (4, 5) respective et/ou alimentable par la pression dans la chambre de pression (4, 5), l'arbre (6) s'étendant dans un creux dans la plaque et/ou la rondelle de palier (8), et le couple se transférant par l'intermédiaire du creux intégralement sur la surface de la plaque et/ou la rondelle de palier (8).
  19. Moteur-couple selon la revendication précédente, le creux dans la plaque et/ou la rondelle de palier (8) possédant un tracé hélicoïdal, dans lequel s'étend l'arbre (6) avec son tracé également hélicoïdal, la section d'arbre hélicoïdale assise dans le creux étant fixée axialement et/ou radialement par rapport au creux, de préférence étançonnée par un élément mécanique.
  20. Moteur-couple selon la revendication 18, l'arbre (6) présentant dans la zone du creux de la plaque de palier (8) plusieurs échelonnements cylindrique circulaire se trouvant à l'intérieur de son tracé hélicoïdal et placés en position excentriques les uns par rapport aux autres, qui sont croisillonnables contre la plaque de palier.
  21. Moteur-couple selon une quelconque des revendications précédentes, l'arbre (6) possédant un pivot de palier et/ou de sortie (9) façonné de préférence intégralement, qui s'étend à l'intérieur d'une surface enveloppante interne du profil d'arbre et/ou avec son diamètre (dL) correspond environ au diamètre d'arbre (dw), déduction faite de la double excentricité d'arbre (ε), c'est-à-dire dL = dw - 2ε.
  22. Moteur-couple selon une quelconque des revendications 1 à 20, l'arbre (6) possédant un pivot de palier et/ou de sortie (9) façonné de préférence intégralement, qui est plus grand qu'un diamètre d'arbre et correspond pour l'essentiel à une surface enveloppante externe du profil d'arbre et/ou avec son diamètre (dL) correspond environ à la somme du diamètre d'arbre (dw) et au quadruple de l'excentricité d'arbre (ε), c'est-à-dire dL = dw + 4ε.
  23. Moteur-couple selon une quelconque des revendications précédentes, des sacs de compression alimentables étant constitués sur les points d'appui de l'arbre (6) entre le carter (1) et la section de palier côté arbre, des secteurs circonférentiels situés en face les uns des autres sur la surface d'enveloppe interne du creux de palier d'arbre du carter et le tourillon respectif côté arbre étant limités par des éléments d'étanchéité s'étendant axialement et/ou des sections d'éléments d'étanchéité dans le sens circonférentiel du tourillon et constituant respectivement un sac de compression, dont l'un ou l'autre peut être mis en relation avec la chambre de pression avoisinante selon le sens de rotation d'entraînement.
  24. Moteur-couple selon une quelconque des revendications précédentes, le piston (3) étant fabriqué en une matière à frottement à sec, de préférence un matériau synthétique résistant à l'abrasion et faible en friction, de préférence de la céramique et/ou du plastique.
  25. Moteur-couple selon une quelconque des revendications précédentes, le piston (3) étant constitué élastiquement dans au moins un sens de charge du moteur-couple de sorte que le piston (3) constitue un élément d'amortissement dans au moins le sens de charge nommé.
  26. Moteur-couple selon une quelconque des revendications précédentes, au moins la chambre de pression (4, 5) se trouvant en relation avec une conduite de surpression, dont le débit est commandé par une soupape de surpression, la conduite de surpression et la vanne de surpression étant disposées avantageusement dans le piston (3).
EP07723087.8A 2006-03-07 2007-03-07 Moteur-couple Not-in-force EP1991792B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202006003589U DE202006003589U1 (de) 2006-03-07 2006-03-07 Drehmotor
PCT/EP2007/001966 WO2007101679A1 (fr) 2006-03-07 2007-03-07 Moteur-couple

Publications (2)

Publication Number Publication Date
EP1991792A1 EP1991792A1 (fr) 2008-11-19
EP1991792B1 true EP1991792B1 (fr) 2013-05-15

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EP07723087.8A Not-in-force EP1991792B1 (fr) 2006-03-07 2007-03-07 Moteur-couple

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US (1) US20090090238A1 (fr)
EP (1) EP1991792B1 (fr)
KR (1) KR20080113028A (fr)
CN (1) CN101395386A (fr)
AU (1) AU2007222602B2 (fr)
CA (1) CA2642613A1 (fr)
DE (1) DE202006003589U1 (fr)
MX (1) MX2008011366A (fr)
RU (1) RU2008139606A (fr)
WO (1) WO2007101679A1 (fr)

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DE102008030362A1 (de) * 2008-06-26 2009-12-31 Kinshofer Gmbh Hub-/Schwenkmotor
DE102008030361A1 (de) * 2008-06-26 2009-12-31 Kinshofer Gmbh Wankstabilisatorsystem sowie Torsionsmotor zur Verstellung eines aktiven Wankstabilisators
US8534642B2 (en) 2009-02-02 2013-09-17 Dale Moretz Seal member for fluid transfer system
US20130042751A1 (en) * 2009-04-16 2013-02-21 Carl Romack Fluid-Actuated Controller Capable of Feedback Regulation
CN104220764A (zh) * 2012-02-09 2014-12-17 莫戈公司 旋转致动器
WO2013119242A1 (fr) 2012-02-09 2013-08-15 Moog Inc. Système d'actionneur et procédé associé
MX367696B (es) 2014-09-17 2019-09-02 Siemens Ag Instalacion electrica resistente a disparos.
DE202015006973U1 (de) * 2015-10-06 2017-01-10 Kinshofer Gmbh Hydraulischer Schwenkantrieb sowie Greifer mit einem solchen Schwenkantrieb
EP3403005B1 (fr) 2016-01-13 2022-01-12 Moog Inc. Ensemble actionneur rotatif tolérant aux défaillances et à addition
DE102018127295A1 (de) 2018-10-31 2020-04-30 HKS Dreh-Antriebe GmbH Vorrichtung zum Leiten von Hydraulikflüssigkeit

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US1828965A (en) * 1929-01-23 1931-10-27 Bucyrus Erie Co Dipper trip
US3183792A (en) * 1963-01-10 1965-05-18 Alton K Allen Free piston oscillator
HU177203B (en) * 1977-10-26 1981-08-28 Epitoegepgyarto Vallalat Working roll
US4426916A (en) * 1981-06-18 1984-01-24 Wimberley Lewis L Variable displacement motor
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JPS6184403A (ja) 1984-09-29 1986-04-30 Takashi Hosokawa 流体圧揺動モ−タ
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DE20107206U1 (de) * 2001-04-02 2002-08-08 Kinshofer Greiftechnik Antriebsvorrichtung für eine Greifeinrichtung

Also Published As

Publication number Publication date
US20090090238A1 (en) 2009-04-09
EP1991792A1 (fr) 2008-11-19
CN101395386A (zh) 2009-03-25
AU2007222602B2 (en) 2012-03-08
KR20080113028A (ko) 2008-12-26
RU2008139606A (ru) 2010-04-20
MX2008011366A (es) 2008-11-10
DE202006003589U1 (de) 2007-07-19
AU2007222602A1 (en) 2007-09-13
CA2642613A1 (fr) 2007-09-13
WO2007101679A1 (fr) 2007-09-13

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