WO2014005922A1

WO2014005922A1 - Backup bearing for heavy-duty magnetic bearings in rotating machines

Info

Publication number: WO2014005922A1
Application number: PCT/EP2013/063518
Authority: WO
Inventors: Detlef Haje; Christoph Grund; Helmut Kühn
Original assignee: Siemens Aktiengesellschaft
Priority date: 2012-07-06
Filing date: 2013-06-27
Publication date: 2014-01-09
Also published as: EP2847479A1; DE102012211860B4; DE102012211860A1

Abstract

The invention relates to a turbomachine (100) comprising a housing (101), a shaft (102) which is mounted so as to be rotatable relative to the housing (101) about an axis of rotation (103) of the shaft, and a first support roll (110) that has a first axis of rotation (111). The first support roll (110) is located at a distance from the shaft (102). Furthermore, the first support roll (110) is disposed in such a way that the first support roll (110) and the shaft (102) can be force-transmittingly coupled to one another when the shaft (102) is displaced, and the first support roll (110) revolves about the first axis of rotation (111) when the shaft (102) rotates.

Description

description

Safety bearing for highly loaded magnetic bearings of rotating machinery

Technical area

The present invention relates to a turbomachine and a method for operating a turbomachine.

Background of the invention

In turbomachines, such as in a turbocompressor or in a turbine rotor blades are arranged on a rotatable shaft, which are flowed by a Strömungsme ^¬ dium. The shaft of a turbomachine is rotatably mounted with axial and radial bearings in a bearing housing of the turbomachine. To support the shaft in the bearing housing, bearings, for example, are used in conventional bearings. Furthermore, magnetic bearings are used with which a smooth rotatable mounting of the shaft is possible. Due to magnetic ^¬ forces, the shaft is rotatably mounted in a predetermined axial and / or radial position. Magnetic bearings can be designed as passive magnetic bearings. In passive magnetic bearings, for example, diamagnetic materials are used. With active magnetic bearings, the bearing force is generated by adjustable electromagnets. The electromagnets may be controlled to produce a desired magnetic force that holds the shaft in a predetermined radial and / or axial position.

In active axial magnetic bearings, the shaft has a Axialla- gerscheibe, which is rotatably held in a vorbe ^¬ certain position between two stator elements which are fixed to the bearing housing. The thrust washer is usually integrally formed already during production of the shaft. educated. Thus, the axial bearing disc, for example, GE rotates with ^¬ ^¬ means of turning or milling of the base body of the shaft. Alternatively, the thrust washer can also be mounted on the shaft.

In active radial magnetic bearings, the shaft is supported by the bearings annular (at least partially) enclosing magnetic bearings. The stator elements of an active magnetic bearing have coils to generate the electromagnetic forces. In order to disturb the electromagnetic flow as little as possible, the stator should as possible have no axial faces on ^¬ . The stator elements then each form a closed stator ring. Between two such stator rings is in the mounted state of the shaft, the thrust washer.

As an alternative to the magnetically levitated shafts, rotors of large machines, such as, for example, steam and gas turbines, generators or process gas compressors, can be mounted by means of slide bearings. A load-bearing lubricating film is used between the stationary and moving parts of the bearings.

Due to the power loss associated therewith, which is caused by the friction in the lubricating film and the required Plepleis ^¬ tion for the provision of the lubricant, who ^¬ the lower-loss storage techniques preferred, such as the magnetic bearings described above. The advantage of magnetic bearings is that they can be operated as far as possible without lubricating oil. Magnetic bearings can be successfully used, for example, for smaller rotor loads, for example up to two tons. However, for large rotor loads and for high peripheral speeds, which typically occur in the above-mentioned turbomachines, the provision of reliable backup bearings is necessary. A backup bearing catches the rotor in the event of a magnetic bearing failure, causing the shaft to leak. Existing fishing ^¬ bearing solutions offer a limited load-bearing capacity or encryption to schleißbeständigkeit, since the rotor falls upon failure of the magnetic ^¬ storage in the catch bearing and substantially terminates as a catch bearing without lubrication in a sliding bearing. The resulting friction loads require a fast deceleration of the rotors and limit the usability of the magnetic bearings.

In a design of the backup bearing as a rolling bearing, which surrounds the shaft, the rolling bearing must have a large shaft diameter. However, rolling bearings with such a large shaft diameter are not available for the required speeds and load capacities.

SUMMARY It is an object of the present invention to provide a stable bearing assembly of a shaft for a turbomachine be ^¬ riding determine.

The object is achieved with a turbomachine and a method for driving the fluid machine according to the inde ^¬ dependent claims.

According to a first aspect of the present invention, a turbomachine is described. The turbomachine includes a housing, a rotatable relative to the housing about a Wel ^¬ lendrehachse mounted shaft and a first Stützrol ^¬ le with a first rotational axis. The support roller is beabs ^¬ tandet arranged to the shaft. The first support roller is arranged fer ^¬ ner such that upon displacement of the shaft, for example in an axial and / or radial displacement of the shaft, a force-transmitting coupling between the first support roller (in particular between a Abroll ^¬ surface of the support roller) and the Wave (especially the Shaft surface) is generated and upon rotation of the shaft (at least during the force-transmitting coupling), the support roller rotates about the first axis of rotation. As a flow machine in the present Appli ^¬ dung a fluid energy machine is known, wherein the Ener ^¬ gieübertragung between the fluid and machine is carried out by a flow according to the laws of fluid dynamics. A turbomachine may, for example, be a turbocompressor, a gas turbine, a steam turbine, a jet engine or another turbine or a compressor of axial or radial design.

The shaft of the turbomachine is rotatable with respect to the housing, in particular a bearing housing, the Strömungsma ^¬ machine stored. The shaft of the turbomachine has the shaft rotation axis. A direction parallel to the axis of rotation is defined as the axial direction of the shaft. A direction which passes through the center of the shaft and is oriented perpendicular to the axis of rotation is referred to as the radial direction of the shaft and the turbomachine.

The first support roller is rotatable, for example by means of ei ^¬ nes roller bearing, mounted on the housing. The first support roller may have a cylindrical shape, wherein the first support ^¬ roller is mounted at their respective end portions by means of a sliding bearing or a rolling bearing on the housing. In a central region between the two end regions, the first support roller may have a cylindrical region which has a larger diameter than the two end regions. The first support roller can in this case be such arranged on the Ge ^¬ housing that, in the case where the turbo machine and the shaft in normal operation are located, there is a gap between the shaft and the central area of the first support roller. Shifts the shaft, wherein ^¬ play, due to a failure of the shaft bearing, the first supporting roller is arranged such that the shaft ^¬ due to the shift in contact with the first support roller comes so that there is a force-transmitting coupling over this contact area. The shaft is as it were on the support ^¬ role in the direction of the shaft. To avoid increased edge pressures, the support roller may have a spherical shape in the contact area with the shaft. The support roller, so to speak has a cylindrical rolling area, wherein the outer surface of the cylindrical Abrollbereichs is spherically formed from ^¬. Due to the convex, curved circumferential surface of the circumferential surface of the shaft at the axial ends of the Kantenberei- che easily respect. Withdrawn and thus Zvi ^¬ rule avoided in Kon ^¬ clock of the supporting roller with the shaft an edge pressure the axial ends of the supporting roller and the shaft.

At the contact areas of the support rollers with the shaft shrunk bearing bushes can be provided on the shaft.

The first support roller is made for example of hard rubber or a metal such as brass or steel. Example ^¬, the first support roller is made of a metallic body, wherein the contact surfaces are covered with the shaft with a soft coating, for example of rubber or a hard plastic. In particular, the material of the first support roller in the contact region with the shaft is softer or more ductile than the corresponding material of the shaft.

Further, the first support roller is arranged such that it rotates on contact with the shaft about its first axis of rotation. The first axis of rotation is aligned such that the first support roller rotates relative to the shaft such that there is no frictional or sliding connection in the contact region between the shaft and the first support roller but a rolling connection with a low rolling friction.

The diameter of the first support roller, and in particular the diameter of the central cylindrical portion of the first support roller, is smaller than the diameter of the shaft. Thus, a bearing journal diameter of the first support roller, which is stored for example roller bearings on the housing, smaller than a corresponding shaft bearing or a corresponding shaft journal diameter of the shaft, with which the shaft is rotatably mounted on the housing. Since the bearing ^¬ journal diameter of the first support roller is smaller than that of the shaft, the first support roller, for example at a rate ^¬ a rolling bearing having a high rotational speed, including egg ^¬ ner sufficient capacity.

In order to better distribute the forces to be transmitted from the shaft to a catch bearing according to the invention, a plurality of further support rollers, such as the second and third support rollers described below, can be arranged next to the first support roller. Thus, the transmitted forces are split and maintained at the appropriate support rollers at an acceptable level, since the forces are distributed over several support rollers.

According to a further exemplary embodiment, the first support roller is arranged such that the first rotation axis is parallel to the shaft rotation axis. The first support roller is arranged such that upon displacement of the shaft ent ^¬ long the direction of gravity, the force-transmitting coupling between the first support roller and the shaft can be generated. The first support roller is arranged, for example, under the shaft, wherein the first axis of rotation is aligned parallel to the shaft rotation ^¬ axis. If the shaft example ^¬ because of a defect of the shaft bearing on the first support ^¬ roll, so the shaft rotates together with the first support roller. Due to the rotation of the first support roller about the first axis of rotation and the rotation of the shaft about the shaft axis of rotation, the shaft rolls on the first support roller. Frictional forces are reduced because the first support roller and the shaft have, so to speak, the same peripheral speeds at their contact point or contact area. Since the first support roller is arranged under the shaft, the first

Support role record the weight of the shaft and the Wel ^¬ le wear. Thus, the shaft is very gently collected without tensions or abrasion in the contact area of the Wave and the first support roller are caused. A defect of the shaft due to the dropping on the fishing camp or the first support roller can thus be reduced. According to a further exemplary embodiment, the shaft has a shaft shoulder with a surface whose normal is aligned parallel to the shaft rotation axis. The first support roller has a contact surface which is complementary to the surface in the Wesentli ^¬ chen. The first support roller is further arranged such that upon an axial displacement of the shaft along the shaft rotation axis, a further force-transmitting ^¬ bearing coupling between the contact surface and the surface of the shaft can be generated. With the embodiment described above, a Wel ^¬ le can be collected, which is moved due to a bearing defect along the axial direction. The first rotation axis of the first supporting surface can be aligned, for example, paral lel ^¬ or orthogonal to and spaced from the shaft axis of rotation.

According to a further exemplary embodiment, the shaft has a further shaft shoulder with a further surface, the normal of which has an angle to the shaft rotational axis. The first support roller has a further contact surface which is complementary to the further surface. The ers ^¬ te support roller is arranged such that when Verschie ^¬ tion of the shaft, a further force-transmitting coupling zwi ^¬ tween the other contact surface and the further surface of the shaft can be generated.

The angle may, for example, have a range between 0 ° and 90 °, in particular approximately 45 °. The further Wel ^¬ lenabsatz can sen aufwei- for example, a conical shape so that the other surface along an axial gradient enlarges a distance from the shaft axis of rotation or verklei nert ^¬. The further contact surface of the first support roller is formed complementary to the further surface of the shaft. The further surface and the further contact surfaces are in ^¬ particular complementary to each other formed Rotationsflä ^¬ Chen, wherein these touch in a contact area to allow a force-transmitting coupling. In particular, the first axis of rotation of the first support roller may have an angle to the shaft axis of rotation. For example, the first axis of rotation may not be parallel but, for example, orthogonal to the shaft axis of rotation. In particular, the ers ^¬ te rotational axis and the shaft axis of rotation on a point of intersection. The first support roller and the shaft form when contacted on the cone-shaped surfaces, so to speak, a kind of bevel gear, wherein the smaller first support roller as pinion and the larger shaft can be understood as crown gear. Thus, since the first axis of rotation does not have to be formed parallel to the shaft ^¬ axis of rotation, additional con ^¬ structive freedom of storage of the first support wheel on the housing created. This allows for better and effective ^¬ re construction of the flow machine according to the invention.

According to a further exemplary embodiment, the first support roller on a rolling bearing. By means of the rolling bearing, the support roller is mounted on the housing. A rolling bearing is for example a ball bearing or a

Angular contact ball bearings. A rolling bearing generally has an inner ring and an outer ring which are separated by rolling bodies. The outer ring may for example be mounted on the housing and the inner ring on the bearing journal of the first support roller. Between the inner ring, the outer ring and the rolling element (roll, barrel) occur mainly rolling friction.

As a rolling bearing fast running bearing types can be used to withstand the occurring speeds harmless. The rolling bearings may be formed, for example, as a spindle bearing (angular contact ^¬ ball bearing). For high loads is one Paired bearings of bearings for supporting the first support role helpful.

According to a further exemplary embodiment, the turbomachine has a lubricant device. The

Lubricating ^device is coupled to the rolling bearing such that lubrication of the rolling bearing with a lubricant ^¬ medium can be generated. For example, a Tauchschmie ^¬ tion or Olnebelschmierung can be implemented by means of the lubricant-teleinrichtung, to provide sufficient delay for the Schmie ^¬ bearings.

According to a further exemplary embodiment, the turbomachine further comprises a drive unit for driving the first support roller. The drive unit drives the first support roller in normal operation of the flow shaft, for example, if there is no contact with the rotating shaft. The drive unit may for example be coupled via a belt to the support roller in order to implement a belt drive. The drive unit may also have a

Have electric motor, which transmits the torque to the shaft directly or indirectly via a transmission.

The drive unit may also have aerodynamic surfaces, such as wings or spoilers. The aerodynamic surfaces may be located close to the shaft so as to be driven by a drag flow created by rotation of the shaft, thereby rotating the first support roller. Thus, a flow drive for the first support roller by means of at ^¬ drive unit is provided in other words.

In normal operation (ie with proper functioning of the shaft bearings), the roller-supported support rollers can run at a certain speed in order to prevent the support rollers from becoming stuck during a long standstill. In addition, when the shaft is dropped a sudden acceleration from the

Standstill of the support rollers avoided. According to a further exemplary embodiment, the drive unit is designed such that when passing the force-transmitting coupling of the first support roller with the shaft, the shaft can be driven by means of the first support roller. For example, the drive unit may be designed sufficiently strong to transmit a torque to the shaft and thus drive the shaft. In case of a defect of the shaft bearing and the resulting resting of the shaft on the first support roller, rotation of the shaft can still be made possible due to the drive unit. Thus, an emergency operation of the flow machine can erect Sustainer ^¬ th are, so to speak, since the shaft is the first support roller is trie ^¬ ben.

According to a further exemplary embodiment, the turbomachine has a braking device which is ^{ausgebil ¬} det to brake the first support roller. The Bremseinrich ^¬ tion, for example, have a disc brake to brake the rotation of the support roller. Furthermore, the

Brake device be integrated in the drive unit, so ^¬ a braking ^¬ effect is achieved, for example by means of an engine braking. The support rollers can be optionally equipped with the braking device to limit the wave outflow time after the shaft is dropped, wherein the braking device can be formed mechanically or electrically acting. According to a further exemplary embodiment, the turbomachine has a second support roller with a second axis of rotation. The second support roller is spaced from the shaft. The second support roller is further arranged in such ^¬ order that upon displacement of the shaft a force transmitting coupling between the first support roller, the second support roller and the shaft is generated and rotates upon rotation of the shaft, the first support roller about the first axis of rotation and the second support roller rotates about the second axis of rotation. The second support roller may be formed according to the first support roller and the same as above, described for the first support roller features and embodiments. For example, the second support roller may also be roller-mounted. In addition, the second support roller can be lubricated by means of the lubricant device, be driven by means of the drive unit and / or be braked by the braking device.

According to another exemplary embodiment, the second support roller is offset relative to the first support roller along the circumferential direction of the shaft. According to a further exemplary embodiment, the turbomachine has a third support roller with a third axis of rotation. The third support roller is spaced from the shaft. The third support roller is angeord ^¬ net, that during a displacement of the shaft against the

Gravity direction, a further force-transmitting coupling between the first support roller and the shaft can be generated. The third support roller is arranged for example on the shaft be ^¬ abstandet. Due to rotations, further force-transmitting coupling between the third support roller and the shaft may occur so that the shaft can not break up out of the housing or contact the housing. By means of the third support roller, a destruction of the shaft is thus prevented if the shaft bearing fails due to a defect and the shaft threatens to break out at the top.

The third support roller may be formed according to the first and / or the second support roller and have the same features and designs described above, for the first and second support roller. For example, the third support roller may also be roller-mounted. In addition, the third support roller can be moved by means of the lubricant device. be lubricated, driven by the drive unit ^¬ the and / or be braked by the braking device.

The first support roller, the second support roller and the third support roller can be arranged distributed in the circumferential direction of the shaft uniformly around the shaft on the housing. The first and second support rollers can substantially together accommodate the weight of the shaft. The third support roller, which is positioned over the shaft, limits a displacement of the shaft upwards. For example, the support rollers may be spaced about the shaft in a 120 ° angle along the shaft circumference and so to speak, on the positio ^¬ ns 4 pm (first support roller), 8 hrs (second support roller) and 12 pm (third supporting roller) along the shaft circumference angeord- net become. The two lower support rollers (first support roller and second support roller) each carry a share of Wel ^¬ lengewichtskraft. Furthermore, it is also possible to arrange four Stützrol ^¬ len, which are each arranged at symmetrical intervals along the circumferential direction around the shaft, for example, each 90 °.

According to a further exemplary embodiment, the turbomachine has a magnetic bearing. In particular, the turbomachine here has a first stator ring for generating an electromagnetic bearing force. The first stator ring has a first opening, which is larger than the shaft, so that the shaft is arranged without contact with the first stator ring. The first stator ring is arranged such that by means of the electromagnetic bearing force a constant axial distance or a constant radial distance to the bearing disk is durable. The stator is buildin ^¬ Strengthens example, on the housing of the flow machine. By means of the electromagnetic bearing force of the stator, a predetermined distance between the stator and the bearing plate is kept constant, yet the La ^¬ gerscheibe with the shaft is rotatable relative to the first stator ring. The first stator ring has respective coils, which are arranged in the circumferential direction of the shaft. Thus, the first stator ring can generate a controllable electromagnetic force about the circumference around the shaft and thus a radial or axial distance between the respective stator ring and the

Keep bearing disc / bearing point constant. Thus, be ^¬ touchless storage of the bearing disc / bearing and allows the shaft. With the invention described above, a backup bearing device is provided in which the weight of the shaft is absorbed by roller-mounted support rollers (in particular first support roller and second support roller). Due to the geometrical and kinematic conditions of the support rollers with respect to the shaft, high rotor dimensions, for example over 100 tons, can be absorbed via the support rollers or their roller bearings or roller bearing arrangements, while the roller-mounted support rollers have a sufficient speed limit and a sufficient speed limit Have load-bearing capacity.

In normal operation of the turbomachine, the support rollers are arranged so that they have a distance of about 0.05 mm to about 0.5 mm, in particular from about 0.1 mm - about 0.3 mm. Thus, a continuous load entry is prevented in the corresponding support rollers.

The support rollers may also be temporarily adjusted for centering and alignment purposes of the shaft so that the rotor is positioned in the desired position and supported for example by means of the support rollers and corresponding adjusting screws or fitting pieces between the support rollers and the shaft. With the above invention, the flow engine can be almost an unlimited number of poles down the shaft, that is, an unlimited number of effects of delay Wellenla ^¬ bear. Furthermore, the wave can litter or after a defect in the shaft bearing can be caught more gently, because there is no sudden and rapid deceleration of the shaft after the ejection, since the shaft rests on the corresponding support rollers and rolls slowly. In particular, the roller-bearing support rollers have a long service life. At a rated speed, the life of the support rollers can reach up to 1000 operating hours. The smooth braking of the shaft after it has been dropped on the support rollers makes it possible to naturally and gently brake the shaft.

It should be understood that the embodiments described herein are merely a limited selection of possible embodiments of the invention. Thus, it is possible to combine the features of individual embodiments in a suitable manner with one another, so that a multiplicity of different embodiments are to be regarded as obviously disclosed to the person skilled in the art with the variants of embodiment that are explicit here.

Brief description of the drawings

In the following, for further explanation and for a better understanding of the present invention, embodiments will be described in detail with reference to the accompanying figures.

1 shows a sectional view of a turbomachine with a shaft and four support rollers according to an exemplary embodiment of the present invention;

FIG. 2 is a schematic view of a shaft and a support roller according to an exemplary embodiment of the present invention; FIG.

3 shows a schematic view of a shaft with a shaft shoulder and a support roller according to an exemplary embodiment of the present invention; and Fig. 4 shows a schematic view of a shaft and a support roller with conical contact surfaces according to an example ^¬ embodiment of the present invention.

Detailed description of exemplary Ausführungsfor ^¬ men

The same or similar components are provided in the figures with the same reference numerals. The illustrations in the figures are schematic and not to scale.

1 shows a turbomachine 100 which has a housing 101 and a shaft 102 rotatably mounted about a shaft rotational axis 103 relative to the housing 101. Furthermore, a first support roller 110 with a first axis of rotation 111 is mounted on the housing 101. The first support roller 110 is beabs ^¬ tandet arranged to the shaft 102. The distance 104 can be at ^¬ play, about 0.1 mm to about 0.3 mm. In particular, during normal operation of the turbomachine 100, the distance 104 is maintained.

The first support roller 110 is further arranged such that upon displacement of the shaft 102 (axially or radially), a force-transmitting coupling between the first support roller 110 and the shaft 102 can be generated and upon rotation of the shaft 102, the first support roller 110 around the first Rotary shaft 111 rotates. In addition to the first support roller 110 is in Fig. 1, a second

Support roller 120 with a second axis of rotation 121, a third support roller 130 with a third axis of rotation 131 and a four ^¬ te support roller 140 with a fourth axis of rotation 141 Darge ^¬ represents. The first support roller 110 and the second support roller 120 are arranged, for example, underneath the shaft 102 (or on the lower shaft half), and the third support roller 130 and the fourth support roller 140 are, for example, uppermost. half of the shaft 102 (or on the upper half shaft) angeord ^¬ net.

The shaft 102 is mounted on the housing 101, for example, by means of a magnetic bearing. In case of defect of the magnetic bearing ver ^¬ the shaft 102 moves along the direction of gravity, F, to the shaft 102 rests and on the first supporting roller 110 and the two ^¬ th backup roller 120 a force-transmitting Kopp ^¬ development of the weight of the first supporting roller 110 and the second support roller 120 is provided. The shaft 102 rotates around the shaft axis of rotation 103 with a Umfangsge ^¬ speed Vw. Upon contact of the shaft 102 with the entspre ^¬ sponding first supporting roller 110 and the second support roller 120 to rotate the respective support rollers 110, 120 is also at a peripheral speed VI in accordance with the scope ^¬ speed Vw of the shaft 102. the contact surfaces or contact surfaces of the support rollers 110, 120 roll so to speak, from the surface of the shaft 102 so that it hardly no abrasion or to a low Abrollreibung between the shaft 102 and the respective supporting rollers 110, 120 comes.

In order to provide a more gentle collection of the shaft 102 with the entspre ^¬ sponding support rollers 110, 120, 130, 140, the support rollers 110, 120, 130, 140 can by means of a drive unit 205 to a vorbe ^¬ agreed rotational speed VI also at spaced shaft 102 are brought ,

The third support roller 130 and the fourth support roller 140 are, as shown by way of example in FIG. 1, arranged above the shaft 102, so that upon a displacement of the shaft 102 upward, for example due to vibrations, a spacing of the shaft 102 to the housing 101 can be gently ensured. Fig. 2 shows an exemplary view of the first supporting roller 110 and the shaft 102. According to the first supporting ^¬ roll 110, as shown in Fig. 2, also the other support rollers 120, 130, 140 and designed to be stored can. In Fig. 2, the shaft 102 is shown, which is rotatable about its Wel ^¬ lendrehachse 103. The first support roller 110 has a distance 104 from the shaft 102. The first support roller 110 has a cylindrical shape. The first axis of rotation 111 is, for example, parallel to the shaft axis of rotation 103 being ^¬ directed. In a central region of the first support roller 110, a cylindrical rolling body is shown, which has a radial contact surface 203. In the case of the shedding of the shaft 102, the radial contact surface 203 is in contact with a shaft surface of the shaft 102.

At an axial end of the central region of the first

Support roller 110 is an end portion of the first support roller 110 formed with a smaller diameter compared to the central region. The end region of the first support roller 110 forms, for example, a bearing journal 202. On the La ^¬ gerzapfen 202 a roller bearing 201 is arranged. The rolling bearing 201 has, for example, an inner ring which is in contact with the journal 202 and an outer ring which is fixed to the housing 101. The roller bearing 201 can splash lubricated with ^¬ means of a lubricating device or mist lubrication oil. Furthermore, a drive unit and / or a brake unit can be coupled to the trunnion 202 to the first support roller 110 in the desired manner to zutreiben ^¬ or decelerate.

Further, a bearing cap 204 may be arranged, which einlager the bearing pin 202 and the rolling bearing 201. Together with corresponding axle seals, a lubricating space can be provided, in which sealing a lubrication of the rolling bearing 201 can be provided.

The first support roller 110 can be mounted in the axial direction on one side by a roller bearing 201. In addition, as shown in Fig. 2, the first support roller 110 at one end opposite to the other end another bearing journal 202 ', which by means of another Rolling bearing 201 'is mounted on the housing 101. The further roller bearing 201 'and the further bearing journal 202' can be enclosed by means of a further cover 204 'in order to provide a sealed lubrication region.

FIG. 3 shows another exemplary embodiment of the present invention in which the shaft 102 has a shaft shoulder 301. Furthermore, the first support roller 110 is shown schematically. According to the first support roller 110, as shown in FIG. 3, the others can also be used

Support rollers 120, 130, 140, which are not shown in Fig. 3, are formed.

Due to the shaft shoulder 301, the shaft has a surface with a normal parallel to the shaft rotation axis 103 and a surface with a normal radial to the shaft rotation axis 103. The first rotation axis 111 is formed parallel to the shaft rotation axis ^¬ 103rd The first support roller 110 further includes the central cylindrical portion, the central cylindrical portion having the radial contact surface 203 and an axial further contact surface 302. In particular, the radial Kon ^¬ clock face 203 has a normal that is formed in the contact area with the shaft 102 perpendicular to the shaft axis of rotation 103rd The other contact surface 302 has a normal that is formed in the contact area with the Wel ^¬ le 102 parallel to the shaft axis of rotation 103rd In other words, the contact surface 203 and the further contact surface 302 of the first support roller 110 are formed corresponding to the corre ^¬ spective shaft shoulder surfaces.

When the shaft 102 is displaced along the direction of gravity F, the distance (radial distance) 104 decreases until a force-transmitting coupling between the first support roller 110 and the shaft 102 is established via the radial contact surface 203.

Furthermore, with the arrangement of the first support roller 110 in FIG. 3, an axial displacement of the shaft 102 can also be achieved. long axial direction 304 are caught. With an axial displacement of the shaft 102 along the axial direction 304, there is a force-transmitting coupling between the further contact surface 302 and the shaft 102. The axial distance 303 decreases during axial displacement along the axial direction 304 of the shaft 102. The further contact surface 302 is in particular complementary to the Axialflä ^¬ che (further surface) of the shaft shoulder 301 of the shaft 102 is formed. The first rotation axis 111 is formed parallel to the shaft rotation axis 103 in FIG. With axial displacement of the bung ^¬ shaft 102 along the axial direction 304 and in contact with the further contact surface 302 with the shaft 102 from the shaft 102 and the first support roller 110 rolls or minima ^¬ len friction (Abrollreibung) to each other.

4 shows a further exemplary embodiment, in which the first axis of rotation 111 has an angle (eg between 1 ° and 90 °) to the shaft rotation axis 103, wherein the first support roller 110 can intercept a radial and an axial displacement of the shaft 102 , According to the first support roller 110, as shown in Fig. 4, and the other support rollers 120, 130, 140, which are not shown in Fig. 4, can be formed. The shaft shoulder 301 of the shaft 102 is conical. A normal line of the conical surface of the shaft shoulder Wellenab ^¬ record 301, so to speak has an angle to the shaft axis of rotation 103rd The angle is in particular formed between approximately 1 ° and 89 °. Correspondingly complementary to the conical shaft shoulder surface, the further contact surface 302 of the first support roller 101 is formed. The further contact ^¬ surface 302 has a more normal, which has a white ^¬ direct angle to the first axis of rotation 111 of the first Stützrol ^¬ le 110th The angle and the further angle are in particular the same.

Upon displacement of the shaft 102 along its radial direction or along the direction of gravity F or during displacement the shaft 102 in the axial direction 304 there is a contact of the conical shaft shoulder surface and the conical further contact surface 302 of the first support roller 110. Accordingly, in the manner of a bevel gear, the ent ^¬ speaking surfaces roll (more contact surface 302 and Wellenab ^¬ flow area) to each other from, so that only a slight rolling friction occurs. Thus, a gentle interception of the shaft 102 can be implemented by means of the first support roller 110, wherein in particular a displacement of the shaft 102 in multiple Rich ^¬ tions (radial, axial) can be collected.

Advantageously, the further contact surface of the first support ^roller 110 is designed such that an imaginary extension of the adjoining contact line in the contact region between the further contact surface 302 and the further surface of the shaft shoulder 301 by the axis intersection of the shaft rotation axis 103 and the first axis of rotation 111 first support roller 110 extends. As a result, a Bohrreibungsanteil is reduced and increases the allowable force to be transmitted.

The imaginary extension of the self-adjusting of contact is sort of a generatrix of the further contact surface 302 of the first support roller 110. The surface line is a line that on the jacket of a rotating body (for example the kegelför ^¬-shaped supporting roller 110) longitudinally with respect to its rotation axis (first rotation axis 111) runs, ie the links between the imaginary tip and the (edge) points of the base circle of the first support roller 110th

A first (in particular conical) support roller 110 can in particular absorb the shaft 102 when the shaft 102 is displaced in the axial direction 304, and a further first (in particular conical) support roller 110 can receive the shaft 102 when the shaft 102 is displaced in the radial direction. In addition, it should be pointed out that "comprehensive" does not exclude any ^other elements or steps and "one" or "one" does not exclude a large number. Further thereon was hingewie ^¬ sen that features or steps which have been described with reference to one of the above embodiments, also be used in combination with other characteristics or steps of other exemplary embodiments described above Kgs ^¬ NEN. Reference signs in the claims are not to be considered as limiting.

Claims

claims

1. Turbomachine (100), comprising

a housing (101),

a shaft (102) rotatably mounted about a shaft rotation axis (103) relative to the housing (101), and

a first support roller (110) having a first axis of rotation (111),

wherein the first support roller (110) is spaced from the shaft (102), and

wherein the first support roller (110) is further arranged such that, during a displacement of the shaft (102) a force ^¬ transmitting coupling between the first support roller (110) and the shaft (102) is generated and (102 upon rotation of the shaft ) rotates the first support roller (110) about the first rotation ^¬ axis (111).

2. Turbomachine (100) according to claim 1,

wherein the first support roller (110) is arranged such that the first rotation axis (111) is parallel to the shaft rotation axis (103), and

wherein the first support roller (110) is arranged such that upon displacement of the shaft (102) along the gravitational force direction, the force-transmitting coupling between the first support roller (110) and the shaft (102) can be generated.

3. turbomachine (100) according to claim 1 or 2,

wherein the shaft (102) has a shaft shoulder (301) with a surface whose normal is aligned parallel to the shaft rotation axis (103),

wherein the first support roller (110) has a contact surface (203) which is complementary to the surface,

wherein the first support roller (110) is further arranged such that upon an axial displacement of the shaft (102) along the shaft rotation axis (103), a further force-transmitting coupling between the contact surface (203) and the surface of the shaft (102) can be generated ,

4. turbomachine (100) according to claim 1 or 2,

wherein the shaft (102) has a further shaft shoulder (301) with a further surface, the normal of which has an angle to the shaft rotation axis (103),

wherein the first support roller (110) has a further contact surface (302) which is complementary to the further surface, and

wherein the first support roller (110) is arranged such that upon displacement of the shaft (102) a further force-transmitting coupling between the further contact surface (302) and the further surface of the shaft (102) can be generated.

5. turbomachine (100) according to one of claims 1 to 4,

wherein the first support roller (110) comprises a rolling bearing, ^¬ with which the first support roller (110) is mounted on the housing (101).

6. turbomachine (100) according to claim 5, further aufwei- send

a lubricant device,

wherein the lubricant means is coupled to the rolling bearing (201) such that lubrication of the rolling bearing (201) can be generated with a lubricant.

7. Turbomachine (100) according to one of claims 1 to 6, further comprising

a drive unit (205) for driving the first support roller (110).

8. Turbomachine (100) according to claim 7,

wherein the drive unit (205) is designed such that when passing the force-transmitting coupling of the first support roller (110) with the shaft (102), the shaft (102) by means of the first support roller (110) is drivable.

9. Turbomachine (100) according to one of claims 1 to 8, further comprising a braking device configured to brake the first support roller (110).

10. Turbomachine (100) according to one of claims 1 to 9, further comprising

a second support roller (120) having a second Drehach ^¬ se,

wherein the second support roller (120) is spaced from the shaft (102), and

wherein the second support roller (120) is further arranged such that during the displacement of the shaft (102) a force ^¬ transmitting coupling between the first support roller (110), the second support roller (120) and the shaft (102) can be generated and upon rotation of the shaft (102), the first support roller (110) rotates about the first rotation axis (111) and the second support roller (120) rotates about the second rotation axis (121).

11. Turbomachine (100) according to claim 10,

wherein the second support roller (120) is offset relative to the first support roller (110) along the circumferential direction of the shaft (102).

12. Turbomachine (100) according to one of claims 1 to

11, further comprising

a third support roller (130) having a third axis of rotation

(131),

wherein the third support roller (130) is spaced from the shaft (102), and

wherein the third support roller (130) is arranged such that upon displacement of the shaft (102) against the gravitational force direction, a further force-transmitting coupling zwi ^¬ tween the third support roller (130) and the shaft (102) can be generated.

13. Turbomachine (100) according to one of claims 1 to

12, further comprising

a first stator ring for generating an electromagnetic bearing force, wherein the first stator ring has a first opening which is larger than the shaft (102) so that the shaft (102) is arranged rotatably without contact with the first stator ring, and

wherein the first stator ring is arranged such that by means of the electromagnetic bearing force a constant axial distance or a constant radial distance to the shaft (102) is durable.

14. A method for operating a turbomachine (100) according to one of claims 1 to 13.