DE1976014U - PINLESS ROLLER BEARING FOR LARGE TILTING MOMENTS, AXIAL AND RADIAL LOADS. - Google Patents

Description

PATENT, π. LAWYER

DIPL.-ING.H. FROM SCHÜMANN

Bayer. Hypotheken- und Wechselbank Munich, 8 Munich 22, Widenmayerstraße 5

Account number MX 6342 Telegram address: Protector Munich

Postal checking account: Munich 49463 Telephone: 224893

31. OkI. 196?

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German Pafep.tcmi. Utility model body.

G. and J. Jaeger GmbH, Wuppertal-Elberfeld

Trunnion-free rolling bearings for large tilting moments, axial and radial loads

The rotary connection of the rotatable upper part with the Fixed lower part of slewing cranes, excavators and safety systems for ship and air traffic has as a result of the large Weight of the upper part to absorb large axial forces even at rest. For the lifting equipment mentioned, there is still one more the static overturning moment caused by the boom. Both types of load reach a multiple of the static Values if for the hoists as a result of the intermittent operation when picking up the load or for all of the aforementioned systems dynamic loads occur as a result of the wind pressure. This It is particularly difficult to safely absorb large loads if the slewing ring is designed without a pivot pin is what is usually preferable for design reasons.

It is already known to use a slewing ring for such to train pinless rotary joint in such a way that it consists of consists of an outer ring and a multi-part inner ring, each with one vertical and two horizontal raceways, cynical ones with a U-shaped space in

one wreath standing vertically and two wreaths horizontally lying cylindrical rollers are arranged. The division of the inner ring takes place in one not with the running surface planes matching level.

In the case of the trunnion-free rolling bearing after the control, the a running ring and a guide ring encompassing this U-shape owns, with cylindrical rollers between each two of each other associated annular and between the two arranged cylinder jacket-shaped running surfaces of these rings are, the guide ring is divided radially in the two planes of its circular running surfaces, so it consists of three Divide.

In this way, simple geometric shapes of the surfaces to be machined of all ring-shaped individual parts are obtained. This allows a simplified and thus cheaper machining of the rolling bearing and allows the highest level of accuracy in the manufacture of the bearing.

With double-acting axial cylindrical roller bearings, So shaft bearings with a wave washer, it is known to keep the two housing washers at a distance by means of a sleeve. This sleeve also serves as a run-up board for the outside directed side surfaces of the cylindrical rollers, which between the T / ellenscheibe and the two housing discs run. at the pivot-less timber bearing after the hiring are not only zvi / ei washers with horizontal running surfaces, but also there is a casing ring with a vertical running surface lying between these.

In a special embodiment of the innovation, they are axial loaded cylindrical rollers guided in cages, which are in radial Support direction on the edges of the guide ring while

for the axial guidance of the cylindrical rollers that transmit the radial forces only provided for the rims of the guide ring are. This results in a significantly simplified assembly of the bearing and a cage for the radial bearing saved at all.

Further details of the innovation are in the following Description of two exemplary embodiments explained with reference to the drawing, in which represents

lig. 1: a roller bearing with an inner race, cut axially; Pig. 2: a roller bearing with an outer race, cut axially.

In lig. 1, 1 denotes a raceway. He owns Bores 2, in which a thread 3 is cut, so that the race 1 with the rotatable upper part of the system, e.g. of an excavator, can be screwed tightly * The race 1 has the two circular running surfaces 4 and a cylinder jacket-shaped running surface 5. The running ring 1 encompassing guide ring that connects to the lower part of the system is connected, has a U-shaped cross-section and is composed of the center ring 6, the upper running disc 7 and the lower Running disk 8 assembled. For mutual centering of the annular parts 6, 7 and 8 have these bores 9 into which dowel pins 10 are inserted. By tie rod 11, through a bore 12 of the upper running disk 7 and the Grip middle ring 6 and into the nut thread 13 of the lower Running disk 8 are screwed in, the individual parts 6, 7 and 8 of the guide sr ing s clamped together. The upper pulley 7 has the annular running surface 14 which lies opposite the corresponding running surface 4 of the race 1. the lower running disk 8 has the annular running surface 15, that of the lower corresponding running surface 4 of the raceway

opposite. 33er cylinder jacket-shaped running surface 5 of the running ring 1 is located. Similarly designed running surface 16 of the central ring 6 opposite »Between each pair of the mutually associated running surfaces there are cylindrical roller sets 17, 18 and 19, of which the first two transmit the axial load, while the third transmits the radial load. The roller set 17 is guided in a cage 20 which is supported radially on the rim 21 of the center ring 6. In the same way, the roller set 18 is guided in a cage 20, the cage being able to be radially supported on the rim 22 of the center ring 6. The roller set 19 transmitting the radial load is guided in the axial direction between the ribs 23 and 24 of the center ring 6. The center ring 6 is provided with a ring gear 25 for the purpose of driving the upper part of the system by a pinion (not shown) of a drive motor attached to the upper part. Due to the simple geometric shapes of both the race 1 and the components 6, 7 and 8 of the guide ring, a considerable simplification of the machining is achieved. Because the axially loaded running surfaces 14 and 15 of the running disks 7 and 8 lie in the parting plane between the running disks and the center ring 6, they can be faced together with the mating faces in one operation. The mutual centering of the guide parts 6, 7 and 8 is also simplified because dowel pins 10 are provided instead of a centering collar. Finally, the simplified shape of all ring-shaped parts enables only an extremely small machining allowance to be provided.

In Fig. 2, a bearing similar to that shown in Fig. 1 is shown. The race 1 is designed as an outer ring, while the guide ring in contrast to that in Fig. 1 shown is divided only once, the parting line in turn in the plane of the running surface 15 of the lower running disk located. Although the guide ring is only divided once, the considerable simplification is also from this exemplary embodiment to see, which is achieved over the previously known versions.

Claims (4)

RÄ.62235W1. 'Expectations 1. Trunnion-free roller bearing to accommodate large tilting moments, axial and radial forces, with a U-shaped encompassing the race Guide ring, v / obei cylindrical rollers between each two of the associated circular ring-shaped and between the two cylindrically shaped running surfaces of these rings are arranged, characterized in that the guide ring is radial in the two planes of its circular running surfaces is divided. 2. Rolling bearing according to claim 1, characterized in that the cylindrical rollers transmitting the axial forces are guided in cages are, which are supported in the radial direction on the edges of the guide ring, while for the axial guidance of the radial forces transferring cylindrical rollers are provided exclusively on the edge of the guide ring. 3. Rolling bearing according to one of the preceding claims, characterized in that the parts of the guide ring by means of tie rods are clamped together and mutually centered by dowel pins .. 4. Y / roller bearing according to one of the preceding claims, characterized characterized in that a part of the guide ring with a ring gear is provided.