EP3792404B1 - Dispositif de vissage et de battage - Google Patents

Dispositif de vissage et de battage Download PDF

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Publication number
EP3792404B1
EP3792404B1 EP19197103.5A EP19197103A EP3792404B1 EP 3792404 B1 EP3792404 B1 EP 3792404B1 EP 19197103 A EP19197103 A EP 19197103A EP 3792404 B1 EP3792404 B1 EP 3792404B1
Authority
EP
European Patent Office
Prior art keywords
driving device
outer rotor
anchor
grooves
armature
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.)
Active
Application number
EP19197103.5A
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German (de)
English (en)
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EP3792404A1 (fr
Inventor
Günther THURNER
Martin Thurner
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.)
Krinner Innovation GmbH
Original Assignee
Krinner Innovation 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 Krinner Innovation GmbH filed Critical Krinner Innovation GmbH
Priority to EP19197103.5A priority Critical patent/EP3792404B1/fr
Priority to DK19197103.5T priority patent/DK3792404T3/da
Priority to ES19197103T priority patent/ES2936520T3/es
Publication of EP3792404A1 publication Critical patent/EP3792404A1/fr
Application granted granted Critical
Publication of EP3792404B1 publication Critical patent/EP3792404B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
    • E02D7/22—Placing by screwing down
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • B25D11/102—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool
    • B25D11/104—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool with rollers or balls as cam surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit

Definitions

  • the invention relates to a screwing device, in particular a screw foundation screwing device.
  • WO 2015 128 048 A1 discloses a device for installing ground screws in the ground.
  • the device comprises a rotary device for screwing in the screw foundation and an impact device for generating an impact force in the direction of insertion of the screw foundation.
  • the drive shaft has vanes with pairs of contact surfaces, via which pairs of contact surfaces the torque of the motor is transmitted to the drive shaft.
  • the contact surface pairs are designed in such a way that they allow a relative movement between the hollow shaft and the drive shaft in the direction of the insertion direction during impact.
  • the contact surface pairs are arranged on a diameter that is significantly larger than the diameter of the two shafts, ie the motor shaft and the drive shaft. If the mechanical load on the pairs of friction surfaces is to be reduced, it is proposed to increase the diameter on which the pairs of contact surfaces are arranged, in particular to five times the diameter of the drive shaft.
  • a disadvantage of such a torque transmission is that friction occurs between the pairs of contact surfaces, particularly when the impact is applied in the longitudinal direction and the torque is applied simultaneously in the circumferential direction, and this friction destroys the surface of the pairs of contact surfaces over time.
  • the screwing device according to the invention is in particular a screw foundation screwing device.
  • the screwing-in device comprises an anchor with an axis of rotation for receiving a screwing-in tool. Furthermore, the screwing-in device comprises an outer rotor which is arranged concentrically to the axis of rotation of the armature and can be driven in rotation by a motor.
  • the screwing-in device has an impact device, from which impact energy can be introduced into the anchor.
  • the armature is mounted in the outer rotor by means of rolling elements arranged circumferentially on the armature in such a way that a relative movement between the armature and the outer rotor can be carried out in the direction of the axis of rotation and a torque about the axis of rotation can be applied to the armature by the outer rotor.
  • the torque can be transmitted via the rolling elements.
  • the rolling bodies are preferably arranged in grooves, in particular a large number of grooves, both in the outer rotor and in the armature.
  • a large number of grooves which run parallel to one another can be arranged in the armature.
  • 16 or 24 grooves can be arranged on the circumference of the armature.
  • the grooves are preferably distributed evenly spaced around the circumference.
  • the grooves are made in an outer surface of the armature.
  • Corresponding grooves are arranged in the outer rotor on an inner surface of the outer rotor. The number of slots in the outer rotor and their length, if applicable, correspond to the slots in the armature.
  • One or more rolling elements can be in each of the grooves. If there are several rolling elements, they are separated from one another by intermediate elements, for example roller bearing cages. This minimizes friction.
  • the roller bearing cages are preferably solid, so that they can transmit the impact force, and have a surface corresponding to the roller bearing surface as a raceway. With a large number of rolling elements per groove, i. H. at least two roller bearings per groove, the torque to be transmitted is increased with the same roller bearing size.
  • the rolling elements are designed as spheres.
  • the radius or diameter of the ball is preferably slightly smaller than the radius that defines the surface of the groove.
  • the ball can deflect slightly, i. H. usually not plastically deformed and thus adapts to the surface of the respective groove or the ball track.
  • the rolling bodies are designed as rollers.
  • Rollers have the advantage over balls that a higher torque can be transmitted from the outer rotor to the armature.
  • the rollers are designed in particular as cylindrical rollers.
  • the rollers are set at an angle ⁇ in a plane transverse to the axis of rotation relative to the radial direction. The torque can thus be transmitted via the running surface of the rollers in one direction of rotation. In the opposite direction, the torque is transmitted via the side walls of the rollers, but this is disadvantageous in terms of wear.
  • the rollers are thus set in such a way that they transmit the torque via the running surfaces in the screwing-in direction.
  • the grooves preferably have a longitudinal direction in which the relative movement between the armature and the outer rotor takes place.
  • the relative movement is limited by the length of the grooves, with the corresponding grooves in the armature and the outer rotor preferably having the same length.
  • the rolling elements roll on the surface of the grooves, i.e. on the bearing raceway, over the entire length of the groove when they move from one end position at one end of the groove to the opposite end position at the other end of the groove.
  • the longitudinal direction is preferably arranged parallel to the axis of rotation of the armature or the outer rotor.
  • preferably not only the corresponding grooves, but all grooves in the armature and in the outer rotor have the same length.
  • the path of the relative movement between the armature and the outer rotor is specified and limited by the length of the grooves.
  • the main direction of extension of the groove is inclined by an angle ⁇ .
  • the groove also has a main direction of extension parallel to the axis of rotation; however, the groove also has a component in the circumferential direction.
  • the grooves have a helical configuration.
  • the angle ⁇ preferably has a value in the range of a few degrees, in particular 1, 2 or up to 5 degrees.
  • the angle ⁇ is preferably aligned in such a way that the speed increase takes place when an impact occurs. The rotational speed is thus increased during the impact and decreases during the subsequent recoil or backward movement of the anchor. In this way, the angular velocity of the armature, and thus of the driving tool, pulsates synchronously with the hammer mechanism.
  • the outer rotor is preferably designed in a divided manner.
  • the division preferably takes place in a plane transverse to the axis of rotation and intersects the grooves in the outer rotor.
  • the outer rotor is divided into an outer rotor part and a closing ring.
  • the decisive length of the grooves is preferably worked into the outer rotor part.
  • Preferably only a short area of the grooves is arranged in the longitudinal direction in the closing ring.
  • the closing ring has a circumferential chamfer with a radius, which serves as the end of the groove and thus as a stop for the rolling bodies. The individual grooves are therefore no longer subdivided in the closing ring.
  • the length of the grooves in the end ring is smaller than the radius of the rolling elements.
  • the radius of the circumferential chamfer preferably corresponds to the radius of the rolling body or is greater than the radius of the rolling body surface, ie the rolling surface.
  • the path available for the relative movement between the outer rotor and the armature is limited by the length of the grooves.
  • the rolling body In an end position, the rolling body is clamped between one end of the armature groove and an opposite end of the outer rotor groove.
  • the second end position is defined by the opposite ends of the armature slots or outer rotor slots.
  • the outer rotor part is made of steel, whereas the end ring is made of aluminum.
  • the closing ring is preferably arranged in such a way that it serves as a stop for the balls after the impact has been introduced.
  • the closing ring is thus arranged at the lower end of the outer rotor which faces the ground or the screw-in tool.
  • the screwing-in device preferably has a damping element between an axial shoulder in the armature and an axial shoulder in the outer rotor.
  • the axial shoulder has a shoulder surface which extends in the radial direction, ie the diameter of the armature and the outer rotor increases or decreases.
  • the damping element is arranged between the axial shoulder on the outer diameter of the armature and/or on the inner diameter of the outer rotor. The damping element is thus able to dampen shocks from the armature to the outer rotor.
  • the damping element is preferably arranged on the armature on a side of the bearing facing away from the tool holder.
  • the damping element is thus able to absorb a recoil, which occurs after the impact impulse has been applied to the armature and the screwing tool, in the opposite direction to the impact impulse.
  • the damping element is preferably dimensioned such that it rests on both sides between the axial shoulders before the rolling elements reach their end position, but allows the roller bearings and thus also the armature or the outer rotor to reach their end bearings relative to one another.
  • the damping element is designed as an elastomer, which is arranged as a circular disk on the outer diameter of the armature.
  • the damping element can also be designed as an oil damping element or air damping element.
  • a seal is preferably arranged between the armature and the outer rotor.
  • the armature or the armature shaft preferably has an enlarged diameter in the region of the bearing compared to the adjacent sections of the armature.
  • the outer rotor is preferably designed as a rotationally symmetrical hollow body, in particular as a bowl-shaped hollow body, which is open in the direction of the tool holder.
  • the bowl-shaped area of the outer rotor and the enlarged area of the armature overlap, so that the rolling bodies are arranged between the armature and the outer rotor in the overlapping area.
  • the outer rotor preferably terminates with the bowl-shaped bearing area in the direction of the tool holder.
  • a seal is arranged between the outer rotor and the armature on the side of the bearing facing the workpiece.
  • the seal is preferably designed as a radial seal, in particular as a radial shaft seal or as a labyrinth seal.
  • the seal is preferably arranged in the closing ring of the outer rotor.
  • the driving tool receptacle is preferably designed to receive a screw foundation, so that the screw foundation serves as a drilling tool.
  • the screwing-in tool holder preferably has a core which stabilizes the screw foundation from the inside and receives the screw foundation in a twist-proof manner.
  • the screwing in preferably takes place in series with the introduction of the impact energy or at least temporarily overlapping with the introduction of the impact energy.
  • the impact energy can also be introduced into the screw foundation without interrupting the screwing-in process.
  • the screw foundation usually remains in the ground as a ground anchor. Further details on exemplary insertion methods or screwing-in methods, which can be carried out with a screwing-in device according to the invention, are given in the publication WO 2015 128 048 A1 removable.
  • the driving device can apply a torque and an impact energy to a driving tool.
  • a drilling tool ie an earth auger
  • screwing in a screw foundation for example, the ground around the foundation is essentially compacted. Screwing in is essentially a displacement screw.
  • drilling on the other hand, the overburden is transported out of the borehole via a helix.
  • a (percussion) drilling process can also be carried out with the device according to the invention, so that the driving tool is a drilling tool.
  • Both a screw foundation and a conventional drill, in particular a masonry or rock drill can be used as the drilling tool.
  • the screwing-in device is preferably designed in such a way that it can be hung on a carriage.
  • the feed can be exerted on the screwing device in the direction of the axis of rotation, ie in the screwing-in direction, via the carriage.
  • the feed is preferably adjustable, in particular adjustable as a function of the helix height of an outer helix of the screw foundation and/or the speed of the armature.
  • the armature and the outer rotor are rotatably mounted on the carriage or via a bracket or a housing.
  • the carriage is also slidably mounted in a turning device.
  • the impact device also has a hammer, ie a mass, which is also slidably mounted on the carriage in a screwing device.
  • the motor for rotating the outer rotor is also attached to the carriage. In one embodiment, the motor is designed as an electric motor or as a hydraulic motor.
  • the carriage with the turning device thus forms a turning system.
  • FIG 1 shows a three-dimensional representation of a screwing device 1 according to the invention.
  • An outer rotor 40 is shown in section to better illustrate the device according to the invention, so that a bearing 50 according to the invention is shown.
  • a screwing device 1 according to the invention comprises an impact device, which is shown here as a hammer 10 . Impact energy can be introduced into an armature 30 via the hammer 10 . The hammer 10 strikes a head 31 of the armature 30.
  • the armature 30 is designed as a shaft with different diameters.
  • the armature is shown here as a one-piece component, a multi-part design also being covered by the teaching according to the invention.
  • the outer rotor 40 is arranged concentrically to the armature 30 . The outer rotor 40 can be driven in rotation by a motor 20 during operation.
  • the screwing-in device 1 has a longitudinal axis 2 which also serves as an axis of rotation or rotation for the armature 30 and the outer rot
  • the motor 20 has an output shaft 21 on which a spur gear 22 is arranged.
  • a drive wheel 41 of the outer rotor 40 can be driven by the spur gear 22 .
  • the outer rotor 40 is drum-shaped. In the area of the drive wheel 41, it has a larger diameter, which merges into an adjoining smaller outside diameter with the same inside diameter.
  • a key-shaped area follows at the bottom in the figure, in which both the inner and the outer diameter are enlarged. This creates space for the bearing 50 via which bearing the armature 40 is mounted in the outer rotor 50 .
  • the outer rotor 40 also has a closing ring 42 at the end, which is designed as a separate component and is screwed to the rotor component 45 .
  • the armature has an area of enlarged outer diameter referred to as the plate 32 .
  • the bearing 50 is arranged in the area of the plate 32 .
  • the plate 32 has armature grooves 54 arranged on the outer circumference.
  • the armature slots 54 are evenly spaced around the circumference of the armature 30 .
  • the armature grooves 54 extend in the longitudinal direction of the armature 30 and parallel to the longitudinal axis 2 or the axis of rotation. They have an essentially part-circular cross-section and are also rounded off at their ends.
  • a ball 52 is arranged as a rolling body 51 in each armature slot 54 .
  • a corresponding number of rotor slots 55 are arranged in the outer rotor 40 .
  • the rotor grooves 55 extend in the longitudinal direction of the rotor 40 and are arranged at equal intervals on an inner surface of the outer rotor 40 in the bowl-shaped area.
  • the armature grooves 54 and the rotor grooves 55 serve as a running surface for the balls 52.
  • a ball 52 is arranged in each pair of grooves consisting of an armature groove 54 and a rotor groove 55.
  • the armature slots 54 and the rotor slots 55 typically have the same length. As a result, the relative movement in the direction of the longitudinal axis 2 between the armature 30 and the outer rotor 40 is limited.
  • the outer rotor 41 has the closing ring 42 on its lower end or the end facing the tool holder 33 .
  • the rotor grooves 55 extend from the rotor component 45 into the closing ring 42.
  • the bearing running surfaces on the rotor side therefore also extend over the rotor component 45 and the closing ring 42.
  • the grooves in the closure ring 42 have no lateral delimitation. Rather, the end ring has a bevel with a radius that delimits the rotor slots 55 in the longitudinal direction and serves as a stop for the balls 52 .
  • Such a training can be produced in a simple manner. However, it must be ensured that the closing ring 32 and the phase 43 are dimensioned in such a way that the individual balls cannot leave the corresponding rotor groove 55 when the bearing 50 is in the mounted state.
  • Torques in both directions of rotation can be transmitted from the rotor 20 via the outer rotor 40 to the armature 30 via the bearing 50 described above.
  • the anchor 30 has a receptacle 33 for a drilling tool.
  • a ground screw 60 is shown here in section and in sections as a drilling tool.
  • the receptacle 33 is arranged on the end of the armature 30 opposite the armature head 31 .
  • the bearing 50 allows impact energy to be introduced from the hammer 10 into the anchor 30 and thus via the receptacle 33 into the screw foundation 60.
  • the bearing 50 limits the impact path. If impact energy is introduced into the screw foundation 60, the energy is fed back in the opposite direction, depending on the nature of the ground.
  • the ground screw 60 practically bounces off hard floors and it results in kickback.
  • an elastic damping element 57 is arranged in the turning device 1 .
  • the damping element 57 is designed as an elastomer and is arranged concentrically to the longitudinal axis 2 between the plate 32 and a shoulder in the rotor component 45 on a side facing the impact device 10 or the side facing away from the tool holder 33 .
  • a radial seal 56 is arranged on the closing ring 42 .
  • the radial seal 56 seals against the plate 32 of the armature 30 so that the ingress of dust into the bearing 50 is prevented.
  • figure 3 shows a section along the plane AA figure 2 .
  • the 16 bearing balls 52 in the bearing 50 are arranged uniformly on the outer circumference of the armature 30 and on the inner circumference of the outer rotor 40 .
  • the balls 52 are located in corresponding armature slots 54 and rotor slots 55, which serve as raceways.
  • FIG 4 is supplementary to the representation in figure 2 ,
  • the hammer 10 is mounted so that it can be displaced in the direction of the longitudinal axis 2 , so that a linear guide 11 is involved here.
  • the hammer 10 is optionally secured against rotation.
  • the anchor 30 is mounted in an anchor bearing 34 in the area of the anchor head 31 .
  • the armature bearing 34 allows both a rotational movement of the armature 30 about the longitudinal axis 2 and a translational movement in the direction of the longitudinal axis 2. This is a plain bearing bush, for example.
  • the outer rotor 40 is additionally mounted via a rotor bearing 44 . Both the linear guide 11 and the armature bearing 34 and the rotor bearing 44 are arranged in a housing, not shown.
  • the rotor bearing 44 is designed as a radial bearing or rotary bearing.
  • a defined bearing is provided during operation. In operation, the bearing is 50, as in figure 4 shown outside of impact insertion due to the resistance caused by the ground when screwing in the screw foundation in an end position.
  • the balls 52 are located on stops at the respective groove ends.
  • figure 5 shows a detail from the bearing 50.
  • the armature 30 and the outer rotor 40 are cut in the plane AA.
  • a radius r 2 , r 2 ′ of the surface of the slots 54, 55 is greater than a radius r 1 of the balls 52.
  • the radius r 2 of the surface of the rotor slot 55 corresponds to the radius r 2 ′ of the armature slot 54 in the embodiment shown in FIG
  • the ends of the grooves in the longitudinal direction also have the radius r 2 or r 2' . The same applies to the radius of the circumferential phase 43 of the closing ring 42, which is shown in 7 is shown.
  • the balls 52 Under load, ie when torque and impact energy are transmitted, the balls 52 are deformed so that the radius r1 in the area of the contact surface adapts to the surfaces with the radii r 2 or r 2 ′ , ie the radius r 1 increases in these areas. Due to the deformation of the balls 52 and the adaptation to the radius of the raceways in the grooves 54, 55, a surface pressure, the so-called Hertzian surface pressure, occurs on the resulting contact surfaces. Due to the deformation of the balls 52, a finite surface pressure occurs, which is therefore lower than a theoretical value for point contact without deformation.
  • FIG. 7 A detail drawing with a section in the radial direction is in figure 7 shown. From the figure 7 the ball 52 is shown in an end stop. Thus, the armature 30 and the outer rotor 40 are also in an end position in the longitudinal direction relative to one another. The sphere is shown in an unloaded state since the radius r 1 has not adjusted to the radii r 2 or r 2' . As in figure 7 shown, they are of the same length, so the balls at the transfer from a first end stop to the opposite second end stop can be moved in both raceways in a rolling movement and no slippage occurs. As in figure 7 shown, the bearing 50 is designed essentially without play in the radial direction to the longitudinal direction 2 .
  • FIG 8 an arrangement of two balls 52 which form the rolling element 51 is shown.
  • the balls 52 are spaced apart from each other by a cage 58 .
  • the cage 58 has recesses with a spherical surface at opposite ends.
  • the radius of the spherical surface r 3 corresponds to the radius r 1 of the balls 52.
  • the cage is made of a resistant material, in particular metal, in order to be able to transmit the impact energy without damage, in particular to the spherical surface, and without plastic deformation.
  • FIG 6 shows an alternative embodiment in which the rolling elements 51 are designed as rollers 53.
  • the rollers 53 are cylindrical.
  • the rollers 53 are pivoted by the angle ⁇ with respect to the radial direction.
  • the grooves 54, 55 have, as in figure 6 shown has a triangular cross-section.
  • the rollers 53 have a radius r 4 .
  • the ends of the grooves 54, 55 which form the stop for the relative movement of the armature 30 and the rotor 40 to one another, have a radius r 5 (not shown) which is larger than the radius r 4 .
  • the training is analogous to the training of the balls 52 in figure 7 .
  • the arrow direction in 6 represents the screwing-in direction.
  • the torque is transmitted via the side walls of the rollers 53, so that static or sliding friction occurs here.
  • a lower torque can be transmitted without damaging the surface of the grooves 54, 55 and the rollers 53.
  • Rollers 53 thus have the advantage that the torque that can be transmitted is greater in one direction than with balls, but the torque that can be transmitted is dependent on the direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Dental Preparations (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Rolling Contact Bearings (AREA)

Claims (15)

  1. Dispositif de vissage (1), en particulier dispositif de vissage pour fondation vissée, présentant un boulon d'ancrage (30), doté d'un axe de rotation, pour recevoir un outil de vissage, un rotor extérieur (40) qui est disposé de manière concentrique à l'axe de rotation du boulon d'ancrage (30) et peut être entraîné en rotation par un moteur (20), un dispositif de battage (10) qui permet d'appliquer de l'énergie de battage au boulon d'ancrage (30),
    caractérisé en ce que le boulon d'ancrage (30) est logé dans le rotor extérieur (40) au moyen d'éléments roulants (51) disposés en circonférence au niveau du boulon d'ancrage (30) de telle sorte qu'un mouvement relatif peut être effectué entre le boulon d'ancrage (30) et le rotor extérieur (40) en direction de l'axe de rotation, et un couple autour de l'axe de rotation peut être appliqué par le rotor extérieur (40) au boulon d'ancrage (30) par l'intermédiaire des éléments roulants (51).
  2. Dispositif de vissage (1) selon la revendication 1, caractérisé en ce que les éléments roulants (51) sont disposés dans une pluralité de rainures (54, 55) à la fois dans le rotor extérieur (40) et dans le boulon d'ancrage (30).
  3. Dispositif de vissage (1) selon la revendication 2, caractérisé en ce que dans chacune des rainures (54, 55), au moins deux éléments roulants (51) sont disposés qui sont séparés l'un de l'autre par une cage de palier à roulement (58).
  4. Dispositif de vissage (1) selon la revendication 2 ou 3, caractérisé en ce que les rainures (54, 55) s'étendent dans une direction longitudinale en parallèle à l'axe de rotation.
  5. Dispositif de vissage (1) selon l'une quelconque des revendications 2 à 4, caractérisé en ce que les rainures (54, 55) sont disposées en oblique, et une première composante directionnelle s'étend dans la direction longitudinale en parallèle à l'axe de rotation et une deuxième composante directionnelle s'étend dans la direction circonférentielle.
  6. Dispositif de vissage (1) selon l'une quelconque des revendications 2 à 5, caractérisé en ce que les rainures (54, 55) dans le rotor extérieur (40) sont limitées par un anneau obturateur (42) à une extrémité tournée vers l'outil de vissage.
  7. Dispositif de vissage (1) selon la revendication 6, caractérisé en ce que l'anneau obturateur (42) présente un chanfrein périphérique (43) ayant une forme de section transversale ronde dont le rayon correspond approximativement au rayon de l'élément roulant (51).
  8. Dispositif de vissage (1) selon l'une quelconque des revendications 2 à 7, caractérisé en ce que la course disponible pour le mouvement relatif est limitée par la longueur des rainures (54, 55).
  9. Dispositif de vissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que les éléments roulants (51) sont réalisés sous forme de billes (52).
  10. Dispositif de vissage (1) selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les éléments roulants (51) sont réalisés sous forme de rouleaux (53).
  11. Dispositif de vissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un élément amortisseur (57) est disposé entre un épaulement axial dans le boulon d'ancrage (30) et un épaulement axial dans le rotor extérieur (40).
  12. Dispositif de vissage (1) selon la revendication 11, caractérisé en ce que l'élément amortisseur (57) est un élastomère, un amortisseur à huile ou un amortisseur à air.
  13. Dispositif de vissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un joint d'étanchéité (56) est disposé entre le boulon d'ancrage et le rotor extérieur.
  14. Dispositif de vissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le boulon d'ancrage (30) présente comme outil de vissage un logement d'outil de vissage pour une fondation vissée (60).
  15. Dispositif de vissage (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de vissage (1) peut être accroché à un affût.
EP19197103.5A 2019-09-12 2019-09-12 Dispositif de vissage et de battage Active EP3792404B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP19197103.5A EP3792404B1 (fr) 2019-09-12 2019-09-12 Dispositif de vissage et de battage
DK19197103.5T DK3792404T3 (da) 2019-09-12 2019-09-12 Indskruningsindretning med slagvirkning
ES19197103T ES2936520T3 (es) 2019-09-12 2019-09-12 Dispositivo de atornillado con efecto de impacto

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19197103.5A EP3792404B1 (fr) 2019-09-12 2019-09-12 Dispositif de vissage et de battage

Publications (2)

Publication Number Publication Date
EP3792404A1 EP3792404A1 (fr) 2021-03-17
EP3792404B1 true EP3792404B1 (fr) 2022-11-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19197103.5A Active EP3792404B1 (fr) 2019-09-12 2019-09-12 Dispositif de vissage et de battage

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EP (1) EP3792404B1 (fr)
DK (1) DK3792404T3 (fr)
ES (1) ES2936520T3 (fr)

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DE2144449A1 (de) * 1971-09-04 1973-03-08 Impex Essen Vertrieb Hammerbohrmaschine
DE102014002986B3 (de) 2014-02-28 2015-03-12 Krinner Innovation Gmbh Verfahren und Vorrichtung zum Einbringen von Schraubfundamenten ins Erdreich
BR112017021369A2 (pt) * 2015-04-08 2019-09-24 Primo Rombaldi Albert adaptador para a cravação rápida e econômica de estacas de concreto armado

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ES2936520T3 (es) 2023-03-17
DK3792404T3 (da) 2023-02-20
EP3792404A1 (fr) 2021-03-17

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