DE4326150C2 - Device for the axial fixing of components - Google Patents

Description

The invention relates to a device for the axial fixing of components, especially of bearing rings, in particular with the features from the Preamble of claim 1.

Already known options for axially securing components, Rolling bearing rings in particular are conventional and very use simply designed components, for example adapter sleeve, nut e. t. c. For larger components and especially for the application case of large, Forces to be absorbed by the bearing are fixed in the axial direction problematic with these options due to the also enormous Component sizes of the fixing elements and thus also in Related increase in effort in assembly and disassembly. In most cases, the use of additional aids For example, a hammer required to reduce the Occupational safety for the personnel leads.

When using nuts for the axial fixing of components, in particular of rolling bearing rings occurs in addition to the problem of the size of the required Power to tighten the mother also had the problem of determining the tightening torque to prevent accidental loosening of the nut from the shaft in the operating state to avoid.

In the known from an unpublished internal proposal Arrangement for the axial fixing of components, especially one Rolling bearing inner ring for use in rolling mills, the determination is made through a mechanical latch mechanism that Fixing element fixed in its position in relation to the inner bearing ring, the force required to tighten or axially set the  Fixing element is applied hydraulically. This version is however, from a large number of components, a high manufacturing and Assembly effort and a weakening of the shaft by the for the function of the ratchet mechanism required ring and longitudinal grooves featured.

A generic device for axially fixing a Ring element on a shaft is from the document DE 38 16 370 A1 known. The device comprises a sleeve with one on the shaft frictionally fixable bore and one axially against the ring element adjustable face. So that an extremely precise fixation and support of the ring element can be reached on the shaft, the sleeve consists of a thick-walled outer sleeve with a weakly tapered bore fitting surface with one in this built-in thin-walled inner sleeve with a positive adapted conical mantle fitting surface. Between the outer sleeve and the An inner space is formed in the inner sleeve in which a sealing element is installed. This sealing element limits one axially inwards Pressure oil chamber. In the outer sleeve is between the mating surfaces mouth oil hole incorporated. At least the end of the big one Diameter of the inner sleeve protrudes axially beyond the outer sleeve when the device is fixed on the shaft. For the axial fixing of a Ring element on a shaft, the inner sleeve is designed such that this one at the end of its smaller diameter on its lateral surface Has threaded section on which a flange ring is screwed. However, this only serves as a fastening element for holding together the outer sleeve with the inner sleeve so that no sliding of the outer sleeve done by the inner sleeve. A major disadvantage of such Execution is that in addition to the possibility of twisting the two sleeves against each other in the circumferential direction no limit to Displacement in the axial direction, especially when releasing the inner one  Sleeve is provided, which from a safety point of view as is problematic to look at.

The invention is therefore based on the object of a device for axial fixing of machine parts, especially roller bearing rings, to develop in such a way that the disadvantages mentioned are avoided. The number of required components, the manufacturing and the Assembly effort should at the same time increase occupational safety for assembly personnel are kept as low as possible.

A key focus is also on reducing the Machine downtimes that are quick and easy to perform Assembly and disassembly required.

The device should be designed and designed such that on the shaft debilitating grooves and other constructive measures can be dispensed with can.

The object is achieved by the characterizing features of claims 1 and 4 solved. Preferred embodiments are in the subclaims reproduced.

By using two coaxial sleeves - one inner and one an outer sleeve - which are arranged and designed so that they at least one gap space, which can be acted upon with pressure medium, on their Forming interfaces with each other takes place when the gap space is applied deformation of the inner sleeve in the radial direction with pressure medium, wherein the inner sleeve is braced at least indirectly with the shaft. This includes the case where an additional annular element is provided between the inner sleeve and shaft.  

The forces for generating the frictional connection are caused by pressure medium upset and forwarded. The axial fixing and releasing is thus possible with simple, less force-intensive operations. As Pressure fluid is preferably a liquid, especially hydraulic oil used. Such a press fit produced by pressure medium is through characterized a simple and inexpensive manufacture. To the at least indirect bracing of the shaft and inner sleeve is only one Pressurizing the corresponding gap space required. The gaps are closed again to release the connection relieve.

The device according to the invention for the axial fixing of components is characterized by an inexpensive production, a low Manufacturing effort, short assembly and disassembly times and high Occupational safety for the staff.

Bracing the inner sleeve with the shaft can be done in several ways happen. In the first case, inner and outer sleeves are over at least part of their length is complementary conical to each other. Both At their interfaces, sleeves form at least one gap space, which at Pressurization in the axial direction becomes larger, whereby preferably the outer sleeve against the inner sleeve or else conversely conceivable, postponed. Both the inner sleeve and the outer sleeve also provides direct support in the axial direction take over the component to be determined.

In the second case, the inner and outer sleeves are on their outer sides connected to each other and thus form an annular interior, the is pressurized. There is a between the inner sleeve and the shaft additional sleeve-shaped element arranged that by deformation of the inner sleeve in the radial direction when the annular  Interior is clamped frictionally with the shaft. For Realization of the bracing of shaft and sleeve-shaped element and sleeve-shaped element and inner sleeve, however, are the individual To design elements so that certain sleeve wall thickness ratios to each other.

The direct support of the component to be fixed in the axial direction in this case preferably takes place through the sleeve-shaped element.

Another advantage of the device according to the invention is that for Realization of the frictional connection not through grooves and other measures causing a notch effect are weakened.

The invention is explained in more detail with reference to drawings. In it is in shown the following:

Fig. 1 shows an embodiment of an arrangement according to the invention in a sectional view for the application of an axial fixing of a rolling bearing ring;

FIG. 2 shows a section of view I from FIG. 1;

Fig. 3 shows an embodiment of FIG 1 with a different embodiment of the inner sleeve.

Fig. 4 shows a further embodiment of the device according to the invention with three sleeves.

Fig. 1 illustrates an embodiment of an arrangement according to the invention in a sectional view.

A rolling bearing 1 , comprising an inner ring 2 and an outer ring 3 , is pressed in the radial direction by selecting the appropriate fits, on the outer diameter d _{wa of} a shaft 4 and in the inner diameter d _{bi of} a bore in a bearing housing 5 .

In the axial direction, the roller bearing, which is to act as a fixed bearing in this exemplary embodiment, is fixed on the left side in the drawing by a shaft shoulder of the shaft 4 on the inner ring and a stop on the outer ring 3, not shown in detail here. A preferred exemplary embodiment of the device according to the invention for fixing the inner ring 2 is provided on the right-hand side. A sleeve 7 enclosing the shaft end, which is conical on the outer circumference 8 over at least part of its length, is frictionally clamped to the shaft 4 . The sleeve 7 is flange-like in the other part, which is directed towards the inner ring 2 . An end face 9 of the sleeve 7 supports the inner ring 2 on its end face 10 . In order to realize the frictional engagement between shaft 4 and sleeve 7, the sleeve 7 is surrounded by a second sleeve 11 l on at least a part of its length. Over a part of its length, this sleeve 11 has an inner surface 12 that is conically complementary to the surface 8 of the sleeve 7 . A stop 13 , which is designed in an L-shape, forms a structural unit with the sleeve 7 and is used for guidance and as a stop for the sleeve 11 . According to the design of the sleeves 11 and 7 , their interfaces 8 and 12 form the walls of at least one rotationally symmetrical gap space. In this example, both form conical annular gap spaces 14 and 15 with each other, which have separate pressure medium channels 16 and 17 , 17 being represented by dash-dot lines, since 17 has only been projected into the plane of the drawing. Another pressure medium channel 18 is usually also offset in one plane from the pressure medium channels 16 and 17 , but was also projected here into the drawing plane. By supplying pressure medium into the gap 14 , the sleeve 11 is displaced against the sleeve 7 and braced by the consequent radial expansion of the sleeve 7 against the shaft 4 . In order for the displacement to take place at the interfaces as wear-free as possible, the conical surfaces 8 and 12 are lubricated by high pressure oil via the channel 18 . Both sleeves or the gap spaces 14 and 15 are sealed off via the O-rings 19 to 23 . This also serves to prevent the lubricating film from tearing open, which is reflected in increased wear on the contact surfaces.

To release the frictional connection between shaft 4 and sleeve 7 , the gap 14 is relaxed again and the gap 15 is pressurized. The outer sleeve 11 is withdrawn from the inner, which leads to a cancellation of the radial expansion of the inner sleeve 7 . So that the outer sleeve is not completely detached from the inner sleeve when loosened, the outer sleeve 7 has at least one guide pin 24 which is guided in a correspondingly assigned through bore 25 in the stop 13 and limits the axial mobility of the sleeve 11 . This stop is not necessary to implement the function of axially securing the inner ring 2 ; it serves here to prevent the outer sleeve from completely detaching from the inner sleeve 7 in the event of relaxation of the pressure chamber 14 or the pressurization of the pressure chamber 15 and to avoid twisting of the two sleeves against one another. The guide pin 24 forms a structural unit with the outer sleeve 11 .

Also on the end face 27 of the outer sleeve, a pressure medium connection 28 to 30 is assigned to the individual pressure medium channels. These are used to control the supply of pressurized oil and close the channels after the frictional connection has been created.

In this illustration, guide pins 24 and connection elements 28 - 30 have been projected back into a plane. The section of the side view 1 shown in FIG. 2 illustrates the arrangement of the pressure medium connections 28 and 29 , which is preferably offset to a common diameter d, and the arrangement of the guide bolt 24, which is also carried out on this diameter, and accordingly also the through bore 25 in the stop 13 . For easier handling of the pressure medium connections 28 and 29, as well as the pressure medium connection 30 ( not shown here) during assembly and disassembly, the L-shaped stop 13 preferably has correspondingly open-cut recesses 31 in the region of its outer diameter d _AA .

The number of guide bolts 24 arranged on the diameter d and correspondingly the through bores 25 assigned to the stop 13 are determined in accordance with the requirements of the specific application. Preferably, however, at least two guide bolts and two through bores 25 are provided on the stop 13 .

The pressure medium channel 17 shown in FIG. 1 and the gap space 15 serve here as additional support for releasing the frictional engagement. While the pressure medium channel 16 or the gap space 14 is relieved, the gap space 15 is acted upon by pressure medium and thus the outer sleeve is moved away from the inner ring 2 . A waiver for reasons of installation space or other design conditions is possible without restricting the function.

To ensure that the entire device 6 , including the inner and outer sleeves 7 and 11 , does not slide off the shaft 4 during disassembly after the frictional engagement has been released, a cover 32 is provided which is fastened to the outer ring stop 33 . The outer ring stop 33 is in turn attached to the bearing housing 5 . A seal 34 is provided between the outer ring stop 33 and the inner sleeve 7 , which prevents the lubricant for bearing lubrication from escaping from the bearing area and the entry of foreign bodies and substances into the bearing.

Further constructive details for the design of the two sleeves are the Voith brochure "Connection technology" can be removed.

FIG. 3 illustrates an embodiment of the device according to the invention in accordance with the principle described in FIG. 1.

The basic structure and mode of operation corresponds to that described in FIG. 1, which is why the same reference numerals are used for the same elements. However, the inner sleeve 7 has an almost conical shape over its entire length. The flange-like design of the part of the inner sleeve facing the inner ring 2 has been replaced by a design which avoids the abrupt change in the outer diameter of the inner sleeve 7 , as a result of which the rigidity of the inner sleeve is increased in this front region.

In FIG. 4, a further embodiment of the device according to the invention is shown schematically. The inner ring 2 is axially fixed here by means of a hollow bush 37 , comprising an inner sleeve 7 and an outer sleeve 11 , which are connected to one another on both sides and form an annular space 38 which can be pressurized with pressure medium. The sleeve 7 is made very thin compared to the sleeve 11 in order to be able to deform when the space 38 is pressurized. An annular element 35 acts here as the fixing element, which is braced with the shaft 4 by expansion of the part 7 in the negative radial direction. The inner ring 2 is supported by mutual contact of the parts 35 and 2 on their end faces. The annular space 38 has at least one pressure medium channel 39 and a pressure medium connection 40 .

Details on the design and design of the hollow bushing and that The principle of operation is the Voith company brochure "Connection technology" remove.

The described exemplary embodiments illustrate the basic principle of Possibility of axial component definition using a frictional Connection. To adapt to the corresponding application constructive changes or the further design of the individual Components conceivable.

In the examples listed here, the device or its individual Components always carried out so that the shaft directly clamped sleeve also directly to be determined in the axial direction Component supports. With an appropriate design, however, others can Elements that are involved in the creation of the frictional connection at least are indirectly involved, the component to be determined in the axial direction support directly.

A special application of the device according to the invention is the application for the axial fixing of a bearing inner ring of a bearing for Rolling mills.

Claims (4)

1. Device for the axial fixing of components ( 2 ) on shafts and axes with the following features:

• 1.1 with two coaxial sleeves - an inner sleeve ( 7 ) and an outer sleeve ( 11 );
• 2. 1.2 the two sleeves are arranged such that they form at least one rotationally symmetrical and coaxial to the shaft gap space ( 14 , 15 ) with each other at the interfaces;
• 3. 1.3 the inner ( 7 ) and the outer sleeve ( 11 ) are complementary conical to each other over at least part of their length;
• 4. 1.4 the gap space ( 14 , 15 ) can be acted upon with pressure medium, whereby the gap space is enlarged when pressure medium is applied and the outer sleeve is displaced against the inner sleeve;
• 5. 1.5 an end face ( 9 ) of the inner or outer sleeve supports the component ( 2 ) directly;

characterized by the following features:

• 1. 1.6 with a device that limits the displacement and rotation of the outer sleeve ( 11 ) relative to the inner sleeve ( 7 );
• 2. 1.7 the device comprises a, with the inner sleeve ( 11 ) a structural unit formable stop ( 13 ) for limiting the movement of the outer sleeve ( 11 ) in the axial direction and at least one, connected to the outer sleeve guide pin ( 24 );
• 3. 1.8 the stop ( 13 ) has through openings ( 25 ) for receiving the guide bolts ( 24 ).

2. Device according to claim 1, characterized in that the change in the outer diameter of the inner sleeve ( 7 ) takes place substantially over its entire length. 3. Device according to one of claims 1 or 2, characterized by the following features:

• 1. 3.1 the inner sleeve ( 7 ) with the stop ( 13 ) and the outer sleeve ( 11 ) form two gap spaces ( 14 , 15 ) with each other;
• 2. 3.2 a separate pressure medium channel ( 17 , 18 ) is assigned to each gap space ( 14 , 15 );
• 3. 3.3 the pressure medium channels are arranged in the outer sleeve ( 11 );
• 4. 3.4 the pressure medium channels ( 17 , 18 ) are each assigned a pressure medium connection ( 18 , 30 ).

4. Use of a device according to claims 1 to 3 for axial fixing of rolling bearing rings.