EP0080670A1 - Dispositif de rotation de charges suspendues - Google Patents

Dispositif de rotation de charges suspendues Download PDF

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Publication number
EP0080670A1
EP0080670A1 EP82110702A EP82110702A EP0080670A1 EP 0080670 A1 EP0080670 A1 EP 0080670A1 EP 82110702 A EP82110702 A EP 82110702A EP 82110702 A EP82110702 A EP 82110702A EP 0080670 A1 EP0080670 A1 EP 0080670A1
Authority
EP
European Patent Office
Prior art keywords
stator
rotor
drive mechanism
rotating device
rotary
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.)
Granted
Application number
EP82110702A
Other languages
German (de)
English (en)
Other versions
EP0080670B1 (fr
Inventor
Gunther Neumann
Heinz Thumm
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.)
Heinz Thumm Oelhydraulische Antriebe GmbH
Original Assignee
Heinz Thumm Oelhydraulische Antriebe 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 Heinz Thumm Oelhydraulische Antriebe GmbH filed Critical Heinz Thumm Oelhydraulische Antriebe GmbH
Publication of EP0080670A1 publication Critical patent/EP0080670A1/fr
Application granted granted Critical
Publication of EP0080670B1 publication Critical patent/EP0080670B1/fr
Expired legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3677—Devices to connect tools to arms, booms or the like allowing movement, e.g. rotation or translation, of the tool around or along another axis as the movement implied by the boom or arms, e.g. for tilting buckets
    • E02F3/3681—Rotators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
    • B66C13/08—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack for depositing loads in desired attitudes or positions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C3/00—Load-engaging elements or devices attached to lifting or lowering gear of cranes or adapted for connection therewith and intended primarily for transmitting lifting forces to loose materials; Grabs
    • B66C3/005—Grab supports, e.g. articulations; Oscillation dampers; Orientation
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/40—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets
    • E02F3/413—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets with grabbing device
    • E02F3/4135—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets with grabbing device with grabs mounted directly on a boom

Definitions

  • the invention relates to a rotating device for hanging loads, in particular for excavator or crane grabs or load magnets of the type specified in the preamble of claim 1.
  • two axially stressed bearings are usually used (see, for example, DE-OS 28 38 346).
  • a considerable construction effort and a corresponding space requirement are required.
  • Either two-part or multi-part shafts or additional machine elements such as snap rings, nuts and screws are required.
  • the snap rings which are intended to form part of the bearing shoulders, pose a considerable danger inside a rotating device, because due to the large surface pressures occurring there, it closes Damage or even come off the snap rings.
  • the snap rings also require sharp-edged ring grooves in the shaft, in the area of which there are notch stresses and thus an increased risk of breakage due to the high impact loads that occur with gripper rotating devices.
  • the invention has for its object to provide a rotating device that is particularly simple and resistant and enables a particularly compact design.
  • roller bearing arrangement which can absorb both radial forces and axial and moment loads, and whose running surfaces for the roller bearing bodies are at least partially arranged directly on the stator and / or on the rotor, makes it possible to reduce the number of individual bearings arranged within the motor and thus a reduction in construction volume. Neither the ring shoulders usual for the support of the bearings nor snap rings or similar machine elements are required, which could represent a risk of damage, especially in tough use. Furthermore, for the first time a largely constant shaft diameter over the entire length is also possible beyond the bearing area, so that simpler manufacture and assembly of the turning device is ensured.
  • one of the parts of the tread can Stator or rotots are executed separately from the rest of the part containing the drive mechanism.
  • the drive mechanism and the sealing rings which are exposed to increased wear can thus be exposed relatively easily, for example for repair and maintenance purposes, without the bearing with the rolling bearing bodies having to be removed.
  • the detachable bearing part is preferably designed as a threaded ring or as a plate-shaped flange part.
  • the axial boundary surfaces of the drive elements are designed to be variable over the circumferential area.
  • inlets and outlets for the hydraulic fluid must be provided in these areas.
  • the parts to be connected must be aligned with one another in the circumferential direction.
  • this alignment can be achieved in particular by using an additional intermediate ring which is connected to the part containing the drive mechanism in a rotationally fixed manner, for example with the aid of axial pins.
  • All types of hydraulic and pneumatic drives come into consideration as the drive mechanism, in particular vane drives with and without stop, axial and radial piston drives, and the gerotor, which can all be arranged inside the rotary device between the stator and rotor.
  • the bearing principle according to the invention can also be applied to a drive mechanism with a housing rigidly connected to the stator outside the rotor and a drive pinion engaging in an external ring gear of the rotor.
  • the roller bearing arrangement preferably consists of a four-point bearing with spherical roller bearing bodies. With a corresponding design of the running surfaces, however, a crossed roller bearing with roller-shaped roller bearing bodies can also be provided. Furthermore, a bearing arrangement with two spaced-apart, mutually braced angular contact bearings or axial bearings is possible, the running surfaces of which are at least partially molded directly into the stator and / or rotor material. Even in the case of a rotating device with an external drive mechanism, it is advantageous to achieve a compact design if a four-point bearing with treads at least partially molded into the stator and rotor material is used. However, since the space problems inside the rotating device are not so critical, it is also possible in this case without major disadvantages to use commercially available four-point bearings with separate races.
  • a preferred field of application of the rotating devices according to the invention are gripper rotating devices for excavators, which can be rotated both when the load is hanging and when the gripper is pressed on, for example to produce boreholes.
  • the rotating devices shown in the drawing are intended for excavator grabs where high tensile, compressive and torque loads occur. They essentially consist of a stator 1 which can be connected to an excavator boom (not shown), a rotor 6 which is connected to the stator via a rotary connection 4 and to which an excavator gripper (not shown) can be fastened, and a drive mechanism 8 which acts between the stator 1 and rotor 6.
  • the rotary connection 4 is consistently designed as a roller bearing arrangement that absorbs both axial and radial and moment loads, which ensures a particularly compact design of the rotary device.
  • the running surfaces 10, 60 of the roller bearing arrangement are molded directly into the stator 1 or rotor 6 itself or into a part which is releasably connected to it in such a way that an axially symmetrical annular space is formed.
  • the rolling bearing bodies 41 can be guided, e.g. with a plug 11 'closable bore 11 or through an annular closable opening are introduced into the annular space.
  • the rotary connections 4 shown in FIGS. 1 to 10, 13 and 14 are four-point contact bearings with spherical roller bearing bodies 41.
  • a crossed roller bearing with roller-shaped roller bearing bodies can also be provided, which also absorbs the radial, axial and can absorb moment loads.
  • 11 and 12 finally show two arrangements with braced angular contact ball bearings or axial bearings.
  • the stator 1 contains a vane drive as the hydraulic drive mechanism 8, which according to FIG. 2 can be designed as a swivel vane drive 8 ′ with a stop 81 ′ and according to FIG. 3 as a rotating vane drive 8 ′′.
  • the stator 1 essentially consists of three Parts, the cup-shaped housing part 12, which contains, among other things, the drive mechanism 8, the bearing part designed as a threaded ring 13 and a non-rotatably connected to the housing 12 intermediate ring 14 which limits the drive mechanism 8 downwards and contains the wear-prone radial sealing ring 15.
  • the cup-shaped Housing part 12 has an internal thread 16 at its lower end, by means of which it can be detachably fastened to the external thread 17 of the threaded ring 13.
  • the housing part 12 can thus be easily removed, for example for repair and maintenance purposes, exposing the drive mechanism 8 and the intermediate ring 14 with the sealing ring 15 from the ring nut 13 removed and then screwed back on.
  • the threaded ring 13 contains a recess 18 in its externally accessible circumferential area, into which a mounting tool can be inserted, via which a tool for unscrewing or screwing on the housing part 12 required torque can be exerted on the threaded ring.
  • the rotor 6 contains a cylindrical shaft 62 and a flange 63 which projects radially in the lower region and on which bores 64 are provided for fastening the gripper arrangement. If the threaded ring 13 is to be removed from the rotor shaft 62, the plug 11 'must first be removed from the bore 11 when the housing part 12 is removed, so that the roller bearing bodies 41 can be successively removed from the annular space 10, 60 through the bore 11. In the assembled state, the plug 11 'is secured to the threaded ring 13 by a pin 19 and is also covered by the lower edge region of the housing part 12, so that it cannot be unintentionally released during operation.
  • the wing drive 8 'or 8 "in the case of FIG. 2 and one in the case of FIG. 3 contains two wings 80 which are mounted in a recess 65 of the rotor shaft 62 and pressed under the action of a compression spring 81 against the inner surface 20 of the stator 1, which divide the annular space 82 formed between the stator 1 and the rotor 6 into separate chambers.
  • the annular space 82 can optionally be connected via the openings 83, 84 to the inflow line or the return line of a hydraulic pump arrangement, not shown, depending on the desired direction of rotation Hydraulic lines are located in the upper area of the housing part 12.
  • the exemplary embodiments of a rotary device shown in FIG. 4 contain in the right part a radial piston drive 8 111 with radial cam track 24 in the stator and in the left part an axial piston drive 8 IV with two axial cam tracks 25 in the stator.
  • the cylinder drum 85 is annular and has an internal toothing 86 with which it is pushed onto an external toothing 68 of the rotor shaft from above and is connected to the latter in a rotationally fixed manner.
  • the hydraulic fluid is supplied and returned to and from the piston cylinders from above via a plan distributor 26, the channels 27 of which are connected to the corresponding hydraulic lines via the connections 21 on the stator housing 12. Otherwise, the structure is similar to the embodiment of FIG. 1.
  • the stator 1 is again in three parts and consists of a cup-shaped housing part 12 which overlaps the drive mechanism, a threaded ring 13 screwed to the housing part 12 and an intermediate ring 14 with radial seal 15 which is connected in a rotationally fixed manner to the housing part 12 and limits the drive mechanism downwards.
  • the rotary connection 4 is through a four-point bearing is formed, the running surfaces of which are molded directly into the threaded ring 13 and the rotor shaft 62.
  • At the upper end of the rotor shaft 62 there is also a radial bearing 5 designed as a floating bearing.
  • Fig. 5 shows two further embodiments of a rotating device, of which the one shown on the right a wing drive 8 V and the left Darge introduced an inner gerotor 8 VI contains.
  • Be the F lügelantrieb for example, as a rotary vane drive with stop shown in FIG. 2 or as around rotating vane type shown in FIG. 3 or Fig. 6 are formed.
  • a larger number of is provided in the same angular distance from each other in recesses 65 of the annular body 88 'are arranged wings 80, which are pressed by means of pressure springs 81 at their end faces against the inner surface 20 of the stator 1 and on in this way divide the annular space 82 into a plurality of chambers which can be acted upon separately with hydraulic fluid.
  • the inner gerotor 8 vi or internal gear motor corresponding to the left part of FIG. 5 is shown enlarged in cross section in FIG. 7. It consists of an inner toothed ring 88 fitted with a splined profile 87 on the rotor shaft 62 and an intermediate toothed ring 90 which interacts both with the teeth 89 of the inner toothed ring 88 and with the teeth 28 of the stator housing 12.
  • the toothed rings which interact with one another each differ by one Tooth.
  • the stator 1 with the outer ring gear 89 and the rotor 6 with the inner ring gear 88 are arranged concentrically to one another, while the middle tooth ring 90 is arranged eccentrically to this and accordingly executes a wobbling movement around the common stator and rotor axis during the rotation.
  • the operation of the gerotor is known per se (cf. DE-OS 29 22 921).
  • FIG. 5 coincides with the rotating devices according to FIGS. 1 and 4, so that reference can be made to the above statements in this regard.
  • 8 shows two further exemplary embodiments of a rotating device, of which the one shown in the right part in turn contains a wing drive 8 V and the one shown in the left part an inner gerotor 8 VI .
  • the difference from the exemplary embodiments according to FIG. 5 essentially consists in the fact that the upper part of the stator 12 1 is not a pot housing, but in plate construction with the bearing ring 13 'and the drive part 8 V or . 8 VI is connected by means of screws 29 and pins 30.
  • This design requires a slightly larger diameter than the exemplary embodiments according to FIG. 5, since the screws 29 and pins 30 require additional space in the radial direction.
  • FIG. 9 also shows a rotary device with radial piston drive 8 VII , in which the stator 1 contains a shaft 32 with cylinder bores 91, 94 for receiving the pistons 92 and a central distributor 93, while the rotor 6 as a pot housing with a radial curve 70 for support the piston 92 is formed.
  • the four-point bearing 4 with its bearing grooves 10 ', 60' and roller bearing bodies 41 is located above the area containing the drive mechanism B VII directly between the stator 1 and the rotor 6, both of which are formed in one piece.
  • the radial floating bearing arranged in the lower region of the rotating device can either be designed as a sliding bearing 5 '(right part of FIG. 9) or as a rolling bearing 5 "(left part of FIG. 9).
  • the structure and function of the radial piston drive 8 VII is on known (see. DE-PS 23 38 736).
  • FIG. 10 shows two further exemplary embodiments of a rotating device which has an axial piston drive B VIII with an axial cam track 70 'in the rotor.
  • the hydraulic fluid is supplied and returned to and from the piston cylinders 91 'from above via a cylindrical distributor 93' which is arranged in a cylinder bore 94 'of the stator 1.
  • a four-point bearing is provided as the rotary connection 4, the inner running surface 10 'of which is arranged directly in the cylindrical shaft 32' of the stator 1.
  • the outer running surface 60 'of the four-point contact bearing is located on a ring 74 which is connected to the rotor part 62' by means of a plurality of screws 78 distributed over the circumference.
  • the ring 74 there is a filling opening 71 for the roller bearing body 41, which can be closed with a stopper 71 '.
  • the outer running surface 60 'of the four-point contact bearing is formed in two parts. One half is molded directly into the material of the rotor part 62 ', while the other half is molded into a flange ring 63' which can be fastened to the rotor part 62 'with a plurality of screws 73'.
  • the roller bearing bodies 41 can be introduced into the annular space of the bearing through an annular opening, which is released when the flange ring 63 'is removed.
  • Bores 64 are provided on the flange ring 63 'as well as on the flange 63 in the right part of FIG.
  • the exemplary embodiments shown in FIG. 10 enable a construction with a particularly low overall height.
  • FIG. 11 shows two further exemplary embodiments with radial piston drive 8 VII , in which the stator 1 contains a shaft 32 with a cylindrical bore 91, 94 for receiving the pistons 92 and a central distributor 93, while the rotor 6 as a pot housing with a radial curve 70 for support the piston 92 is formed.
  • the bearing arrangement here consists of two angular contact ball bearings arranged above and below the drive mechanism, which can be braced with a threaded ring 34 or 76.
  • the threaded ring 34 or 76 can be readjusted in the event of wear, so that the bearing arrangement can always be kept free of play.
  • the inner treads 10 "and 10" ' are molded directly into the stator shaft, while the outer tread 60' 'is molded into the rotor material and the tread 60' 'into the threaded ring 76.
  • the treads which are concavely curved in cross-section, have a reduced notch effect with reduced risk of breakage compared to the sharply offset shoulders, as are provided when using prefabricated bearings.
  • the threaded ring 76 has an external thread with which it can be screwed into a corresponding internal thread on the rotor 6 while the bearing arrangement is braced.
  • the threaded ring 76 contains a plurality of recesses 77 which are accessible from the outside and on which an assembly tool can be attached.
  • the arrangement shown in the right part of FIG. 11 is particularly suitable for those rotating devices which have a suspension device 39 which does not widen upwards.
  • stator-side threaded ring 34 is appropriate, since a threaded ring on the rotor side would not be accessible from the outside.
  • the threaded ring 34 can be screwed with its internal thread onto an external thread of the stator shaft 32 while bracing the bearing arrangement.
  • Recesses 18 ' are also provided on the threaded ring 34, on which an assembly tool can be attached.
  • the roller bearing arrangement 4 consists of two spaced-apart, mutually braced axial roller bearings, which in the clamped state can absorb both axial and moment loads.
  • the roller-shaped roller bearing bodies 41 ", 41"' are supported directly on the rotor side on the treads 60 "and 60"' molded there.
  • Direct support on the stator is also provided on the stator side in the area of the tread 10 ′′, while the tread 10 ′′ is formed by an end face of the threaded ring 34.
  • the bearing arrangement is braced with the aid of the threaded ring 34, which can be screwed with its internal thread onto a corresponding external thread of the stator shaft 32.
  • the drive mechanism 8 not shown, can in turn consist of one of the internal hydraulic drives explained in the context of the above exemplary embodiments.
  • 13 and 14 yet D deer device illustrated a having an external drive mechanism 8 IX in Fig..
  • the rotor 6 is provided with an outwardly facing ring gear 100 which interacts with a pinion 101 on the output shaft 102 of the drive motor 8 ix arranged on a stator arm 103.
  • a four-point bearing is provided as the rotary connection 4, the outer running surface 60 of which is arranged or molded in the part of the rotor 6 which carries the ring gear 100, while the inner running surface 10 is located on a cylindrical shaft 32 'of the stator 1 which engages in the rotor 6.
  • the treads 10, 60 of the four-point bearing molded into the stator and rotor material offer considerable advantages in terms of a compact design, it is also possible without major disadvantages to use commercially available four-point bearings with separate races, since the space problems inside the stator and rotors are not so critical because of the drive motor moved outwards.
  • the disadvantages resulting from the asymmetry of the external drive mechanism 8 IX can be accepted if complicated rotary unions are required for actuating the gripper and possibly sawing or cutting devices provided on the gripper.
  • the space 104 inside the stator and the rotor is only available for the rotary unions 105, as indicated by dash-dotted lines in FIGS. 13 and 14.
  • An electrical rotary feedthrough is even possible here without major difficulties to be provided in the form of an electrical slip ring rotor (not shown) arranged centrally for an electrical energy supply in the gripper region or in a load magnet.
  • the attachment to an excavator boom is carried out with the suspension device 106 flanged to the stator 1, while an excavator gripper can be attached to the base plate 108 of the rotor 6 with screws 107.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Hydraulic Motors (AREA)
EP82110702A 1981-11-25 1982-11-19 Dispositif de rotation de charges suspendues Expired EP0080670B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3146695 1981-11-25
DE19813146695 DE3146695A1 (de) 1981-11-25 1981-11-25 Hydromotor, insbesondere fuer greiferdreheinrichtung an baggern oder kraenen

Publications (2)

Publication Number Publication Date
EP0080670A1 true EP0080670A1 (fr) 1983-06-08
EP0080670B1 EP0080670B1 (fr) 1987-05-06

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Family Applications (1)

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EP82110702A Expired EP0080670B1 (fr) 1981-11-25 1982-11-19 Dispositif de rotation de charges suspendues

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DE (2) DE3146695A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3720306A1 (de) * 1987-06-19 1989-01-05 Thumm Heinz Oelhydraulik Drehvorrichtung fuer haengende lasten
WO2003082725A1 (fr) * 2002-04-02 2003-10-09 Indexator Ab Systeme d'un rotateur
WO2011128427A3 (fr) * 2010-04-17 2011-12-29 Holp Gmbh Dispositif de rotation pour un équipement auxiliaire d'un engin de travaux publics
WO2016099372A1 (fr) * 2014-12-19 2016-06-23 Indexator Rotator Systems Ab Rotateur pour un outil porté par une flèche
CN112154117A (zh) * 2018-06-08 2020-12-29 因得克斯阿托尔罗塔托尔系统股份公司 液压转子装置
EP3981727A1 (fr) * 2020-10-06 2022-04-13 LASCO Heutechnik GmbH Couronne rotative, système de préhension, ainsi que grue

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE457436B (sv) * 1987-12-28 1988-12-27 Oesa Ab Rotator foer kranburna arbetsredskap
DE3812883A1 (de) * 1988-04-18 1989-01-26 Manfred Keller Hydraulischer schwenkantrieb mit drehmomentuebersetzung
DE3843753A1 (de) * 1988-12-24 1990-06-28 Schaeff Karl Gmbh & Co Baggerarm
DE4335678C2 (de) * 1993-10-20 2002-06-20 Thumm Heinz Oelhydraulik Drehvorrichtung für Baggergreifer
DE29621601U1 (de) * 1996-12-12 1998-04-09 Kinshofer Greiftechnik GmbH, 83666 Waakirchen Zweischalengreifer
FI114436B (fi) * 2000-07-07 2004-10-29 Plustech Oy Muunninyksikkö
DE10309258B4 (de) * 2003-03-03 2006-10-12 Archimedes Voulgaris Hydraulikmotorenbau Gmbh Einrichtung zur Befestigung und zum Drehantrieb eines Greiferwerkzeugs
US20070215371A1 (en) * 2003-10-22 2007-09-20 Wright Stewart J Dampening Apparatus
DE102008025026A1 (de) * 2008-05-24 2009-11-26 MTS Gesellschaft für Maschinentechnik und Sonderbauten mbH Bagger-Zusatzgerät

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FR332292A (fr) * 1903-05-22 1903-10-20 Schmid Roost J Couronne de roulement pour coussinets à billes
GB459995A (en) * 1935-06-29 1937-01-19 Packard Motor Car Co Improved mountings for ball bearings and methods of assembling same
FR817265A (fr) * 1936-05-08 1937-08-31 Roulement-butée à billes
DE1276476B (de) * 1966-06-30 1968-08-29 Zahnradfabrik Friedrichshafen Lagerung einer Gewindespindel fuer Kraftfahrzeuglenkungen
DE2338736A1 (de) * 1973-07-31 1975-02-20 Thumm Fa Heinz Hydraulik-motor fuer den drehantrieb eines bagger-greifers
FR2265664A1 (en) * 1974-03-29 1975-10-24 Stimec Bernard Crane load anti-gyratory mechanism - has articulated link between upper frame and lower one engaging with load
US4059316A (en) * 1976-06-21 1977-11-22 Reed Tool Company Bearing retaining pin for earth boring drill
FR2358811A7 (fr) * 1976-07-15 1978-02-10 Bobin Michel Grappin destine notamment a la manutention de la ferraille
DE2922921A1 (de) * 1978-06-07 1979-12-20 Nichols Co W H Innen-gerotor und verfahren zu seinem betrieb
DE2838346A1 (de) * 1978-09-02 1980-03-20 Thumm Fa Heinz Drehvorrichtung fuer einen baggergreifer o.dgl.
DE2838428A1 (de) * 1978-09-02 1980-03-20 Thumm Fa Heinz Drehvorrichtung fuer haengende lasten

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GB817964A (en) * 1956-07-23 1959-08-06 Frederick Weatherill Improvements relating to oscillating vane hydraulic motors
FR1498399A (fr) * 1966-06-24 1967-10-20 Engin hydraulique rotatif
GB2009351B (en) * 1977-12-06 1982-05-26 Poclain Sa Device for the rotary assembly of a member controlled by pressurised fluid

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR332292A (fr) * 1903-05-22 1903-10-20 Schmid Roost J Couronne de roulement pour coussinets à billes
GB459995A (en) * 1935-06-29 1937-01-19 Packard Motor Car Co Improved mountings for ball bearings and methods of assembling same
FR817265A (fr) * 1936-05-08 1937-08-31 Roulement-butée à billes
DE1276476B (de) * 1966-06-30 1968-08-29 Zahnradfabrik Friedrichshafen Lagerung einer Gewindespindel fuer Kraftfahrzeuglenkungen
DE2338736A1 (de) * 1973-07-31 1975-02-20 Thumm Fa Heinz Hydraulik-motor fuer den drehantrieb eines bagger-greifers
FR2265664A1 (en) * 1974-03-29 1975-10-24 Stimec Bernard Crane load anti-gyratory mechanism - has articulated link between upper frame and lower one engaging with load
US4059316A (en) * 1976-06-21 1977-11-22 Reed Tool Company Bearing retaining pin for earth boring drill
FR2358811A7 (fr) * 1976-07-15 1978-02-10 Bobin Michel Grappin destine notamment a la manutention de la ferraille
DE2922921A1 (de) * 1978-06-07 1979-12-20 Nichols Co W H Innen-gerotor und verfahren zu seinem betrieb
DE2838346A1 (de) * 1978-09-02 1980-03-20 Thumm Fa Heinz Drehvorrichtung fuer einen baggergreifer o.dgl.
DE2838428A1 (de) * 1978-09-02 1980-03-20 Thumm Fa Heinz Drehvorrichtung fuer haengende lasten

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3720306A1 (de) * 1987-06-19 1989-01-05 Thumm Heinz Oelhydraulik Drehvorrichtung fuer haengende lasten
WO2003082725A1 (fr) * 2002-04-02 2003-10-09 Indexator Ab Systeme d'un rotateur
WO2011128427A3 (fr) * 2010-04-17 2011-12-29 Holp Gmbh Dispositif de rotation pour un équipement auxiliaire d'un engin de travaux publics
WO2016099372A1 (fr) * 2014-12-19 2016-06-23 Indexator Rotator Systems Ab Rotateur pour un outil porté par une flèche
CN112154117A (zh) * 2018-06-08 2020-12-29 因得克斯阿托尔罗塔托尔系统股份公司 液压转子装置
CN112154117B (zh) * 2018-06-08 2023-02-28 因得克斯阿托尔罗塔托尔系统股份公司 液压转子装置
EP3981727A1 (fr) * 2020-10-06 2022-04-13 LASCO Heutechnik GmbH Couronne rotative, système de préhension, ainsi que grue

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Publication number Publication date
DE3276234D1 (en) 1987-06-11
DE3146695C2 (fr) 1993-04-22
DE3146695A1 (de) 1983-07-07
EP0080670B1 (fr) 1987-05-06

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