WO1999024730A1 - Mecanisme de rotation dote d'une securite anti-surcharge - Google Patents

Mecanisme de rotation dote d'une securite anti-surcharge Download PDF

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Publication number
WO1999024730A1
WO1999024730A1 PCT/EP1998/001823 EP9801823W WO9924730A1 WO 1999024730 A1 WO1999024730 A1 WO 1999024730A1 EP 9801823 W EP9801823 W EP 9801823W WO 9924730 A1 WO9924730 A1 WO 9924730A1
Authority
WO
WIPO (PCT)
Prior art keywords
arrangement according
elements
gear
locking
drive
Prior art date
Application number
PCT/EP1998/001823
Other languages
German (de)
English (en)
Inventor
Erich Russ
Original Assignee
Imo Industrie-Antriebseinheit Stoll & Russ 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 Imo Industrie-Antriebseinheit Stoll & Russ Gmbh filed Critical Imo Industrie-Antriebseinheit Stoll & Russ Gmbh
Priority to AU72119/98A priority Critical patent/AU7211998A/en
Publication of WO1999024730A1 publication Critical patent/WO1999024730A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/84—Slewing gear
    • B66C23/86—Slewing gear hydraulically actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock

Definitions

  • the invention is directed to an arrangement protected against overload for the rotatable coupling of two concentric connection elements, comprising a rotary bearing between the connection elements for receiving axial and radial loads and tilting moments and a drive coupled to both connection elements for their relative rotation, and one or more, the drive upstream and / or downstream transmission elements.
  • a generic rotary drive is to be developed in such a way that, in addition to the axial and radial loads and tilting moments, torque overloads from the drive acting on the load side, which are harmful to the rotary drive, and in particular be kept away from an intermediate transmission.
  • the invention provides an element arranged between the drive or transmission on the one hand and a connection element on the other hand, which, in the event of a torque overload, cancels the rotational connection between the drive or transmission on the one hand and the relevant connection element on the other.
  • connection elements are designed as concentric rings or disks with fastening means arranged in a ring, in particular bores. Since the tangential force required for the transmission of a constant torque decreases with the distance to the axis of rotation, a large diameter of the connecting elements and a large distance of the ring-shaped fastening means from the relevant axis of rotation contribute to the reduction of the tangential forces and thus to Material relief at. In addition, a large number of fastening means can be provided at a relatively large distance from the axis of rotation.
  • the construction according to the invention undergoes an advantageous further development in that the radius of the rotary bearing corresponds approximately to the radius of the connecting elements.
  • the rotary bearing is designed with one or more four-point and / or angular contact bearings with a maximum number of rolling elements corresponding to the circumference of the rotary bearing. This measure also contributes to absorbing loads resulting from external tilting moments and thereby keeping them away from the gear unit.
  • the drive of the rotary arrangement according to the invention can be designed as a hydraulic-mechanical or as an electrical-mechanical energy converter. While the former embodiment has proven itself in particular on vehicles and mobile devices such as the concrete demolition grapple mentioned at the beginning, the latter arrangement makes it possible to draw the required energy from the power supply network in the case of stationary machines.
  • an element preventing energy surges in particular a shock valve
  • a shock valve can be arranged between the drive energy converter and its energy source.
  • unforeseen torque surges can also result from sudden fluctuations in the hydraulic pressure, as can be caused by the sudden standstill of other machine units operated in parallel.
  • Such a shock valve can be combined with a pressure reducing valve to adapt to a higher operating pressure.
  • the invention further provides that the transmission also has an annular element with teeth.
  • the ring gear preferably forms the interface to the drive unit, which for this purpose can be provided with one or more pinions and / or screws, which serve the intermeshing rotation with the ring gear.
  • the overload protection comprises two rotating parts, each with one of two adjacent or slightly spaced rotating surfaces, each having one or more correspondingly arranged depressions distributed along its circumference, with one pair of wells each approximately perpendicular Slidable locking element is provided to the relevant rotational surfaces, which is pressed into a locking position by a spring element.
  • the overload protection according to the invention uses a positive locking instead of a frictional connection for the rigid coupling of the two axes in the lower torque range, which is released from each other only by completely pushing back all locking elements in one of the two rotating parts. This requires overcoming the spring forces, which is caused by an increasing torque. If such a lock is then released, the two parts of the overload safety device can be rotated against one another almost frictionlessly, in contrast to a conventional slip clutch, so that the overload safety device does not heat up and its properties are not changed even with frequent switching.
  • the switching threshold can therefore be set fairly precisely to a desired value and then remains constant even with frequent switching and ideally over the entire service life of the arrangement in question, so that an exact calculation variable is available for the plant construction and dimensioning.
  • the locking element on its opposite side of the compression spring in the circumferential direction of the Overload protection has convexly curved and / or bevelled surface. This is a structurally inexpensive measure to let the torque to be transmitted work against the forces of the spring elements provided on the locking elements. Because on such a convexly curved or beveled surface a radial component can be split off from the driving force acting in the tangential direction for torque transmission, which counteracts the spring pressure. On the other hand, the deflection of the spring and thus the locking element according to Hooke's law is linked to the force acting on the spring.
  • the threshold value for the disengagement into the freewheel can be specified precisely and permanently by the choice of the spring constant and / or by the geometry of the convexly curved or beveled surface.
  • the front of the locking element is approximately dome-shaped and / or is formed by a rolling element. This geometry of the locking element ensures that it is gently lifted out of the relevant depression of the opposite rotating part.
  • the recess opposite the spring element has approximately the shape of a concave or conical depression.
  • the locking balls and the depressions partially receiving them in an axial plane have approximately identical radii of curvature, the locking balls can simultaneously be transferred to the axial guidance of one of the two gear elements.
  • the radius of curvature of the concave depression in the circumferential direction of the rotation surface in question is approximately two to ten times, preferably approximately four to five times as large as the radius of curvature of one Ball element, so a slight resilience can be realized, which means that a slight relative rotation is possible at higher torques, but below the triggering threshold, but without completely canceling the rotation.
  • the invention further provides that the surface of revolution (s) run along surfaces which are conical or cylindrical-shaped or face-end. While a maximally flat design of the coupling can be produced by arranging the depressions and locking elements in approximately cylindrical jacket-shaped surfaces by the respective rotating parts being joined together in a ring, an arrangement in which the relevant rotating surfaces are designed as disks arranged along the axis of rotation can be designed , achieve a complete decoupling of the tangential force required for the switchover to the freewheel to overcome the spring forces or the associated torque from centrifugal forces caused by the speed.
  • the spring element is preferably formed from one or more disc springs.
  • Disc springs of this type are very flat components which have a very stiff spring characteristic, i.e. very high spring forces can be generated even with the slightest deflections, in particular compressions. This fact is of great importance for the construction according to the invention, where the locking element only has to be deflected by a few millimeters or even fractions thereof in order to be lifted out of the depression in the opposite rotational surface.
  • the socket is preferably screwed into an internal thread of the recess. Since the bushing preferably also has a rear contact surface which absorbs the counterpressure of the spring element, the length of the spring element and thus its compressive force can be adjusted by such a screw adjustment. For this purpose, the rear side of the bushing can have a profile for attaching a turning tool.
  • the invention is preferably characterized by a lubricating nipple inserted from the accessible side, in particular through or in the counter element.
  • a lubricating nipple inserted from the accessible side, in particular through or in the counter element.
  • Such grease nipples are used to lubricate the locking elements so that they can run along the opposite rotational surface almost without friction.
  • the spring element should have a concentric recess, which can be realized, for example, by approximately ring-shaped disc springs.
  • This embodiment allows a further development in that rotationally symmetrical, in particular spherical, locking elements can roll in the released, free-running state on the opposite surface of rotation.
  • the invention provides a groove-like running surface for the rolling elements in the rotational surface which is opposite the recesses receiving the springs.
  • a tread can For example, have an arcuate cross section, the depth of which is, however, less than the depth of the depressions receiving the balls. It mainly serves to guide the balls in their raised position exactly to the next depression, so that if the torque is reduced in the meantime, the balls snap back into them and the overload protection device can transmit the now reduced torque again.
  • the transition from the groove to a depression can be smooth or fluid.
  • a rotary part of the overload protection device preferably that which receives the compression springs
  • a connecting part to be screwed to a system part. Since this part has to perform an additional support function as a connecting element, it must on the one hand be made particularly stable and on the other hand it must also be stably supported. Due to the resulting construction volume, this part is preferably suitable for receiving the compression springs.
  • a radially inner or outer surface of the other rotational part of the overload protection is formed with a ring gear as part of the gear element.
  • FIG. 1 shows a cross-section to the drive and output axis through the mutually rotatable parts of the overload protection of a rotary drive according to the invention
  • FIG. 2 shows an enlarged illustration of detail II from FIG. 1;
  • FIG. 3 shows a section through FIG. 1 along the line III-III, the drive unit also being shown;
  • Fig. 4 is a representation corresponding to Figure 3 another
  • FIG. 5 shows a representation corresponding to FIG. 3 of a further modified embodiment of the invention.
  • FIG. 6 shows a worm gear embodiment in a representation similar to FIG. 4.
  • the inner ring 2 has an approximately rectangular cross section, on the inside of which a toothing 5 is provided as part of the gear element. This is used for meshing engagement with a pinion 6, which is driven by a hydraulic motor 7.
  • the outer circumference of the inner ring 2 serves as a first rotational surface 8 of the overload protection 1, which corresponds to a second, inner rotational surface 9 of the outer ring 3.
  • the raceway 13 has an approximately circular cross-section, as shown in FIG. 3. At equidistant intervals, which correspond to the distances between the balls 11 in the outer ring 3, are in the region of the groove 13 Additional depressions 14 are provided, into each of which a ball 11 is pressed under the influence of a spring element 15 arranged radially outside the respective ball 11.
  • each and one spring element 15 are integrated within a bush 16 to form a structural unit which is inserted into a radial recess 17 in the outer ring 3.
  • Each radial recess 17 has a circular cross section and passes through the outer ring 3 from its inner rotating surface 9 to its peripheral boundary surface 18 and is provided with a chamfer 19 at the mouth there.
  • the recess 17 has an internal thread into which the bush 16 can be screwed thanks to a complementary external thread.
  • the bushing 16 has an approximately cup-shaped shape, with an approximately constant, circular inner cross section, the diameter of which corresponds approximately to the diameter of the ball 11.
  • a stack of stacked disc springs 20, the diameter of which approximately corresponds to the inner cross section of the bushing 16, serves as the spring element 15.
  • Disc springs have the great advantage that they can exert high compressive forces even with the slightest deformation.
  • the plate springs 20 have an annular shape, so that there is an approximately circular contact surface for the ball 11.
  • an external thread counter element 21 which, like before, the socket 16 after the assembly of the two rings 2, 3 is screwed into the recess 17 from the outer peripheral surface 18 and then the socket in the desired position.
  • the counter element 21 has approximately the shape of a pot, but it is screwed into the recess 17, in contrast to the socket 16 with its bottom first, so that in the finished state the two bottoms of the socket 16 and the counter element 21 abut one another plane-parallel.
  • In the peripheral periphery of the counter element 21 there are depressions 22 for the attachment of a turning tool.
  • the bottoms of both the socket 16 and the counter element 21 are provided with a coaxial recess, of which the recess in the counter element 21 has an internal thread.
  • a lubricating nipple 23 is screwed into this internal thread until its front surface sealingly abuts a shoulder in the bottom recess of the socket 16. From this grease nipple, grease is pressed through the hole in the bottom of the bushing 16 and through the recesses in the disc springs 20 to the ball 11, which can roll almost frictionlessly within the groove 13 and the bushing 16 due to this lubrication. This virtually eliminates wear of the ball 11 during the freewheeling phase.
  • Figure 3 can be seen that the outer ring 3 to the axis of rotation 4 parallel, preferably threaded holes for inserting or screwing in fastening screws, which creates a connection to the ring 3 for rotatable system parts. So that such system parts are also borne by the ring 3 and the axial and radial forces and tilting moments that occur are kept away from the gear 5, 6, the ring 3 is additionally rotatably mounted on an annular flange 25, which is the second connecting element.
  • the bearing function is taken over by spherical rolling elements 26 which, according to the principle of a ball bearing, ensure that the ring-shaped first connecting element 3 can rotate relative to the second connecting element of the rotary drive 25, and on the other hand provide sufficient resistance to radial, axial or tilting forces.
  • the ring flange 25 can - if necessary within a housing - be fixed by means of screws on a chassis or system part, which can be screwed into the threaded recesses 27 provided therefor.
  • the inner area of the rotary drive is closed off by a circumferential cylinder jacket 28 and an annular disk 29 covering the ring gear 5 and the pinion 6, on the one hand, and a circular or annular disk 30 arranged below the pinion 6, on the other hand, and thereby protected from environmental influences.
  • the penetration of dust into the sensitive inner area of the overload protection device is prevented by the elastic sealing lips 31, 32 covering the air gap between the two rotation surfaces 8, 9 and the roller bearing area 26.
  • the embodiment 42 according to FIG. 4 differs from the one described above primarily in that here the ring 41 of the rotary drive 42 provided with the ring gear 40 has a larger diameter than the complementary ring 43 and is arranged outside the same.
  • the pinion 44 which is driven by a motor 62, is located outside the two rings 41, 43.
  • the annular connecting element 43 differs from the ring 3 of the first embodiment primarily in that the balls 45 are now radially outside the spring elements 46 are arranged.
  • the other elements of the rotary arrangement (42) such as balls 48 guided on the second connecting element 47 for absorbing axial and radial forces and tilting moments, the same dust-sealing sealing lips 49 and recesses 50 in the ring 43 for inserting or screwing in fastening screws and threaded holes 51 in the second connecting element 47, which is located within the ring 43, correspond to the arrangement according to FIGS. 1 to 3.
  • a further special feature of this embodiment is that the balls 45 are not inserted into bushings, but rather directly into a threadless bore of the inner ring / connecting element 43.
  • Radially inside the balls 45 are each the stacked disc springs 46, which are supported on a plate 52.
  • the plates 52 are held in position by the front end faces of screws 53 which are screwed into radial threaded bores which are aligned with the longitudinal axis of the recess 54 receiving the ball in question.
  • a plurality of motors 7, 62 can be arranged at equidistant intervals on the circumference of the ring 2 or 41.
  • the guide 11, 45 of the ring 2, 41 provided with a ring gear 5, 40 is relieved in particular by diametrically opposed motors 7, 62 and pinions 6, 44 connected to them.
  • the motors 7, 62 are preferably designed as hydraulic motors with an inlet connection 57 and an outlet connection 58 for the hydraulic oil.
  • each motor 62 is surrounded by the housing of the arrangement.
  • the embodiment 63 of the rotary drive according to the invention according to FIG. 5 represents a development of the first embodiment. It can be seen here that the basic arrangement of the first connection element 64 largely corresponds to the relevant element 3 according to FIG. 3, the ring 2 there finds its counterpart in FIG the ring 65 provided with a ring gear 5, which meshes with a pinion 6 as in the arrangement according to FIG. This is driven by one or more hydraulic motors 7.
  • a first difference of this arrangement compared to the rotary drive according to FIG. 3 is that here the second connection element 66 is arranged radially outside the first connection element 64 and rotatable about the axis 4 via a four-point ball bearing 67, but is otherwise fixed immovably on the latter.
  • the motor housing 68 is fastened to an annular cover 69 of the rotary drive, which is fixed to the outer connecting element 66 by screwing it together.
  • the recesses 71 serving to receive the locking elements 70 cannot be made continuously up to the outside of the connection element 64. Therefore, here in the connecting element 64 in the foot region of the recesses 71 designed as radial threaded blind holes, there is an axial bore 72 parallel to the axis of symmetry 4, into which a bolt 74 is screwed in for the purpose of countering a bushing 73 accommodating the locking element 70 in the recess 71 in question can be.
  • FIG. A construction which in principle differs from the previous embodiments is shown in FIG.
  • the axis of rotation of the arrangement is to be thought relatively far to the right.
  • the outer connection to the outer element 76 being able to be made in the form of ring-shaped threaded blind holes 78 distributed over its circumference and parallel to the axis of rotation, while the relevant ones are attached to the other machine - or chassis part serving threaded holes 79 are also arranged in a ring-shaped distribution on the opposite end face of the inner connecting ring 77.
  • two oblique roller bearings 80, 81 are provided between the two connecting elements 76, 77, offset in the axial direction, the roller axes of which are inclined relative to one another by approximately 90 °.
  • the inner connecting ring 77 is coupled to a further, externally toothed ring 82 which is received in a groove-shaped recess which runs approximately centrally between the two inclined roller bearings 80, 81 and is protected against torque overload with the inner ring 77 to a limited extent by means of a locking element according to the invention connected is.
  • the ring gear 82 is thus able to transmit torques below a torque threshold to the inner ring 77, however, in the event of an overload, the coupling is canceled by the locking elements 83, which are arranged around the circumference and consist of depressions in the ring 82 against the pressure from radially inside of the spherical locking elements 83 arranged disc springs 84 are pressed out and thereby the positive engagement is canceled.
  • the gear ring gear 82 can be operated as a result of the overload protection according to the invention or several tangential Sennecken 85 are driven so that in extension of the worms 85 in question hydraulically driven motors with a comparatively low power can be flanged to the larger connecting element 76, which also serves as the housing. Due to the high reduction ratio of the worm gear 85, 82, relatively large torques can be generated without, on the other hand, high torques acting from outside being able to damage the ring gear 82.
  • the inner connection element 77 has a central recess, so that the bushings 86 are accessible for the purpose of adjusting the pressure force, checking and / or adjusting the lubrication.
  • the bushings 86 are countered by externally placed threaded rings 87 or the like, which are supported against the radially inner surface 88 of the inner connecting element 77.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)

Abstract

Une configuration protégée de toute surcharge (42, 63, 89) et destinée à l'accouplement rotatif de deux éléments de liaison concentriques (3, 25; 43, 47; 64, 66; 76, 77). Cette configuration comprend entre les éléments de liaison un logement de pivotement (26; 48; 67; 80, 81) destiné à la réception des charges axiales et radiales et des couples de basculement. Cette configuration comprend également un mécanisme (7; 62) relié aux deux éléments de liaison et permettant leur mouvement de rotation l'un par rapport à l'autre. De plus, cette configuration comprend éventuellement au moins un élément d'engrenage (5, 6; 40, 44; 82, 85) placé en amont et/ou en aval du mécanisme. Un élément placé (1) entre le mécanisme ou l'engrenage, d'une part, et un élément de liaison, d'autre part, supprime la liaison de rotation entre le mécanisme ou l'engrenage, d'une part, et l'élément de liaison concerné, d'autre part, en cas de surcharge résultant du couple de rotation.
PCT/EP1998/001823 1997-11-06 1998-03-27 Mecanisme de rotation dote d'une securite anti-surcharge WO1999024730A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU72119/98A AU7211998A (en) 1997-11-06 1998-03-27 Rotating drive unit with an overload cut-out

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19748881.1 1997-11-06
DE19748881 1997-11-06
DE19809780 1998-03-06
DE19809780.8 1998-03-06

Publications (1)

Publication Number Publication Date
WO1999024730A1 true WO1999024730A1 (fr) 1999-05-20

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Application Number Title Priority Date Filing Date
PCT/EP1998/001823 WO1999024730A1 (fr) 1997-11-06 1998-03-27 Mecanisme de rotation dote d'une securite anti-surcharge

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WO (1) WO1999024730A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10015093A1 (de) * 2000-03-28 2001-10-11 Imo Ind Antriebseinheit Stoll Vorrichtung zur verdrehbaren Kopplung zweier koaxialer Anschlußelemente
DE102011105819A1 (de) * 2011-05-27 2012-11-29 Liebherr-Werk Nenzing Gmbh Kran mit Überlastsicherung
WO2014166512A1 (fr) * 2013-04-12 2014-10-16 Imo Holding Gmbh Palier à couple, éolienne et véhicule
WO2017053533A3 (fr) * 2015-09-23 2017-06-22 Nexen Group, Inc. Table rotative étanche

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH353226A (de) * 1956-06-27 1961-03-31 Philips Nv Rotierende Rutschkupplung
US3093984A (en) * 1960-12-01 1963-06-18 Rca Corp Coupling mechanism
EP0031873A2 (fr) * 1979-10-09 1981-07-15 Maschinenfabrik Benninger Ag Transmission à moteur et son utilisation
SU901681A1 (ru) * 1979-11-05 1982-01-30 Предприятие П/Я Г-4897 Шарикова предохранительна муфта
SU1032241A1 (ru) * 1982-01-29 1983-07-30 Воронежский лесотехнический институт Предохранительна муфта
DE3500945A1 (de) * 1985-01-14 1986-07-17 Verpackungssysteme AG, Schaffhausen Drehmomentbegrenzende kupplung
EP0631068A1 (fr) 1993-06-19 1994-12-28 IMO - INDUSTRIE-MOMENTENLAGER STOLL & RUSS GmbH Agencement pour l'entraînement en rotation d'un élément d'une machine ou d'une installation avec un engrenage à vis sans fin

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH353226A (de) * 1956-06-27 1961-03-31 Philips Nv Rotierende Rutschkupplung
US3093984A (en) * 1960-12-01 1963-06-18 Rca Corp Coupling mechanism
EP0031873A2 (fr) * 1979-10-09 1981-07-15 Maschinenfabrik Benninger Ag Transmission à moteur et son utilisation
SU901681A1 (ru) * 1979-11-05 1982-01-30 Предприятие П/Я Г-4897 Шарикова предохранительна муфта
SU1032241A1 (ru) * 1982-01-29 1983-07-30 Воронежский лесотехнический институт Предохранительна муфта
DE3500945A1 (de) * 1985-01-14 1986-07-17 Verpackungssysteme AG, Schaffhausen Drehmomentbegrenzende kupplung
EP0631068A1 (fr) 1993-06-19 1994-12-28 IMO - INDUSTRIE-MOMENTENLAGER STOLL & RUSS GmbH Agencement pour l'entraînement en rotation d'un élément d'une machine ou d'une installation avec un engrenage à vis sans fin

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Title
DATABASE WPI Section PQ Week 050, 2 February 1983 Derwent World Patents Index; Class Q63, AN b1275 j, XP002075707 *
DATABASE WPI Section PQ Week 8448, 16 January 1985 Derwent World Patents Index; Class Q63, AN 84-298883, XP002075706 *

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10015093A1 (de) * 2000-03-28 2001-10-11 Imo Ind Antriebseinheit Stoll Vorrichtung zur verdrehbaren Kopplung zweier koaxialer Anschlußelemente
EP1150039A3 (fr) * 2000-03-28 2003-03-12 IMO Antriebseinheit GmbH Dispositif pour un accouplement rotatif de deux raccordements coaxiaux
DE10015093B4 (de) * 2000-03-28 2004-02-26 Imo Industrie-Antriebseinheit Stoll & Russ Gmbh Vorrichtung zur verdrehbaren Kopplung zweier koaxialer Anschlußelemente
DE102011105819A1 (de) * 2011-05-27 2012-11-29 Liebherr-Werk Nenzing Gmbh Kran mit Überlastsicherung
US11192762B2 (en) 2011-05-27 2021-12-07 Liebherr-Werk Nenzing Gmbh Crane with overload safety device
WO2014166512A1 (fr) * 2013-04-12 2014-10-16 Imo Holding Gmbh Palier à couple, éolienne et véhicule
WO2017053533A3 (fr) * 2015-09-23 2017-06-22 Nexen Group, Inc. Table rotative étanche
US10975951B2 (en) 2015-09-23 2021-04-13 Nexen Group, Inc. Sealed rotary table
EP3943782A1 (fr) * 2015-09-23 2022-01-26 Nexen Group, Inc. Table rotative étanche
US11365796B2 (en) 2015-09-23 2022-06-21 Nexen Group, Inc. Sealed rotary table

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