EP1887229A1 - vérin rotatif et méthode pour la fabrication dudit vérin - Google Patents

vérin rotatif et méthode pour la fabrication dudit vérin Download PDF

Info

Publication number
EP1887229A1
EP1887229A1 EP06016270A EP06016270A EP1887229A1 EP 1887229 A1 EP1887229 A1 EP 1887229A1 EP 06016270 A EP06016270 A EP 06016270A EP 06016270 A EP06016270 A EP 06016270A EP 1887229 A1 EP1887229 A1 EP 1887229A1
Authority
EP
European Patent Office
Prior art keywords
shaft
piston
rotary motor
motor according
housing
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.)
Withdrawn
Application number
EP06016270A
Other languages
German (de)
English (en)
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kinshofer GmbH filed Critical Kinshofer GmbH
Priority to EP06016270A priority Critical patent/EP1887229A1/fr
Publication of EP1887229A1 publication Critical patent/EP1887229A1/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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

Definitions

  • the present invention relates to a rotary motor, preferably rotary drive for construction machinery, trucks and the like, with an elongated, preferably approximately tubular housing, a piston axially slidably received in the housing, which is axially displaceable by applying pressure medium in a pressure chamber, and a in the housing axially fixed, rotatably received shaft, wherein the piston is in threaded engagement with the shaft and / or the housing.
  • the invention further relates to a method for producing such a rotary motor.
  • Such a rotary motor is for example from the DE 201 07 206 known, in which the piston is on the one hand rotatably guided on the inner circumferential surface of the circular cylindrical housing and on the other hand is in threaded engagement on a threaded portion of the shaft. If the piston is displaced axially by hydraulic loading in the housing, its axial movement is converted via the screw engagement into a rotational movement of the shaft. In order to seal the piston relative to the housing and the shaft and thus to be able to apply correspondingly hydraulic pressure via the pressure chamber, the piston has one of the screw engagement section spaced sealing portion which slides on the one hand on a shaft sealing portion and on the other hand on the Gescouseinnenmantel components and is sealed.
  • 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 present invention seeks to remedy this situation. It is the object of the invention to provide an improved rotary motor of the type mentioned, which avoids the disadvantages of the prior art and the latter develops in an advantageous manner.
  • a compact design rotary motor is to be created, which is characterized by favorable torque generation and transmission on the piston.
  • the present invention thus leaves the previous approach to separate the sealing of the piston on the shaft and the housing of the portion causing the rotary guide or the screw engagement.
  • a pair of surfaces on the piston and shaft and / or piston and housing, which causes the screw engagement simultaneously forms a sealing surface pair for sealing the pressure chamber for pressurizing the piston.
  • the same piston section simultaneously serves for torque transmission and sealing. In this way, a considerably shorter overall length can be achieved, since the axial spacing between the sealing portion and Dreh Inserts- or screw engagement portion of the piston is eliminated.
  • the respective components, in particular housing and shaft can be produced endlessly and tailored to requirements and lengths.
  • the piston on its two opposite sides the same size effective piston surfaces, so that no oil storage required per se is.
  • the full piston area can effectively be used with equal forces in both directions.
  • 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 pressures in both drive directions.
  • for a given pressure results in a maximum torque output.
  • the screw engagement between the shaft and the piston is not achieved by a conventional threaded toothing section of the shaft and the piston.
  • the shaft is twisted in itself, so that its outer contour forms a helically twisted about the longitudinal axis of the shaft polygonal profile. This not only simplifies the production, but also improves the sealability between shaft and piston.
  • the standing with the twisted polygonal profile in screw-engaging inner circumferential surface of the piston can be formed free of thread teeth and have a continuous, continuous surface course without indentations and protrusions, so that the piston and the twisted polygonal profile of the shaft sitting on each other in the manner of a sliding bearing surface pair.
  • a seal can be inserted into the piston inner circumferential surface which is screwed into engagement with the shaft and seals the piston on the outer contour of the shaft.
  • the piston inner peripheral surface is advantageously also formed as a polygonal profile surface, which can be approximately cylindrical in axially very short design of the piston, and otherwise easily twisted about the longitudinal axis of the piston, as is the shaft.
  • a screw engagement could also be provided between the housing and the piston, in particular in that the housing also forms a polygonal profile twisted spirally around its longitudinal axis.
  • the housing has a cylindrical inner surface, which advantageously has a deviating from the circular cross-sectional geometry at which the piston is guided with its outer lateral surface longitudinally displaceable and rotatably supported.
  • the housing may have a flattened, preferably approximately elliptical or oval cross-section. As a result, a flat construction of the rotary motor can be achieved.
  • the housing may have on the outside a substantially rectangular contour.
  • a favorable torque removal can be achieved because a large lever arm is achieved.
  • the housing may be formed so flattened that a longitudinal axis of the cross section by at least 30%, preferably more than 50%, is longer than the transverse axis of the cross section.
  • the housing has a cross-section free of kinks and edges, whereby the sealability is improved.
  • an elliptical or oval cross-section combines a good sealability with a favorable torque removal.
  • an annular circumferential seal may be used to achieve a substantially leak-free sealing of the pressure chamber.
  • the spirally twisted polygon profile of the shaft may also advantageously have a flattened cross-section, z. B. rectangular or in particular elliptical or oval.
  • the cross section may advantageously have a longitudinal axis that is longer than the transverse axis of the cross section by at least 30%, preferably more than 50%.
  • a square cross-section or a hexagonal profile can be used, in which the ratio of longitudinal axis to transverse axis of the cross section is substantially 1: 1.
  • the cross section is also formed free of sharp creases or edges in the shaft, in order to improve the sealability.
  • the shaft is designed as a wing shaft having at least one screwed around the shaft axis, strip-shaped projection on the circumference, can be removed optimally on the torques with the most compact dimensions.
  • the wing shape can be designed in particular double-leaf, d. H.
  • the shaft has two opposite radial projections, which are each strip-shaped and screwed around the shaft axis. These projections form, so to speak Abtragsnasen for removal of torques.
  • the shaft according to an advantageous embodiment of the invention may comprise circular cylindrical segments.
  • Each seated on the shaft piston has an adapted to said wave contour inner peripheral surface in which are adapted to the aforementioned wing of the shaft, groove-shaped recesses are provided which engage around the wings and cause the Drehmomentabtrag between shaft and piston.
  • the piston can also have a wing shape.
  • a wing piston advantageously has also at least one radial, strip-shaped projection, which engages in a corresponding, it encompassing groove-shaped recess in the inner peripheral surface of the housing.
  • the piston has two opposing wing-like, radial projections which engage in corresponding recesses in the inner peripheral surface of the housing.
  • the housing is formed in compound or compound construction.
  • a composite housing may have a plurality of shells which are interlocked and interconnected.
  • at least one inner shell which is in engagement with the piston and can be adapted to the outer contour, as well as an outer shell of the housing forming outer shell provided.
  • These two shells can be connected directly to each other, in particular glued, with appropriate design of the outer shell.
  • a support body made of a suitable integral material, preferably hard foam, aluminum foam or other suitable casting and / or foam mass may be provided between the inner shell and the outer shell, which connects the inner shell with the outer shell.
  • the housing is particularly suitable for mass production.
  • the housing may be made in forming technology, for example, hydraulic cylinder tubes can be brought while maintaining their surface quality by flattening and / or spreading in the desired flattened shape.
  • the piston is mounted on the housing and / or on the shaft by sliding bearings.
  • the slide bearing surfaces on the outer lateral surface and / or on the inner lateral surface of the piston can simultaneously form the sealing surfaces into which separate seals can be inserted, if necessary.
  • a slight leakage over the sliding bearing surfaces of the piston can be accepted. If this is to be avoided, it should be noted in any case that in the sliding bearing surfaces on the outer and / or inner circumferential surface of the piston seals can be used in a simple manner.
  • the piston may have hardened lateral surfaces which form the plain bearings. Alternatively or additionally, separate plain bearing inserts may be provided on the lateral surfaces of the piston.
  • the piston, in particular its lateral surface can also be made of a soft, plasticizing material, wherein the housing is then made of appropriate material in order to achieve a matching sliding bearing surface pairing.
  • the piston may be supported on the housing and / or on the shaft by rolling bearings.
  • the rolling elements are arranged on the piston and roll on rolling elements rolling surfaces on the housing and / or on the shaft.
  • on the housing and / or on the shaft preferably hardened rolling bearing guide tracks be provided.
  • contour rolling bodies are adapted, the running surface of which is adapted to the contour of the housing or of the running surface formed thereon.
  • the twisted polygonal profile of the shaft can basically have a constant pitch over the length of the shaft.
  • a constant implementation of the oil supply is achieved in a corresponding rotational movement over the entire travel of the rotary motor.
  • the twisted polygonal profile of the shaft may also have a pitch that varies along the length of the shaft.
  • a torque adjustment and a rotational speed adjustment of the rotary motor can be achieved, for example, a reduction in the rotational speed can be provided towards the end of the travel path.
  • At least two oppositely moving pistons can be arranged on the shaft, wherein advantageously the shaft and / or the housing opposite screw engaging portions, so that one piston left-handed and the other piston cooperates right-handed with the shaft.
  • the bearings of the shaft need only absorb radial forces, the axial forces exerted by the piston on the shaft cancel each other out.
  • the two pistons advantageously sit on the same twisted polygon portion of the shaft and are axially biased to each other.
  • the axial bias between the two pistons can be accomplished mechanically, for example, by a spring and / or hydraulically by pressurizing the gap between the two pistons.
  • the shaft can advantageously be mounted by means of two bearing caps, which sit axially on the opposite ends of the housing. It can be provided between the bearing caps and the shaft seals each for sealing the pressure chamber.
  • the seals are integrated into the respective bearing surface, on which the shaft is supported on the bearing cap.
  • the bearing of the shaft on the bearing cap can advantageously be a sliding bearing.
  • a rolling bearing with rolling elements between the respective bearing cap and the shaft can also be provided here.
  • the shaft passes through the bearing caps on both sides.
  • the protruding at the respective housing end stub shafts can form the output elements through which the torque is delivered.
  • the polygonal profile of the shaft deviating in cross section from the circular shape can be used directly to achieve the torque removal.
  • a connecting piece for removing the torque can be rotatably attached to the shaft ends, for example, be welded or pressed.
  • the twisted polygon profile can be given to the shaft in various ways. If necessary, it could be thought to work out the polygon profile by machining. According to an advantageous aspect of the present invention, however, the twisted polygonal profile is produced by chipless forming.
  • the shaft may consist of a substantially cylindrical shaft blank, which has a deviating from the circular shape polygonal profile cross-section, are formed. This shaft blank can be deflected from an endless bar profile to the desired length.
  • the shaft blank is twisted by non-cutting deformation about its longitudinal axis in itself, so that it forms with its outer contour the screw engagement with the piston causing, twisted in itself polygonal profile.
  • the forming can be done by cold twisting or hot twisting.
  • the production of the shaft does not have to be completely without cutting.
  • the surface of the shaft can be machined, in particular polished, before or after twisting.
  • the shaft blank may be given its polygonal profile by machining. However, the rotation of the polygon profile is advantageously without cutting.
  • the shaft blank is advantageously rotated in opposite directions from a gear change section starting to opposite sides.
  • the shaft produced thereby is formed from an integrally integral shaft blank.
  • two counter-rotated shaft blanks can be rigidly connected to one another, in particular welded together and / or screwed together, so that the shaft resulting therefrom has two counter-rotating shaft sections.
  • the rotary motor 1 shown in Figure 1 comprises a cylindrical tubular housing 2 made of an endless bar stock and deflected to the desired length.
  • a shaft 3 is arranged in the housing 2 coaxially with the longitudinal axis thereof and rotatably mounted on two bearing caps 4 which close the housing 2 on the end side, but are axially fixed.
  • the shaft 3 is additionally supported centrally by a floating shaft bearing 5 on the housing 2 in order to prevent bending of the shaft 3.
  • the shaft 3 advantageously has a flattened cross-section, as shown for example in FIG.
  • the longitudinal axis 6 of the cross section is in the illustrated embodiment of Figure 2 more than twice as long as the transverse axis 7 of the cross section.
  • the cross section of the shaft 3 forms a flattened polygonal profile deviating from the circular shape with two flat sides 8 parallel to one another, which are bevelled to the narrow side 9, so that the cross-sectional profile is free of wrinkles and edges (see FIG.
  • the polygonal profile of the shaft 3 is spirally twisted in itself, wherein the shaft 3 has a gear change in its center. From the central gear change section, the shaft 3 is twisted towards its two ends in different directions, so that one half of the shaft is left-handed and the other half of the shaft is right-handed.
  • pistons 10 in the housing 2 are axially displaceable, but guided in a rotationally fixed manner, so that an axial movement of the pistons 10 is converted into a rotational movement of the shaft 3 relative to the housing 2.
  • FIG. 2 shows, the rotationally fixed guidance of the pistons 10 in the housing 2 is brought about by the fact that the housing 2 has a cross section deviating from the circular shape.
  • the housing 2 can, as Figure 2 shows, have a flattened, substantially oval or elliptical cross-section which corresponds substantially to the outer cross section of the piston 10.
  • the pistons 10 can be driven axially by being exposed to a pressure medium, which may in principle be air or another gas, but advantageously a liquid, in particular hydraulic oil, so that the shaft 3 carries out the desired rotational movement.
  • a pressure medium which may in principle be air or another gas, but advantageously a liquid, in particular hydraulic oil, so that the shaft 3 carries out the desired rotational movement.
  • the pistons 10 are sealed both with respect to the shaft 3 and with respect to the housing 2.
  • a pressure medium which may in principle be air or another gas, but advantageously a liquid, in particular hydraulic oil
  • a pressure chamber 15, 16, 17 and 18 is provided on each side of the piston 10, which is bounded by the housing 2 and in the case of the pressure chambers 15 and 18 through the housing cover 4 next to the respective piston surface.
  • the pressure chambers 15, 16, 17 and 18 can be filled in a conventional manner with pressurized fluid to move the piston 10 back and forth.
  • the pressure supply system comprises 19 while pressurized fluid feed channels 20, which extend in the interior of the shaft 3. These can be in communication with pressure fluid feed channels 21, which extend in the interior of the pivot lever 29, which are non-rotatably mounted on the stub shafts 23, which emerge through the bearing cap 4 from the housing 2.
  • the pistons 10 are slidably mounted relative to the housing 2 and the shaft 3, respectively.
  • the outer circumferential surface and the inner circumferential surface of the pistons 10 each form sliding bearing surfaces.
  • the bearing cover 4 which closes the housing 2 at the end can be screwed to the housing 2.
  • Mounting lever 24 and abutment can be advantageously integrated into the bearing cap 4 to intercept torques initiated by the housing 2.
  • the shaft 3 is mounted in the bearing caps 4 each have a bearing ring 25 which is fixedly connected to the shaft 3 and is rotatably mounted in the bearing cap 4.
  • Axial forces as well as radial forces can be absorbed by the bearing rings 25, although axial forces are compensated for by the double piston arrangement and thus substantially only radial forces act on the shaft.
  • Figure 4 shows the shaft 3 centrally supporting floating shaft bearing 5 in greater detail.
  • An intermediate bearing ring 26 is seated firmly on the gear change section of the shaft 3 and is floating supported in a guide plate 27 having a cylindrical or slightly spherically curved inner recess in which the intermediate bearing ring 26 is received.
  • the guide plate 27 On its outer circumference, the guide plate 27 is adapted to the oval or elliptical housing profile and supported on the housing 2.
  • the tap of the torque from the shaft 3 can basically be done in various ways.
  • the shaft 3 may have at its two front ends two turned shaft stumps 13 which pass through the respective bearing cap 4 and advantageously each have at least one flattening 28, to which the respective pivot lever 29 are attached can.
  • the stub shaft 13 is thus made integrally from the material of the shaft 3.
  • the polygonal profile section for screw engagement with the respective piston 10 extends only within the housing up to the bearing caps 4 (see FIG.
  • the stub shaft 13 can also, as shown in FIG. 6, initially be manufactured as a separate component and then attached to the shaft 3 and connected thereto in a rigid and non-rotatable manner.
  • the stub shaft according to FIG. 6 can be welded to the shaft 3, a flattening 28 being provided here as well.
  • the shaft 3 itself can be passed with its twisted polygonal profile through the bearing cap 4 and stored on this.
  • a bearing ring 30 which is rotatably mounted in the respective bearing cap 4, but axially fixed, as Figure 7 shows.
  • the bearing ring 20 may be welded to the shaft 3, for example.
  • the shaft 3 is axially fixed, but rotatably mounted.
  • the outer bearing of the piston 10 on the inner circumference of the housing 2 can basically be done in various ways.
  • the plain bearing shown in Figure 2 in which the sliding bearing surface of the piston is formed by the material itself, may also be provided according to Figure 8 that in the outer peripheral surface of the respective piston 10 corresponding sliding bearing blocks 31 are used made of special plain bearing material.
  • these sliding bearing blocks 31 are offset away from the center to the flat sides of the piston in order to achieve the largest possible lever arm in the torque support on the housing 2, as Figure 8 shows.
  • the sliding bearing blocks 31 are located in the outer third of the piston 10 relative to the cross-sectional longitudinal axis of the piston 10.
  • the circular contours allow the bearing blocks 31 to align themselves in the spherical socket-like receptacles in the piston 10 and accordingly adapt to the contour of the housing or the load transfer.
  • the sliding bearing blocks 31 are advantageously offset in the axial direction of the piston 10 to the pressurization sides and arranged in pairs on opposite sides of the housing seal 14.
  • the arrangement of the housing seal 14 centrally between the sliding bearing blocks 31 ensures their lubrication, since from the respective pressure chamber forth pressure medium between the piston outer lateral surface 13 and the Gescouseinnenmantel specifications can pass until it hits the seal 14.
  • the respective piston 10 may also be supported by a roller bearing 32 on the housing 2.
  • the rolling bodies 33 can be centrally arranged with respect to the longitudinal direction of the piston 10 and, viewed in the cross section according to FIG. 10, can be moved outwards in the direction of the longitudinal axis of the cross section towards the narrow side of the piston 10 in order to provide a good lever arm to achieve the torque swing.
  • at least two rolling elements 33 but advantageously at least four rolling elements 33, provided, wherein the rolling elements may optionally be formed elastically.
  • housing seals on the piston 10 can be provided on the outer circumferential surface 13 of the respective piston 10 to the right and left of the roller bearing 32.
  • the roller bearing 32 can advantageously also comprise several pairs of rolling elements 33 which, viewed in the axial direction of the piston 10, are arranged one behind the other and are moved toward the two pressure application surfaces of the respective piston 10. As a result, to a certain extent tilting movements of the piston 10 can be better absorbed.
  • a central seal 14 may be used on the outer circumferential surface 13 of the piston 10 to seal it with respect to the housing 2, which, as shown in FIG. 12, is arranged between the rolling elements 33 as seen in the axial direction. This can Pressure medium between the piston outer lateral surface 13 and the inner circumferential surface of the housing 2 penetrate and thereby lubricate the rolling elements 13.
  • a pressure channel system 34 may be formed, which may advantageously have a pressure storage property or an actual pressure accumulator 53, wherein the pressure channel system 34 via a feed bore 35 with the bearing point of the piston 10 on the housing 2 and / or via a feed bore 36 with the bearing point of the piston 10 is connected to the shaft 3 to give there lubricant.
  • the pressure channel system 34 may be fed by the pressure chambers for actuating the piston 10, as shown in FIG.
  • the pressure channel system 34 in the interior of the piston 10 can communicate via supply bores 37 and check valves 38 with the end faces of the piston 10 to be supplied with pressurized fluid upon pressurization of the respective chamber.
  • seals 12 and 14 can be provided on both sides of the bearing points.
  • each piston 10 comprises two piston parts 10a and 10b, which are mutually axially displaceable, but both are rotatably guided on the housing 2 and are in screw-threaded engagement with the shaft 3.
  • a spring device 39 which may be a compression spring in the embodiment shown in Figure 14, the two piston parts are axially biased to each other.
  • the two piston parts 10a and 10b it is also advantageously possible for the two piston parts 10a and 10b to be prestressed by the pressure medium.
  • the intermediate space 40 communicates between the two piston parts 10a and 10b via check valves 38 with the respective pressure-loaded side of the piston 10, which is the right-hand side in FIG.
  • the pressure fluid passes with the pressure P in the intermediate space 40, so that in this pressure P prevails.
  • the rear piston part 10b follows without pressure, since the same pressure P is applied on both sides.
  • About the compression spring 39 ensures that each front in the direction of movement piston member which removes the pressure, or the piston guide provided thereon, abuts the respective forward screw thread flank, so that a game is excluded.
  • Figure 15 shows a similar piston design 10 with bias and thus backlash.
  • the pressure P is, however, removed in this case via the respective rear piston part, the spring device 39 in this case consisting of tension springs, which attempts to pull the two piston parts 10a and 10b or the guide elements towards each other, so that they engage in play without screwing the shaft 3 stand.
  • both piston parts 10a and 10b are rotatably guided on the housing 2 and in screw engagement with the shaft 3 in the embodiment of FIG.
  • the piston 10 instead of a plain bearing have a rolling bearing 41.
  • the shaft 3 may have a substantially rectangular cross-section, with the inner roller bearing 41 of the piston 10 having rolling elements 42 which sit on the edge of the flat sides of the wave profile, as FIG. 16 shows.
  • the rolling elements 42 may optionally have edge webs, over which they are guided on the narrow sides of the polygonal profile of the shaft 3.
  • the rolling bodies 42 can be arranged centrally on the inner circumferential surface 11 of the piston 10, viewed in the longitudinal direction.
  • shaft seals 12 may be arranged on both sides of the inner roller bearing 41 on the inner circumferential surface 11 of the piston 10.
  • a plurality of pairs of rolling elements 42 can also be arranged in the rolling bearing 41 on the inner circumference of the piston 10 in the axial direction, as shown in FIG. 18. Due to the arrangement of the rolling elements to the pressurized end faces of the piston 10 out acting on the piston 10 tilting moments can be better absorbed to some extent. In addition, a arranged between the rolling elements 42 seal 12 is sufficient, so that at the same time an external lubrication of the bearings is possible because when pressure is applied from one side pressure medium between the shaft 3 and the inner circumferential surface 11 of the piston 10 can pass.
  • the piston 10 may also be supported by ball-like guide elements 43 on the flanks of the shaft 3.
  • the ball-like guide elements 43 are used in ball sockets in the inner peripheral surface 11 of the piston 10, so that they can rotate multi-axially and thus adapt to changes in pitch.
  • the ball-like guide elements 43 can form sliding blocks which slide the piston 10 on the shaft 3.
  • rolling bodies it is conceivable for rolling bodies to be fastened to the ball-like guide elements 43 in order to achieve rolling bearing.
  • a roller bearing of the piston 10 on the shaft 3 need not be limited to an arrangement of the rolling elements on the flat sides 2 of the shaft 3.
  • the mecanical section 41 of the piston 10 may also comprise rolling elements 42 which run on the narrow sides 9 of the polygonal profile of the shaft 3.
  • concave raceways for the crowned rolling elements 42 are introduced into the narrow side 9 of the shaft 3 so that they also lead transversely to their running direction.
  • FIG. 22 An alternative to this is shown in FIG. 22.
  • the narrow sides 9 of the shaft 3 can also form spherical guide tracks for the rolling bodies 42, which in this embodiment have a convexly curved running surface (compare FIG. This also allows a transverse guidance of the rolling elements 42 relative to the shaft 3 can be achieved.
  • the corresponding slide bearing surfaces can in principle be formed directly from the material of the piston 10.
  • the inner circumferential surface of the piston 10 can be hardened and / or processed in a suitable manner.
  • sliding blocks 44 made of suitable plain bearing material can be inserted into the inner circumferential surface 11 of the pistons 10, as FIG. 23 shows.
  • the shaft 3 has a substantially rectangular cross-section with the side edges 45 beveled towards the edge.
  • the rear side may be circular in order to achieve a self-adjustment ,
  • the sliding blocks 44 can also be provided on the narrow sides 9 of the polygonal profile of the shaft 3.
  • the sliding blocks 44 in this case have a convex sliding surface, which is inserted in a concave sliding surface in the narrow side 9 of the shaft 3, as shown in Figure 24.
  • the sliding blocks 44 may be formed by hardened round wire sections, which are inserted into the shaft 9 and on which the piston 3 runs in the manner shown in Figure 24 with its narrow sides.
  • the rolling elements 42 can be performed in principle in a correspondingly formed to the shaft body curve WälzSystemhimfig.
  • an internal rolling bearing 41 with circumferential rolling elements 42 and return of the rolling elements 42 may be provided, as shown in FIG.
  • the respective piston 10 can be provided a WälzSystemschreib enclosureskanal 46 through which the rolling elements 42 are returned from the end of the WälzSystembahn between the piston and shaft 3 to the beginning of said WälzSystembahn. This results in a continuous circulation of the rolling elements 42, as indicated by the arrow 47 in Figure 25.
  • FIG. 27 illustrates the return of the rolling bodies 42 via the rolling body return duct 46.
  • the return is advantageously designed in such a way, in particular in the embodiment shown in FIG. 25, that a lifting of the balls is ensured and they can be returned, as it were, without force.
  • the bearing cap 4 With regard to the attachment of the bearing cap 4 on the housing 2, there are various possibilities.
  • the bearing cap 4 In addition to the screw connection shown in Figure 28 of the bearing cap 4 at the end faces of the housing 2, the bearing cap 4, as shown in Figure 29, also be welded to the housing 2.
  • the bearing caps 4 can also be inserted into the cylindrical housing 2 and secured to its inner lateral surface by retaining rings 48 (see FIG.
  • the shaft 3 may be made in one piece, even if it has a gear change and has at least one right-handed and at least one left-handed section, as shown in FIG.
  • This can be done by a gear change section 49 starting from the initially cylindrical, deviating in cross section from the circular shape shaft blank are rotated in opposite directions to its ends, for example by cold forming or hot forming, so that shown in Figure 31 right-handed and left-handed screw engaging portions 50a and 50b arise.
  • the in-itself rotation of the wave profile can be stopped in order to obtain non-twisted shaft stubs 23, which facilitate the connection of corresponding pivot levers for torque tapping.
  • the bearing rings 20 described above can be welded to store the shaft 3 in the bearing caps 4 can.
  • the double-threaded shaft 3 can also be manufactured from two pieces, as illustrated in FIGS. 32 to 34.
  • Two self-twisted shaft pieces can be screwed together face each other, preferably via two coupling pieces 51 which sit axially fixed on the shaft pieces and be elastic or can cause a flexible coupling (see Figure 32).
  • the two shaft pieces of the shaft 3 can also be connected to one another in a material-locking manner, in particular by a friction welding 52 (see FIG.
  • FIG. 34 shows, a screw connection or butt joint of the right-handed and left-handed shaft pieces is also possible.
  • the two shaft pieces can be inserted into a fitting sleeve, in which they are fixed by cross-bolting.
  • the housing 2 is extruded or designed as an extruded profile.
  • a housing can be produced whose outer contour deviates from its inner contour.
  • the outer contour which is formed substantially rectangular in accordance with FIGS. 35 and 36, can be adapted to the respective installation situation.
  • the inner contour of the housing 2 can be designed so that the largest possible piston useful area is achieved becomes.
  • the housing profile has a plurality of axial bores in which tie rods or bolts are added, for example, to secure the end-side cover.
  • the inner contour of the housing 2 nestles around these axial bores and, moreover, follows the outer contour by the required wall thickness in order to achieve the largest possible piston cross-sectional area.
  • the central shaft bearing 5 may be attached to the threaded rods and the central shaft bearing 5, which supports the shaft 3 in the middle of its gear change section.
  • the central shaft bearing 5 can also be designed as an axial bearing in order to be able to absorb, for example, residual axial forces resulting from inclination errors of the shaft.
  • Figure 36 shows in the guide plate 27 has two through holes 50, through which the pressure chambers 16 and 17 are interconnected.
  • the shaft 3 and the piston 10 each have a wing shape.
  • the shaft 3 comprises a cylindrical, in particular circular cylindrical base body 63, on the outer surface Abtragsnasen 60 are provided in the form of strip-shaped wing projections 64, which are arranged opposite to each other and wound around the axis of rotation of the shaft 3.
  • the wing shaft thus formed can advantageously be made by milling.
  • the aforementioned strip-shaped wing projections 64 run in a spiral shape and may advantageously be integrally formed integrally with the base body 63.
  • the maximum shaft diameter measured in the area of the opposing wing projections 64 is approximately 30 to 40% greater than the minimum shaft diameter measured in the region of the main body 63, cf. FIG. 37.
  • the basic body 63 has a rather large diameter in the case of a circular-cylindrical shape in order to achieve good torque removal, wherein the wing projections 64 are dimensioned with their radial projection only so large that the allowable surface pressures are met during torque erosion. As a result, the volume to be displaced can be kept small.
  • the shaft 3 can be designed in particular as a torsion shaft with a large pitch.
  • the shaft 3 is formed as a hollow shaft. This not only causes a weight reduction.
  • the axial recess 61 can be used in the interior of the shaft 3 as a bore for the oil guide.
  • the piston 10 is adapted with its inner peripheral surface to the outer contour of the shaft 3.
  • the piston 10 in the illustrated embodiment of Figure 37 has a circular cylindrical inner recess which has groove-shaped recesses on opposite sides, which engage around said wing projections 64 in a form-fitting manner, cf. FIG. 37.
  • the piston 10 On its outer contour, the piston 10 also on opposite sides has two Abtragsnasen 62 in the form of strip-shaped, radial wing projections 65, see. FIG. 37. Between the aforementioned wing projections 65, the outer contour of the piston 10 is delimited by a segment-wise circular-cylindrical and / or elliptical peripheral surface.
  • the inner peripheral surface of the housing 2 is adapted in a corresponding manner to the wing shape of the piston 10.
  • the rotary motor may also have the flattened, in particular elliptical or oval cross sections shown in FIG.
  • the shaft 3 may be formed in this embodiment as a hollow shaft, whereby the inner Axialaus Principleung 61 can be used as a bore for the oil supply.
  • the shaft 3 is in this case with its oval or elliptical cross section in itself, ie, about its axis of rotation, twisted, so that it forms an oval or elliptical spiral shaft as a whole.
  • the shaft 3 can be cast and ground in particular be. Possibly. If the shaft 3 can also be swirled, a better surface quality is achieved by grinding.
  • the housing 2 can consist of a cylinder tube which can be pressed or spread into the desired flat shape while retaining its surface condition.
  • FIG. 38 results in a smaller load transfer lever than in the embodiment shown in FIG. 37; However, this smaller load transfer lever is well compensated due to the special, drawn shape.
  • the housings 2 are each shown as single-shelled. In both embodiments, but in particular in the embodiment of Figure 37, the housing 2 may be formed in compound construction.
  • An embodiment of such a compound construction of the housing is shown in FIG. 40, according to which the inner shell 66 adapted to the wing shape of the piston 1 is enclosed by a support body 67, which in turn is enveloped by an outer shell 68.
  • the different shells are advantageously made of different materials and are adapted to their respective function.
  • the inner shell 66 may for example consist of a suitable metal and preferably have a hardened, for example nitrided inner surface to form a wear and low-friction track for the piston 10.
  • the support body 67 is advantageously made of a suitable integral material and may be formed in particular of hard foam, aluminum foam or a suitable casting dimensions.
  • the elliptical outer shell 68 which is shown in the drawn embodiment according to FIG. 40 may consist of different materials.
  • An advantageous embodiment may consist in that the outer shell 68 is made of fiber-reinforced plastic, such as a reinforced fiber reinforced material winding material.
  • Support body made of lighter, less impact-resistant material can achieve the highest strength and shape retention with low weight and also cause the benefits mentioned above.
  • the outer shell 68 can also be adapted to the connection geometry of a component to be connected to the housing 2.
  • the outer shell 68 may have at least one flat bearing surface 69.
  • fastening options can be integrated into the housing 2 in a simple manner due to the compound construction.
  • threaded nuts 70 for example, can be placed on the outer shell 68 from the inside and foamed into the housing 2.
  • the inner shell 66 may also be embedded directly in the outer shell 68, as FIG. 42 shows.
  • the outer shell 68 is advantageously designed as an extrusion or extruded profile.
  • the outer shell 68 may be extruded from GRP or pressed from aluminum strand.
  • the outer shell 68 advantageously comprises a plurality of axial cavities 72, wherein in the axial direction a total of a constant cross-section is provided.
  • fastening options for example in the form of threaded nut receptacles 71, can be integrated into the shell.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP06016270A 2006-08-03 2006-08-03 vérin rotatif et méthode pour la fabrication dudit vérin Withdrawn EP1887229A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06016270A EP1887229A1 (fr) 2006-08-03 2006-08-03 vérin rotatif et méthode pour la fabrication dudit vérin

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06016270A EP1887229A1 (fr) 2006-08-03 2006-08-03 vérin rotatif et méthode pour la fabrication dudit vérin

Publications (1)

Publication Number Publication Date
EP1887229A1 true EP1887229A1 (fr) 2008-02-13

Family

ID=37546583

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06016270A Withdrawn EP1887229A1 (fr) 2006-08-03 2006-08-03 vérin rotatif et méthode pour la fabrication dudit vérin

Country Status (1)

Country Link
EP (1) EP1887229A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008030362A1 (de) * 2008-06-26 2009-12-31 Kinshofer Gmbh Hub-/Schwenkmotor
WO2012024779A1 (fr) * 2010-08-25 2012-03-01 Delaney Technologies Inc. Piston à section polygonale
CN108851390A (zh) * 2018-08-23 2018-11-23 法斗时尚（深圳）投资有限责任公司 一种耳钉结构
CN108851390B (zh) * 2018-08-23 2024-06-04 物勒工名(深圳)智造科技有限公司 一种耳钉结构

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1091437B (de) * 1959-04-16 1960-10-20 Ernst Heinkel Flugzeugbau G M Hydraulischer Schwenkantrieb mittels wendelfoermiger Kolbenverzahnung, insbesondere zur Klappenbetaetigung bei Flugzeugen
US2974646A (en) * 1959-11-02 1961-03-14 Carter Controls Inc Rotary actuator
US3183792A (en) * 1963-01-10 1965-05-18 Alton K Allen Free piston oscillator
DE2338745A1 (de) * 1973-07-31 1975-02-13 Hausherr & Soehne Maschf Drehantrieb
FR2407377A1 (fr) * 1977-10-26 1979-05-25 Epitoegepgyarto Vallalat Verin rotatif
CH653750A5 (en) * 1981-12-14 1986-01-15 Wabco Westinghouse Ag Rotary drive with a shaft driven by a piston axially movable in a cylinder
CH658706A5 (en) * 1983-03-25 1986-11-28 Hausherr Hydraulik & Pneumatik Rotary drive from linear servo - has inside wall of cylinder threaded to grip outside of servo piston
EP0266702A1 (fr) * 1986-11-04 1988-05-11 INNOFINANCE Altalános Innovácios Pénzintézet Cylindre d'entrainement rotatif
DE3725558C1 (en) * 1987-08-01 1989-01-19 Hans Holland Gmbh, 6228 Eltville, De Hydraulic or pneumatic actuator - has constant sealing gap between piston and housing
FR2663995A1 (fr) * 1990-06-29 1992-01-03 Ratier Figeac Soc Verin rotatif hydraulique.
EP0496966A1 (fr) * 1991-01-31 1992-08-05 Silvio Carmeli Vérin
WO1996018043A1 (fr) * 1994-12-05 1996-06-13 Scana Skarpenord A/S Dispositif d'actionnement rotatif hydraulique
EP0745544A1 (fr) * 1995-06-02 1996-12-04 FARID INDUSTRIE S.p.A. Dispositif pour vider un récipient à ordures dans la benne d'un véhicule de ramassage d'ordures
DE20008055U1 (de) * 2000-05-05 2000-08-31 Festo Ag & Co Drehantriebsvorrichtung
DE20107206U1 (de) * 2001-04-02 2002-08-08 Kinshofer Greiftechnik Antriebsvorrichtung für eine Greifeinrichtung

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1091437B (de) * 1959-04-16 1960-10-20 Ernst Heinkel Flugzeugbau G M Hydraulischer Schwenkantrieb mittels wendelfoermiger Kolbenverzahnung, insbesondere zur Klappenbetaetigung bei Flugzeugen
US2974646A (en) * 1959-11-02 1961-03-14 Carter Controls Inc Rotary actuator
US3183792A (en) * 1963-01-10 1965-05-18 Alton K Allen Free piston oscillator
DE2338745A1 (de) * 1973-07-31 1975-02-13 Hausherr & Soehne Maschf Drehantrieb
FR2407377A1 (fr) * 1977-10-26 1979-05-25 Epitoegepgyarto Vallalat Verin rotatif
CH653750A5 (en) * 1981-12-14 1986-01-15 Wabco Westinghouse Ag Rotary drive with a shaft driven by a piston axially movable in a cylinder
CH658706A5 (en) * 1983-03-25 1986-11-28 Hausherr Hydraulik & Pneumatik Rotary drive from linear servo - has inside wall of cylinder threaded to grip outside of servo piston
EP0266702A1 (fr) * 1986-11-04 1988-05-11 INNOFINANCE Altalános Innovácios Pénzintézet Cylindre d'entrainement rotatif
DE3725558C1 (en) * 1987-08-01 1989-01-19 Hans Holland Gmbh, 6228 Eltville, De Hydraulic or pneumatic actuator - has constant sealing gap between piston and housing
FR2663995A1 (fr) * 1990-06-29 1992-01-03 Ratier Figeac Soc Verin rotatif hydraulique.
EP0496966A1 (fr) * 1991-01-31 1992-08-05 Silvio Carmeli Vérin
WO1996018043A1 (fr) * 1994-12-05 1996-06-13 Scana Skarpenord A/S Dispositif d'actionnement rotatif hydraulique
EP0745544A1 (fr) * 1995-06-02 1996-12-04 FARID INDUSTRIE S.p.A. Dispositif pour vider un récipient à ordures dans la benne d'un véhicule de ramassage d'ordures
DE20008055U1 (de) * 2000-05-05 2000-08-31 Festo Ag & Co Drehantriebsvorrichtung
DE20107206U1 (de) * 2001-04-02 2002-08-08 Kinshofer Greiftechnik Antriebsvorrichtung für eine Greifeinrichtung

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008030362A1 (de) * 2008-06-26 2009-12-31 Kinshofer Gmbh Hub-/Schwenkmotor
WO2012024779A1 (fr) * 2010-08-25 2012-03-01 Delaney Technologies Inc. Piston à section polygonale
CN108851390A (zh) * 2018-08-23 2018-11-23 法斗时尚（深圳）投资有限责任公司 一种耳钉结构
CN108851390B (zh) * 2018-08-23 2024-06-04 物勒工名(深圳)智造科技有限公司 一种耳钉结构

Similar Documents

Publication Publication Date Title
EP2464895B1 (fr) Procédé de production de l'écrou fileté d'une vis à billes
EP1991792B1 (fr) Moteur-couple
DE19909347A1 (de) Getriebe
DE2720130B2 (de) Meißeldirektantrieb für Tiefbohrwerkzeuge
EP0328007B1 (fr) Arbre de transmission assemblé
EP1723316B1 (fr) Arbre a cames et procede pour produire un arbre a cames
EP3751174A1 (fr) Mécanisme de réglage
EP1576290B1 (fr) Machine a roues dentees comprenant des plaques laterales axiales
EP3208164A1 (fr) Vis d'entrainement a bille
EP1247005B1 (fr) Arbre se presentant sous forme de piece mecanique avec des conduites integrees
EP1887229A1 (fr) vérin rotatif et méthode pour la fabrication dudit vérin
EP1836403A1 (fr) Profilage d'extremites pour des elements complementaires de courses de paliers lisses permettant de reduire la pression superficielle
DE102006057874B4 (de) Hohlrolle eines Zylinderrollenlagers, Verfahren zur Herstellung einer solchen Hohlrolle
WO2004025142A1 (fr) Transmission a variation continue pourvue de poulies coniques
DE19913889B4 (de) Hubkolbenmaschine
DE102016204982A1 (de) Fahrzeuggetriebe
EP0846861A1 (fr) Pompe annulaire à engrenages continuellement variable
DE2437688B2 (de) Axialstellvorrichtung für eine parallel- und innenachsige Rotationskolbenmaschine
EP1826405A1 (fr) Compresseur à plateau en biais
DE102005033452A1 (de) Drehmotor sowie Verfahren zu seiner Herstellung
DE102006035082A1 (de) Verfahren und Vorrichtung zur Herstellung einer Welle-Nabe-Verbindung
DE19624083A1 (de) Getriebe
DE4224075A1 (de) Hydraulisches Antriebs- und Bremssystem
DE10322501A1 (de) Drehkolbenpumpe
EP2464853A1 (fr) Pompe haute pression

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20071019

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20080627