The invention refers to a bearing arrangement for supporting a shaft, which is made of components having different thermal expansion coefficients, wherein the bearing arrangement comprises a thermal decoupling.
Bearing arrangements of different kinds are known from the state of the art. In particular in case of sliding bearings, it is often desired that a bearing insert of the sliding bearing is made of a wear-resistant material, e.g. a ceramic material, for reducing wear. When such a bearing insert co-operates with a shaft which is e.g. made of a steel material, problems may occur due to the thermal expansion coefficient of steel, which is much higher compared to that of the ceramic material. This may result in damages at the bearing arrangement.
From EP 0 563 437 A2, a bearing arrangement is known, in which a ceramic bushing is supported in a centering manner opposite to a shaft at an outer periphery of the bushing by means of a counter-bearing arrangement. This bearing arrangement basically has proven of value and is e.g. used for rotary pumps. Currently, however, increased requirements concerning the load capacity arose, and in particular the diameters of the shafts are made larger due to the high demand for larger equipment. Further, speed-controlled machines are more and more used, such that different duty points with different heat generation occur due to the speed control. Therewith, it is not possible to adapt the bearing arrangement for just one duty point.
It is therefore an object underlying the present invention to provide a bearing arrangement which secures a safe operation also upon regular speed changes of a shaft while having a simple structure and being manufactured easily and at low costs.
This object is solved by a bearing arrangement having the features of claim 1. The sub-claims comprise advantageous further developments of the invention.
The inventive bearing arrangement having the features of claim 1 has the advantage that it enables a thermal decoupling at the bearing, such that the individual components of the bearing arrangement can be made of materials having different thermal expansion coefficients. Therewith, the materials for the individual components can be adapted optimally to the respective requirements. According to the invention, a structure of the bearing arrangement can be very simple and cost-effective. According to the invention, this is achieved by shrink-fitting a band element onto an outer periphery of a rotating bearing ring such that a shrinkage connection is provided between the band element and the rotating bearing ring. Thus, the rotating bearing ring together with the shrink-fitted band element forms an interconnected element which is inserted into a recess of a retaining ring with a centering snug-fit. According to the invention, a centering snug-fit is a fit having no tolerance or a slight tolerance in the order of μm. Therewith, no press-fit may be present. The interconnected element may thus be inserted into and removed from the recess of the retaining ring manually. The band element is connected to the retaining ring by means of an axial connection. Herein, the interconnected element is at least partially surrounded by the retaining element in the radial direction, wherein the thermal decoupling between the interconnected element and the retaining element is enabled due the insertion of the interconnected element into the retaining element with a centering snug-fit. A stationary bearing ring and a rotating bearing ring form an axial sliding bearing. Therewith, undesired alterations of the running surface positions at the axial sliding bearing due to thermal alterations can be compensated according to the invention. Therewith, a damage of the running surfaces by a so-called edge loading can be prevented.
Particularly preferred, the stationary bearing ring additionally has a sliding surface that is directed radially inwardly, in order to form a radial sliding bearing together with the bushing that surrounds the shaft. Therewith, a radial sliding bearing and an axial sliding bearing can simultaneously be provided at the stationary bearing ring. Due to this multiple surface support at the stationary bearing ring, in particular the number of components can be reduced and a compact bearing arrangement can be provided.
Particularly preferred, the band element is formed symmetrically with respect to an axis disposed perpendicular with respect to a center axis of the shaft. Therewith, it is guaranteed that a constant alteration of the dimensions occur upon temperature changes at the band element. In this context, the band element preferably comprises a large bevel at the two edge portions directed radially outwardly.
Particularly preferred, the bearing arrangement is formed as a twin bearing arrangement and therewith comprises two rotating bearing rings and two stationary bearing rings. Therewith, the shaft can be supported at two mutually spaced regions. Preferably, the rotating bearing rings are arranged at stationary bearing ring sides facing each other in the axial direction for this purpose. In other words: In the axial direction, the rotating bearing rings are arranged between the stationary bearing rings. As an alternative, the rotating bearing rings are arranged at stationary bearing ring sides facing away from each other in the axial direction. In other words: In the axial direction, the stationary bearing rings are arranged between the rotating bearing rings.
Further, the present invention relates to a magnetic coupling including the inventive bearing arrangement. Magnetic couplings are preferably used in speed-controlled machines, in particular in pumps.
In the following, the present invention is described in detail on the basis of preferred embodiments in connection with the accompanying drawing, in which:
In the following, a bearing arrangement 1 according to a first embodiment of the invention is described in detail with reference to
The bearing arrangement 1 of the shown embodiment serves to simultaneously support the shaft 3 axially as well as radially. In this case, the bearing arrangement 1 is provided as a twin bearing for supporting the shaft 3 at two mutually spaced regions. For this purpose, the bearing arrangement comprises a pair of axial sliding bearings 14, 14′ and a pair of radial sliding bearings 15, 15′. The axial sliding bearings 14, 14′ respectively comprise a rotating bearing ring 7, 7′ as well as a stationary bearing ring 6, 6′. The radial sliding bearings 15, 15′ are formed in the radial direction of the shaft between the stationary bearing ring 6, 6′ and an outer boundary 2b of the bushing 2. As is discernible from
The shaft 3 is connected to the bushing 2 at the two opposing ends of the bushing 2 by means of connection or centering arrangements 21, 21′. The connection arrangements 21, 21′ serve to concentrically position the bushing 2 relative to the shaft 3. Each of the connection arrangements 21, 21′ comprises an annular retaining element 8, 8′ which is connected to the shaft 3 by means of pins 12. Further, also the rotating bearing rings 7, 7′ are part of the connection arrangements 21, 21′. As is in particular discernible from
The annular band element 9 further comprises large bevels 9a, 9b at its edge portions directed radially outwardly, wherein these bevels are also formed symmetrically with respect to the axis A. For attaching the interconnected element 23, a snap ring 11 is provided at the bevel 9b of the annular band element 9, which snap ring is retained in a recess in the rim portion 8b.
Therewith, a thermal decoupling between the components having different thermal expansion coefficients can be achieved according to the invention. Besides the shaft 3, also the annular retaining element 8 as well as the annular band element 9 are made of a metallic material. Contrary thereto, the rotating bearing ring 7 and the bushing 2 are made of a ceramic material. Consequently, the rotating bearing 7 does not react with a tipping when the temperature changes, which can result in the wear occurring in the state of the art at the axial sliding surfaces 7a, 6a of the axial sliding bearings 14, 14′. Changes of the tension profile in the shrinkage connection 22 between the annular band element 9 and the rotating bearing ring 7 can be compensated by the interconnected element 23 being inserted with the centering snug-fit. Due to the symmetric design of the annular band element 9 with respect to the axis A, in particular, no tipping of the rotating bearing ring 7 occurs upon different thermal expansions of the individual components.
Number | Date | Country | Kind |
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20 2009 004 160.3 | Mar 2009 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
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PCT/EP2010/001541 | 3/11/2010 | WO | 00 | 12/8/2011 |